Design Specification of Hoist for Water Resources and Hydropower Engineering

7/22/2019 Design Specification of Hoist for Water Resources and Hydropower Engineering

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ICS 27.140

P 59

File No.: 210-2002

DLPROFESSIONAL STANDARD OF

THE PEOPLE’S REPUBLIC OF CHINA

中华人民共和国行业标准 DL/T 5167-2002

Design Specifications for Gate Hoist in Hydropower

and Water Resources Projects

水电水利工程启闭机设计规范

Issued on September 16, 2002 Implemented on December 1, 2002

Issued by: National Economic and Trade Commission of China



Contents

Foreword ............................................................................................................................................3

1. Scope ..............................................................................................................................................5

2. Normative Reference......................................................................................................................6

3. Basic Symbols................................................................................................................................7

4. General Provisions..........................................................................................................................8

5. Design Principle and Requirements ...............................................................................................9

6. Load..............................................................................................................................................18

8. Mechanism ...................................................................................................................................25

9. Structure .......................................................................................................................................40

10. Electrics ......................................................................................................................................58

Annex A (Informative Annex) Hoisting Force, Lift Head, Span and Speed Series of Gate

Hoist Date and Example of Working Class of Gate Hoist................................................................63

Annex B (Informative) Recommended Values of Acceleration (Deceleration) of Running

Mechanism and Corresponding Acceleration (Deceleration) Time..................................................65

Annex C (Informative) Calculation Method of Horizontal Lateral Force Ps during Oblique

Running of Gate Hoist......................................................................................................................66

Annex D (Informative) Calculation Data of Wind Load..................................................................67

Annex E (Informative) Permissible Physical Quantity of Commonly-used Friction Surface

Material ............................................................................................................................................70

(Informative) ....................................................................................................................................71

Friction Coefficient and Efficiency ..................................................................................................71

Annex G (Informative) Relevant Calculation Data of Parts and Track............................................73

Annex H (Informative) Calculation Data for the Hydraulic Gate Hoist...........................................89

Annex J (Informative) Materials for Calculating Stability of Two-way or One-way Bending

Members.........................................................................................................................................106

Annex K (Informative Annex) Overload check of motor...............................................................121

Annex L (Informative Annex) Heating inspection of winding-type asynchronous motor ............. 123

Annex M (Informative Annex) The allowable output capability (P) of YZR series

electromotor under different load duration factor (FC value) and under different CZ values

(the average startup multiples K= 1.7) ...........................................................................................125

Annex N (Informative Annex) The electromotor of gate hoist mechanism FC, CZ and G

values in the capacity selection calculation....................................................................................130 Annex P (informative annex) Current-carrying capacity of conducting wire ................................132

Annex Q (informative annex) Explanations on the text description in these Specifications.......... 136



Foreword

This standard contains amendments to the hydraulic hoist content of SL 41-1993

Hydraulic and Hydropower Project Specification for Design of Gate Hoist according

to Notice on Project of Establishment and Amendment of Power Industry Standard in1997, and the amendment format complies with requirements of Basic Regulation for

Compilation of Power Industry Standard (DL/T 600-2001).

This standard fully reflects new experiences on design, manufacture, installation

and operation of large and medium gate hoist of hydropower and water resource

projects over the last decade, on basis of comprehensive survey, conclusion and

research. Amendment and implementation of this standard may establish a new and

uniform design standard for the industry and further improve industrial design level.

Opinions were asked on the amendment content of this standard from relevant units in

written form in October 1998. Standard amendment working conference was held in

Zhengzhou city, Henan Province, in November 1999, and principle, method and task were determined on the conference. The first exposure draft of Design Specifications

for Gate Hoist in Hydropower and Water Resources Projects was issued in April, 2000,

and was discussed and amended on Changzhou Conference. Then it was issued again

in May, 2000, for more than 50 design institute, factory, college and research institute

of hydropower and water resource system, to give their opinions. In April, 2001, first

draft for approval was worked out, forming formal draft for approval after discussion

and supplement made on Chengdu conference. Examination of the draft standard for

examination was carried out on Hangzhou conference in December, 2001, forming

draft standard for approval after amendment.

Revision involves 18 articles of the hydraulic gate hoist part of original standard,

and 2 articles of the 18 are cancelled, 4 articles are added, and 14 articles are

supplemented. After revision, hydraulic gate hoist part totally contains 20 articles and

36 clauses, and over 90% of original articles are revised. Also, revisions are made to

relevant articles of hydraulic gate hoist part, or to relevant original parts that are

obviously out of date, these revisions involve 12 articles.

The revision practically summarizes and absorbs experiences on fast

development of hydraulic gate hoist over last decade in China, so as to enrich content

of the standard. For instance, it is summarized that malfunctions happened in

operation of hydraulic gate hoist are caused by contamination of hydraulic oil. Someasures to prevent hydraulic oil from pollution are put forth and series new

requirements of cleanness of hydraulic oil, oil filtration, cleaning of oil pipe, as well

as material of oil pipe and oil tank are definitely prescribed. And it is prescribed that

crest spillway radial gate double drum hydraulic hoist shall adopt relevant

synchronous measures according to concrete conditions. In order to strengthen

systematicness and integrality of articles, merges and adjustment are made among

articles involving the same content but being dispersed in different articles, such as

content of oil tube is concentrated in clause 8.4.7.

Appendixes attached thereto are informative appendixes.

This standard is proposed by and under the jurisdiction of Power Industry



Hydropower Plant Metallic Structure and Gate Hoist Technical Committee of

Standardization.

This Standard is compiled by Northwest Hydroelectric Investigation & Design

Institute, State Power Company; Chengdu Hydroelectric Investigation & Design

Institute, State Power Company; Mid-south Design and Research Institute for Hydroelectric Project; and Jiangsu wujin Hydraulic Hoist Co., Ltd. This standard is

drafted by: Chen Wenhong, Zhao Fuxin, Liao Yongping, Gong Jianxin and Guo

Xihong

First issue of this Standard is promulgated on October 1, 1993.



1. Scope

This specification specifies design principle, load, material and mechanism of

gate hoist of hydropower projects.

This standard is applicable to fixed gate hoist and mobile gate hoist that mainlyadopt electric drive to open and close gate and trash rack in hydropower project. Fixed

gate hoist includes different types, such as winding type, screw-rod type, hydraulic

hoist and chain-type, and mobile gate hoist includes portal hoist, trolley hoist and

bridge hoist.



2. Normative Reference

The following documents contain contents which, through reference in this text,

composite provisions of this standard. For dated reference, subsequent amendments

(excepting corrigenda content) to, or revisions of, any of these publications do notapply. Parties to agreements based on this standard are encouraged to investigate the

possibility of applying the most recent editions of the standards indicated below. For

undated references, the latest edition of the normative document referred to applies.

GB/T 116 Specifications for Rivet

GB/T 699 Quality Carbon Structure Steel

GB/T 700 Carbon Structural Steels

GB/T 985 Basic Forms and Sizes of Weld Grooves for Gas Welding Manual Arc

Welding and Gas-shielded Arc Welding

GB/T986 Basic Forms and Sizes of Weld Grooves for Submerged Arc Welding

GB/T 117 Specification for Cast Copper AlloysGB/T 1231 Specifications of High Strength Bolts with Large Hexagon Head,

Large Hexagon Nuts and Plain Washers for Steel Structures

GB/T 1348 Spheroidal Graphite Iron Castings

GB/T 3077 Alloy Structure Steels

GB/T 3098.1 Mechanical Properties of Fasteners - Bolts, Screws and Studs

GB/T 3098.2 Mechanical Properties of Fasteners: Nuts - Coarse Thread

GB/T 3098.3 Mechanical Properties of Fasteners - Set Screws

GB/T 3098.4 Mechanical properties of fasteners-Nuts-Fine pitch thread

GB/T 3098.6 Mechanical properties of fasteners-Bolts, screws and studs made of

stainless-steel

GB/T 3633 Technical requirement for sets of torshear type high strength bolt

hexagon nut and plain washer for steel structures

GB/T 5117 Carbon steel covered electrodes

GB/T 5118 Low alloy steel covered electrodes

GB/T 9439 Grey iron castings

GB/T 11352 Carbon steel castings for general engineering purposes

GB/T 13098 Ethylene oxide for industrial use

GB/T 14039 Hydraulic fluid power-Fluids-Method for coding level of

contamination by solid particlesJB/ZQ 4297 Alloy Casting Steel

JB/ZQ 4295 Stainless Steel, Acidproof, Heat-resisting Forging Steel

ISO 4406 Hydraulic fluid power -- Fluids -- Method for coding the level of

contamination by solid particles

NAS 1638 Hydraulic fluid power -- Fluids -- Method for coding the level of

contamination by solid particles



3. Basic Symbols

M refers to bend diameter or torque;

N refers to axial force;

P refers to applied load;Q refers to shearing force;

P refers to working pressure;

qv refers to flow quantity;

E refers to elastic modulus of steel;

G refers to shearing modulus of steel;

σ refers to positive stress;

τ refers to shear stress;

σs refers to yield strength;

σ b refers to tensile strength;

A refers to area;l or L refers to span or length;

h or H refers to height;

I refers to moment of inertia;

W refers to resistance moment;

d or D refers to diameter;

R refers to radius;

λ refers to slenderness ratio;

δ refers to thickness;

i refers to transmission ratio;

v refers to velocity;

n refers to coefficient or rotate speed;



4. General Provisions

4.0.1 This standard is the necessary regulation and technical basis of type selection,

arrangement, design and calculation of gate hoist. Where discrepancies are found

between this standard with other relevant design standard, this standard will prevail.4.0.2 Except hydraulic gate hoist, working class of gate hoist mechanism is divided

into 4 classes according to their design service life and load status (see Table 4.0.2).

Working class of the main hoisting mechanism is just the working class of the gate

hoist. For examples of working classes of gate hoist, see Appendix A.

Table 4.0.2 Working Classes of Mechanism

Working

Class

Design Service

Life (h)Load Status

Q1-light 800

Q2-light 1600

Be not infrequently used, and not often used to

hoist rated load

Q3-medium 3200Sometimes to hoist rated load, but medium load

is usually hoist.

Q4-heavy 6300 Be frequently used to hoist rated load.

4.0.3 Design Data

Data needed to design gate hoist shall include the followings:

1. Requirements of hoisting mode, water-refilling mode, water-discharging,

local-hoisting and hoisting and travel speed of hydropower and water resource main

gate operation;2. Sizes of gate flap and gate slot, allowable sizes of relevant arrangement, and

relevant sizes and requirements of connection between gate and gate hoist.

3. Electric control mode and interface requirements;

4. Hydrology, weather, mud, sand and water quality;

5. Load data;

6. Relevant conditions of manufacturing, transportation and installation;

7. Earthquake and other special requirements;

8. Requirements of dynamic power and control power supply.

4.0.4 For selection of hoisting force, lift head, span and speed, see Appendix A.

4.0.5 Gate hoist shall be equipped with relevant safety devices, such as brake, load

limiting device, moment limiting device, upper and lower caging device, travel limiter,

buffer, wind-prevention rail clamping device, anchorage, hydraulic system protection

and electric protection device.

4.0.6 Gate hoist shall adopt protective measures, such as moisture-proof, ventilation,

corrosion-proof and weather proof.

4.0.7 Generally, fatigue strength of structural components of hoisting equipments is

not calculated.

4.0.8 Disassembly size and weight of gate hoist shall comply with transportation

provisions, and transportation unit shall have necessary rigidity.



5. Design Principle and Requirements

5.1 General Provisions

5.1.1 Design of gate hoist must satisfy relevant requirements, such as advanced

technology, reliable operation, economic feasibility, convenient maintenance,harmonized landscape, labor security and environmental protection.

5.1.2 Type of gate hoist shall be selected according to hydraulic arrangement, door

type, number of hole, operation and time requirement after comprehensive technical

and economic research. In selection of gate hoist for gates having different usages, the

following principles can be followed:

1. Generally, gate hoist of water release system main gate adopts

one-door-one-machine arrangement, but if gate operation and hoisting limitation allow,

mobile gate hoist can be adopted.

2. Gate hoist of multi-hole water release system usually use mobile gate hoist.

3. For gate hoist of hole-sealing gate used for diversion during construction, thehoisting force shall satisfy the requirement that gate is hoisted under certain delivery

head, and accurate lifting indication device.

4. Gate hoist of tide gate and working water gate adopt one-gate-one-machine

arrangement.

5. Type of gate hoist used to control fast gate at water inlet of power plant and outlet

of pump plant shall adopt hydraulic or winding type fast gate hoist through

comprehensive technical and economic comparison according to engineering

arrangement, gate load during hoisting and lift head. The control power supply that

can fast shut circuit off shall be set according to power-losing conditions of AC power

supply of power plant.

6. When maintenance gate is set at water inlet of multiunit power plant, mobile gate

hoist is usually adopted, and maintenance gate hoist of flood system and water release

system shall be considered where conditions are allowed.

7. For gate hoist of multi-hole trash rack at water inlet of unit, auxiliary hoisting

mechanism can be set at upriver, or auxiliary hook and main hook can also be adopted

within span. If hydraulic structures are dispersedly arranged and gate hoists are

unconditionally used, mobile gate hoist can be set independently.

8. Generally, multi-hole draft pipe maintenance gate of power plant is recommended

to adopt mobile gate hoist.9. For assembly gate or gate that shall be hoisted step by step, mobile gate hoist with

automatic hooking beam operation is usually adopted.

5.1.3 Working conditions of maintenance personnel shall be considered according to

climatic conditions and sandstorm, and fixed gate hoist can either be set in machine

room or be set outdoor. Machine room shall be departed from vent-hole of gate.

Necessary space shall be reserved for maintenance and installation at the side where

machine is near to the machine room, and passage shall be reserved between machine

and wall, and width of the passage shall not be less than 0.8m. Where gate hoist is set

outdoor, separate cover shall be adopted. Dustproof, moisture-proof and rain-proof

measures shall be considered for electric equipments.



In cold region where gate hoist will be operated in winter, the machine room shall

have lagging facility; in hot region where gate hoist will be operated in summer, the

machine room shall have cooling facility; in area where there are frequent sandstorms,

gear transmission of gate hoist is recommended not to adopt open type, or

completely-closed machine room can be set. Selection of working oil or lubricatingoil shall consider air temperature conditions at the operation area.

5.1.4 In addition to the maximum lift head of gate, gate hoist shall also have

appropriate reserve. The maximum working lift head of gate hoist controlling

submerged hole arch door shall satisfy requirements to change side and top water

stop.

5.1.5 According to hydraulic conditions and technical and economic indexes, high-lift

hoist can be adopted, if conditions are met.

5.1.6 Arrangement of high-lift hoist shall prevent disturbance of movable block group,

steel cable and gate slot.

5.1.7 Movable block group shall adopt protective measures to prevent steel cable fromescaping from the slot. Movable block group that is submerged under water is

recommended to adopt sliding bearing axle, and anti-corrosion measures shall be

adopted on the surface. Seal device shall be adopted, if rolling bearing is adopted.

5.1.8 When plane gate is lifted, the hoisting central line shall keep accordance with

the hoisting central line of the gate.

5.1.9 For mobile hoist having large hoisting force, hoisting tool and gate (or sag rod)

are recommended to adopt automatic hooking beam or manual hitch bar. When

connecting shaft is heavy and operation is difficult, fixed hoist is recommended to

adopt manual hitch bar.

5.1.10 Installation elevation of gate hoist shall satisfy requirement of safe operation,

so as to prevent power section and electric equipments of gate hoist from flooding,

and shall be convenient for normal maintenance of gate, gate slot and component of

gate hoist. In addition, anti-corrosion of components exposed to water shall be

considered.

5.1.11 Gate hoist that controls flood relief gate and other emergency gate must be

equipped with reliable stand-by power supply.

5.1.12 During selection of gate hoist series, hoisting force of gate hoist shall be

greater than or equal to calculated hoisting load.

5.1.13 Dropping speed of fast gate hoist of power plant shall be determined accordingto requirements of holes, and decelerator shall be set to guarantee that gate speed

approaching to the bottom is not faster than 5m/min.

5.1.14 Dropping speed of gate controlled by fast gate hoist at outlet of pump station

shall be determined according to requirements of fast-closing hold, and measures shall

be adopted to control its speed approaching to be fully closed.

5.1.15 Double-point hoisting gate hoist shall be equipped with relevant synchronous

measures. And gate operation shall not be affected by error of the double hoisting

points during operation.

5.1.16 Where there is sediment accumulation before gate, hoisting force of

double-point hoisting gate hoist shall be determined according to nonuniformity



coefficient of load on the double hoisting points.

5.1.17 For gate that has requirement of refilling water with small opening, gate hoist

shall be equipped with travel switch or other devices to satisfy small opening

precision.

5.2 Winch Hoist5.2.1 Winch hoist is usually used to control gate which depends on gravity, water

column or other method to close, and one hoist is usually used to control one gate.

5.2.2 In general conditions, gate hoist shall adopt on-site operation. If there are several

gate hoists, a centralized control room can be set for the operation.

5.2.3 Besides strength and reliability, chassis of gate hoist shall also be rigid enough.

5.2.4 If direction of hoisting load is gradient, action of horizontal force on relevant

components shall be considered, and relevant influence shall be calculated.

5.2.5 Requirements of high-lift gate hoist:

1. For high-lift gate hoist with rope guide, flange shall be set at place where steel

cable of rope reel returns; guide screw rod of rope guide shall consider selection of helix angle, arch radius at top turning point as well type of wrap angle of nut.

2. Free double-layer winch high-lift gate hoist is recommended to set turning flange at

position where steel cable returns and to control plane included angle that is vertical

to the reel axle when the steel cable of the second layer deviates.

3. For high-lift gate hoist whose two double-connected pulley block reeving is greater

than 2, fixed pulley block shall be hinged onto bracket of the pulley block, and

disturbance of steel cable and rest bar of fixed pulley block shall be prevented.

4. High-lift gate hoist adopting drum with broken line grooves shall consider length of

the broken line and inclination of rope groove. In addition, turning flange shall be set

at position where drum groove returns.

5.2.6 Requirements of winch hoist controlling tainter gate:

1. For top-exposed arch-gate winch hoist and pan type gate hoist whose hoisting

points are set before the water-supporting deck, the steel cable and hoisting tools are

generally set on the panel of tainter gate as close as possible, and are recommended

not to set movable pulley block; during arrangement, connection method of steel cable,

hoisting tools and lifting eye shall be considered.

2. Top-exposed tainter gate winch hoist, whose hoisting points are set behind the

water-supporting deck, can be substituted by plain gate winch hoist or be retrofitted.

During arrangement, winding, turning method synchronous action of double hoisting points shall be considered.

3. When top-exposed tainter gate is lifted by pan-type gate hoist, regulating block of

steel rope shall be set.

4. Whether stand-by power supply or manual hoisting device shall be set to

top-exposed tainter gate winch hoist shall be determined by hoisting capacity,

significance of gate and reliability of dynamic power.

5. If submerged tainter gate is controlled by plain gate winch hoist, disturbance of

steel cable and rest bar of fixed pulley block shall be prevented. Where fixed pulley

block or guide pulley device is set under the rest bar, their maintenance and

lubrication conditions shall be considered. Coupling shafts of movable pulley block



(or passing sag rod) and lifting eye of submerged tainter gate shall be chrome-plated,

and shall be equipped with lubricating devices. In addition, axle hole shall have

sheath.

5.2.7 Requirement of winch hoist controlling flap gate:

1. Movable pulley block shall be arranged higher than elevation of sedimentaccumulation.

2. Elevation of gate hoist chassis bottom must be 0.21m- 0.2m higher than travel route

of gate top.

3. During operation of gate, steel cable shall not rub with gate flap, and included angle

between connection line of lifting eye center and lifting center of gate hoist and the

vertical line when the gate is fully opened shall not exceed 15 degree.

5.3 Screw Rod Gate Hoist

5.3.1 Electric screw rod gate hoist shall have reliable safety protection device for

electric or mechanical overload.

5.3.2 Manual and electric double-duty or manual screw rod gate hoist shall beequipped with safety handle bars.

5.3.3 When manual mechanism and machine are connected with each other, manual

and electric double-duty shall have safety measures to break all circuit.

5.4 Hydraulic Gate Hoist

5.4.1 According to different operational requirements of gate, design working

condition of hydraulic cylinder of hydraulic gate hoist can adopt double-direction

action type or single-direction action type. For single-direction action type hydraulic

gate hoist, if there requirements of filling valve, maintenance and installation,

appropriate pressure can be added during system design, but pressure value shall be

kept in 0.5MPa - 1MPa.

5.4.2 Double hoisting point hydraulic gate hoist shall adopt relevant synchronous

measures according to different factors, such as type, size, structural stiffness and

lateral support of the gate to be controlled. During operation of top-exposed tainter

gate, if the tainter gate has reliable lateral support and strong torsional stiffness,

hydraulic system can adopt throttle governing and deviation-correction circuit may

not be set. In addition, capacity of gate hoist is recommended to have appropriate

reserves. If hydraulic gate hoist adopts deviation-correction circuit, closed-loop

control shall be adopted, and reliable travel measuring system shall be adopted

according to requirements of synchronous precision. Also, pipe system isrecommended to be arranged symmetrically.

5.4.3 Reasonable arrangement of tainter gate hydraulic hoist shall give integral

consideration to hoisting capacity, travel, obliquity and swing angle.

5.4.4 Arrangement of pump station of hydraulic gate hoist:

1. Number of pump station of hydraulic gate hoist can be determined according to

operation requirement of gate, and one pump station can be set for one hoist (two

cylinders for one machine with double lifting eyes) and one pump station can be

shared by several hoists. Electric motor unit of oil pump in pump station shall be

equipped with stand-by electric motor unit of oil pump.

2. Arrangement of oil pump motors of hydraulic gate hoist shall consider requirements



of anti-vibration, noise-deadening and maintenance convenience.

5.4.5 Hydraulic components shall adopt standard hydraulic components, and system

whose flow quantity is greater than 100L/min is recommended to give priority to

two-way cartridge inserted valve.

5.4.6 Safe and reliable travel supervision device shall be adopted according tosupervisory precision and requirements of hydraulic gate hoist; gate opening

instrument is recommended to adopt multi-rotation absolute sensor; stop device with

different theory is recommended to be set for extreme-position limit, and shall not be

substituted by overflow valve.

5.4.7 Working pressure of hydraulic system is recommended to be less than 25MPa;

test pressure of hydraulic cylinder or hydraulic valve unit shall adopt 1.5P when

P≤16MPa, and shall adopt 1.25P when P>16MPa.

Test pressure of pipe system shall adopt 1.5P when P≤16MPa, 1.25P when

16MPa<P≤25MPa, and 1.15P when P>25MPa; test pressure of oil return pipe and oil

exit pipe shall be determined according to 1.5 times internal pipe pressure.Test pressure duration shall exceed 10 minutes.

5.4.8 Piston rod of hydraulic cylinder of hydraulic gate hoist must adopt

anti-corrosion measures.

5.4.9 End bearings of hydraulic cylinder of top-exposed tainter gate hydraulic hoist

shall be of hinge structure type, and can be arranged at the center of hydraulic

cylinder where upper supporting point can meet relevant conditions. If end bearing is

adopted and vertical obliquity of hydraulic cylinder is relative large when the gate is

fully closed, yield-proof measures shall be adopted. Generally, end bearing of

hydraulic cylinder of hydraulic gate hoist adopts globe bearing.

5.4.10 Beside fast valve hydraulic gate hoist, hydraulic fluid port of lower-cavity of

hydraulic cylinder is recommended to set hydraulic safety locking device.

5.5 Chain Gate Hoist

5.5.1 China gate hoist is mainly used to control top-exposed working gate.

5.5.2 Lifting speed of chain gate hoist shall not exceed 1m/min generally.

5.5.3 Double hoisting point chain gate hoist shall have reliable synchronous devices to

guarantee synchronous operation of the two hoisting points.

5.5.4 In order to prevent the chain from touching water during gate hoisting,

chain-withdrawing device shall be set at one end of chain.

5.5.5 Chain of chain gate hoist shall have anti-corrosion measures.5.6 Mobile Gate Hoist

5.6.1 Span of mobile gate hoist and lifting height of working platform (dam crest,

tailrace platform) shall be able to satisfy requirements of gate operation and trash

rack.

5.6.2 Operational load and travel load of mobile gate hoist shall be determined

according to concrete conditions.

5.6.3 Generally, control and operation are realized on mobile gate hoist.

5.6.4 According to requirement of central arrangement, when mobile gate hoist travels

along a curve, reliable measures shall be adopted to prevent overload and blocking.

5.6.5 According to concrete arrangement, mobile gate hoist with small capacity can



also adopt electric hoist and monorail trolley.

5.6.6 Anti-overturn stability of mobile gate hoist.

1. Verification of working condition

Working condition verification of anti-overturn reliability shall be determined

according to Table 5.6.6-1.2. Proof of anti-overturn stability.

Anti-overturn stability of gate hoist shall be calculated under the worst load

combination according to working conditions listed in Table 5.6.6-2. If moment of all

load and gate hoist to overturn side is equal to or greater than zero (∑ ≥ 0 M ), the gate

hoist can be deemed as stable.

During verification of anti-overturn stability, relevant dangerous side of gate hoist

shall be calculated.

Considering practical impact of different loads on stability, a load coefficient shall be

multiplied by all sorts of load moment during verification of anti-overturn stability of gate hoist. For concrete values, see Table 5.6.6-2.

Table 5.6.6-1 Working Condition Verification

Verification of working condition Characteristics of working conditions

1 Static load without wind

2 Mobile load with wind

3 Off-work state in windstorm

Table 5.6.6-2 Load Coefficient

Verification

of Working

Condition

Self

WeightLoad

Horizontal

Inertia Force

(including

load)

Wind

Power Remark

1 0.95 1.4 0 0

2 0.95 1.2 1 1

3 0.95 0 0 1.15

Gate hoist with cantilever

shall verified the following

items:

(1) Longitudinal (cantilever

plane) stability (working

condition 1, 2 and 3);

(2) Transverse (travel

direction) stability (working

condition 2 and 3).

Transverse and longitudinal

stability (working condition

2 and 3) shall be verified

for gate hoist without

cantilever.

5.6.7 Safety of gate hoist against wind and slide



Safety of gate hoist against wind and slide shall be verified according to the following

two working conditions:

1. Normal working condition:

Pz l≥ 1.1Pw1 + Pa – Pf (5.6.7-1)

Where,Pzl refers to braking force generated by detent of running mechanism on wheel tread,

N;

Pwl refers to the maximum wind power along running direction under working state,

N;

Pa refers to sliding force caused by gradient, N;

Pf refers to frictional resistance during running of gate hoist, N; its running frictional

resistance coefficient shall be selected from Table 5.6.7.

When braking force Pzl is greater than adhesive force of wheel, Pzl shall be substituted

by adhesive force between wheel and track, and its adhesive coefficient shall adopt

0.12.Table 5.6.7 Running Frictional Resistance Coefficient ω

Slide Bearing Rolling Bearing

0.015 0.006

Note: ω=Pf/P, where P refers to total wheel pressure.

2. Off-working state

Pz2 ≥ 1.1Pw2 + Pa - Pf (5.6.7-2)

Where,

Pz2 refers to clamping braking force generated by track clamp of running mechanismalong track direction, N;

Pw2 refers to maximum wind power of gate hoist under off-working condition along

running direction, N.

Friction factor between track and rail clamp (whose surface has scores and that has

been quenched) shall adopt 0.25, and the maximum operating force on manual rail

clamp shall not exceed 200N.

5.7 Safety Protection Device of Gate Hoist

In order to guarantee reliable operation of gate hoist, all sorts of gate hoists shall be

equipped with relevant safety devices.

5.7.1 Brake ApparatusBesides hydraulic gate hoist, all mechanism of gate hoist shall be quipped with brake

apparatus. Screw rod gate hoist shall be equipped with brake apparatus according to

its structural type.

5.7.2 Load Limiter

Hoisting mechanism of gate hoist shall be equipped with load limiter (except in

special cases), and composite error of the load limiter shall not exceed 5%. The load

limiter can be of mechanical type or electrical type; hydraulic system shall be

equipped with overflow valve.

5.7.3 Travel Limiter



Running terminal of each mechanism of gate hoist shall be equipped with relevant

travel limiter.

5.7.4 Buffer

Running mechanism of all electric-drive mobile gate hoist shall be equipped with

buffer, or uptilted arch track can be adopted at track end as buffer.5.7.5 Anemoscope

Exposed mobile gate hoist shall be equipped with anemoscope at upper part of gate

hoist where the wind is not blocked. When wind speed is faster than limited working

wind speed, the anemoscope shall be able to alarm to stop work and automatically cut

off power supply of running mechanism.

5.7.6 Rail clamp and anchor device

Exposed mobile gate hoist shall be equipped with rail clamp. When off-working-state

wind pressure exceeds 700N/m2 or the gate hoist may be flooded, traction cable or

other anchor device must be adopted.

5.7.7 Electric protection deviceElectric protection device shall comply with provisions of 10.4 hereof.

5.8 Automatic Hooking Beam

5.8.1 Hydraulic shaft-crossing-type automatic hooking beam

This type of automatic hooking beam is manly used in operation of large and medium

gates. During design, water shall be prevented from enterring electromotor, oil pump

and junction box, and reliability of signal transmitter and strength of cable shall be

guaranteed. Hoisting speed of cable drum shall be in accordance with the speed of

lifting mechanism.

5.8.2 Mechanical automatic hooking beam

1. Weight automatic hooking beam

Weight automatic hooking beam can be divided into different types, such as weight

rotation type, weight hooking type and improvement type, and they are usually used

to control medium and small gates. Consideration shall be given to design of position

where there are relative rotation and slide, so as to prevent failure of hooking due to

corrosion, sand or other impurities.

2. Hook-type automatic hooking beam

During design of suck kind of hooking beam, running parts and locking devices

controlling the hook shall be considered, so as to prevent failure due to corrosion,

sand and other impurities.3. Free-hook-type automatic hooking beam

This kind of automatic hooking beam is mainly used to control large and medium

gates. During design, hooking and clamping object shall match with each other.

5.8.3 Design of automatic hooking beam

Design of automatic hooking beam shall satisfy the following requirements:

1. The gate shall better stop water at upper stream. Where gate stops water at down

stream, safety and reliability of underwater work shall be considered.

2. When operation of multi-leaves gate and trash rack, manufacturing and installation

accuracy of gate (rack) groove shall be improved, so as to be adaptable to operation in

gate (rake) groove.



3. Automatic hooking beam shall go through static balancing test, and

center-of-gravity position can be adjusted by counterweight. According to different

types, guidance orientation and safety devices shall be set, and operation of hooking

beam shall be guaranteed to be flexible, reliable and free from incline and block.

4. Relative rotation and sliding parts of automatic hooking beam shall adoptlubricating and anti-corrosion measures.



6. Load

Different gate hoists may have different load requirements. Load combinations listed

bellow is applicable to gate hoist of different types.

6.0.1 Self-weight LoadSelf-weight load refers to weight of gate hoist structure, mechanical equipment,

electric equipment and ballast.

6.0.2 Hoisting Load

Hoisting load refers to the maximum hoisting force, holding force and pressure

acted on lifting eye connecting gate hoist and gate (or sag rod, automatic hooking

beam).

6.0.3 Running load

Running load refers to vertical load, excepting self-weight, beared by mobile gate

hoist during operation, such as gate weight or weight of other materials.

6.0.4 Horizontal load1. Running inertia force

Running inertia force refers to the inertia force generated by weight of gate hoist,

trolley and running load during start or stop of running mechanism. Considering

structural dynamic effect of gate hoist or trolley during sudden start or variation of

driving force, running inertia force shall be 1.5 times result of weight multiplying

running acceleration, but shall not exceed adhesive force between driving wheel and

track. For acceleration (deceleration), see Annex B.

2. Horizontal force during rotation of slewing hoist

During movement of slewing machine of slewing hoist, horizontal force generated by

hoisting weight (including wind power, inertia force generated by start and centrifugal

force during rotation) shall be calculated according to horizontal force generated by

inclination between carrying rope and plump line.

Under normal conditions, during calculation of drift angle of carrying rope of motor

power, aI = (0.25 - 0.3)aII; during calculation of fatigue and abrasion mechanical parts,

aI = (0.3 - 0.4)aII; during calculation of the mechanical strength and anti-overturn

stability, the maximum angle of drift of carrying rope shall be a II; where n>0.33r/min,

aII=4 degrees; where n≤0.33r/min, aII=2 degrees. Generally, centrifugal force of self

weight of slewing hoist can be neglected.

In calculation of metallic structure, horizontal force generated by slewing hoist andhoisting weight (suspended weight) during start or stop of slewing hoist shall be 1.5

times result of the weight multiplying acceleration of the weight center (centrifugal

force generated by weight of the slewing hoist is ignored generally). Here, wind

power acting on hoisting weight shall be calculated separately and shall be overlapped

along the worst direction. When the calculated horizontal force of hoisting weight is

bigger than horizontal force calculated according to the maximum angle of drift aII,

value of acceleration is recommended to reduce.

3. Horizontal lateral force generated during oblique running of gate hoist

For horizontal lateral force generated during oblique running of gate-type, bridge-type

and platform hoist, see Annex C.



6.0.5 Impact load

1. Impact load generated by mobile gate hoist on buffer shall be calculated according

to practical dynamic energy generated practical impact speed of bumping limit switch,

but impact speed shall not be less than 50% of rated running speed.

Impact load of fixed connect of buffer and buffer arresting device shall be calculatedaccording to impact condition of rated running speed.

2. During calculation of impact load, kinetic energy of hoisting weight will not be

considered for gate hoist whose hoisting weight can swing freely. But hoisting weight

shall be considered for gate hoist having guide frame to limit hoisting weight from

swinging.

6.0.6 Wind load

1. Exposed mobile gate hoist shall consider wind load. Wind load can be divided into

working-state wind load and off-working-state wind load. Working-state wind load

refers to the maximum calculated wind power that gate hoist can bear in normal

operation. Off-working-state wind load refers to the maximum calculated wind power that gate hoist can bear under off-working condition.

2. Wind load shall be calculated according to formula 6.0.6-1:

Pw＝CK hqA (6.0.6-1)

Where,

Pw refers to wind load acting on gate hoist or hosting weight, N;

C refers to wind coefficient;

K h refers to variation coefficient of wind pressure;

q refers to calculated wind pressure, N/m2;

A refers to windward area, which is vertical to wind direction, of gate hoist or hoisting

weight, m2.

In the above calculation, the worst condition action of wind power on gate hoist shall

be adopted.

3. Calculated wind pressure can be calculated according to formula 6.0.6-2:

q ＝ 0.613v2 (6.0.6-2)

Where,

v refers to calculation wind speed, m/s.

Calculation wind pressure shall be determined according to calculation wind speed at

a height where is 10m from the datum plane. Off-working-state calculation wind

pressure of mobile gate hoist shall be calculated according to that the datum plane isthe lower running level.

Calculation wind pressure can be divided into three types, such as q I, qII and qIII.

Among these three types, qI refers to calculation wind pressure of gate hoist under

normal working state, and it can be used for drag calculation during selection of motor

power and verification of heat-exerting of mechanical components; qII refers to the

maximum wind pressure in working state, and it can be used to calculate strength,

rigidity and stability of mechanical components and to verify overload capacity of

drive device and anti-overturn stability of full machine in working state; qIII refers to

calculation wind pressure in off-working state, and it can be used to verify strength

and anti-overturn stability of mechanical components and metallic structure of gate



hoist and for design calculation of wind-prevention and slide-prevent device and

anchorage of gate hoist.

Calculation wind pressures of gate hoist are listed in Table 6.0.6-1. If local weather

data are available, the calculation wind pressure shall be calculated according to the

most-frequent maximum wind speed provided in local weather data.4. Altitude variation coefficient of wind pressure K h

Working state calculation wind pressure of gate hoist shall not consider variation of

altitude (K h=1). Variation coefficient K h of wind pressure following altitude in

off-working state shall be calculated according to formula 6.0.6-3 and 6.0.6-4.

For land: K h = (h/10)0.3 (6.0.6-3)

For island and sea K h = (h/10)0.2 (6.0.6-4)

Where,

h refers to height from calculation point to datum plane, m.

In the calculation, the height can be divided into isotonic wind segment at every 20m,

and then using the coefficient K h of height of midpoint at each segment to multiplythe calculation wind pressure.

Table 6.0.6-1 Calculation Wind Pressure (N/m2)

Calculation wind pressure

in working state

Calculation wind pressure in

off-working stateRegion

qI qII qIII

Inland 150 500-600

Coastal area 250 600-1000

Taiwan Province and

Hainan Province

0.6qII

250 1500

Note: 1. Coastal area refers to land or island within 100Km far from coastline.

2. qII is recommended to adopt small value in inland of North China, Middle

China and South China; to adopt big value in northwest, southwest and

northeast of China, and Shanghai shall be taken as a border in costal area,

so qII shall adopt 800N/m2 in Shanghai, adopt small value in costal area

north of Shanghai and adopt big value in costal area south of Shanghai; qII

value of off-working-state wind pressure of gate hoist used at areas where

are usually suffered from storm, such as Zhanjiang, or where there are

frequent light wind, shall be calculated by formula 6.0.6-2 according to

yearly maximum wind speed recorded in local weather data.

3. Where wind pressure qII = 150N/m2, equivalent wind speed is 15.6m/s;

where wind pressure qII = 250N/m2, equivalent wind speed is 20.19m/s.

5. Wind coefficient C

1) for wind coefficient C of single-slice structure and single-piece object of gate hoist,

see Table 6.0.6-2.

2) For space structure with two or more pieces, the wind coefficient can adopt the

wind coefficient of single-piece structure. For calculation of windward area, see

Annex D.3) Wind load of space truss with triangle cross section can adopt 1.25 times wind load



on projected area of truss vertical to wind.

4) When wind direction and structure form a angle, wind load on structure can be

calculated by dividing the wind load into two forces along two directions according to

the angle formed.

Table 6.0.6-2 Wind Coefficient C of Single-slice Structure No. Structural type C

1 Plane girder made of molded steel (solidity ratio ψ=0.3 - 0.6) 1.6

2Molded steel, steel plate, molded steel girder, steel

plate girder and box-section componentL/h

5

10

20

30

40

50

1.3

1.4

1.6

1.7

1.8

1.9

3 Circular pipe and tubular structure Qd2

≤1

≤3

7

10

≥13

4Closed driver's cab, machine room, balancing weight, steel rope and

objects.

1.1 -

1.2

Note: 1. In this table, L refers to length of structure or structural component, h refers

to height of windward face, m and q refer to calculation wind pressure (see

Table 6.0.6-1) (in N/m2); d refers to exterior caliber of pipe (in m);

2. When driver's cab is set on ground, C = 1.1, when it is suspended over ground, C = 1.2.

6.0.7 Temperature load

Generally, temperature load is not considered.

6.0.8 Installation load

During design of gate hoist, load generated during installation must be considered.

During installation of exposed gate hoist, wind pressure shall adopt 100N/m2.

6.0.9 Snow load

Snow load is only considered at area where there is snow frequently, and its value

shall be determined according to local relevant data.

6.0.10 Gradient load

If gate hoist is movable on track, when installation gradient is not greater than 0.3#,

gradient load can not be considered, otherwise, gradient load shall be calculated

according to practical gradient.

6.0.11 Earthquake load

When basic intensity of earthquake at area where gate hoist is used is equal to or

greater than 7 degrees, horizontal earthquake load shall be considered.

6.0.12 Test load

Before gate hoist is used, dynamic load and static load tests shall be carried out. Thetesting field shall be solid and plane, and wind speed shall not exceed 8.3m/s



generally. Dynamic test shall adopt 110% of rated load, and static test shall adopt

125% of rated load. The test shall be carried out to the worst position of the gate hoist.

Where there are special requirements, special consideration can be taken.

Large mobile gate hoist can also adopt hydraulic dynamometer to carry out the test.

During the test, testing regulations must be established to regulate load-adding order and methods which shall be observed.



7. Material

7.1 Casting Material

7.1.1 Carbon steel casting shall adopt ZG230-450, ZF270-500, ZG310-570 and

ZG340-640 stipulated in GB/T 11352.7.1.2 Alloy steel casting shall adopt ZG35CrMo, ZG42CrMo, ZG40crz65Mn,

ZG40Mn2 and ZG50Mn2 regulated in JB/ZQ4297.

7.1.3 Gray pig iron casting shall adopt HTl50, HT200 and HT250 stipulated in GB/T

9439.

7.1.4 Ductile cast iron shall adopt QT450-10 and QT500-7 stipulated in GB/T 1348.

7.1.5 Copper-alloy casting shall adopt ZCuSn5Pb5Zn5, ZCuSn10Pb1, ZCuA110Fe3,

ZCuA110Fe, 3Mn2, ZCuZn38Mn2Pb2 and ZCuZn25A16Fe3Mn3 stipulated in GB/T

1176.

7.2 Forging

7.2.1 Carbon steel forging shall adopt 20, 25, 35, 45, 50Mn and 65Mn stipulated inGB/T 699.

7.2.2 Alloy steel forging shall adopt relevant materials stipulated in GB/T 3077.

7.2.3 Stainless steel forging shall adopt relevant material stipulated in JB/ZQ 4295.

7.3 Structural Metallic Material

7.3.1 Generally, structural metallic material shall adopt 0235 stipulated in GB/T 700

or Q345 stipulated in GB/T 1591.

7.3.2 Main bearing material shall adopt Q235C or Q345C.

7.3.3 When temperature at local area where the gate hoist is used is equal to or lower

than -20℃, Q235D or Q345D shall be adopted.

7.4 Joint Material

7.4.1 Welding material

1. Welding rod of manual welding shall adopt relevant types stipulated in GB/T 5117

and GB/T 5118. Selection of type of welding rod shall conform to strength of main

metal.

2. Automatic and semi-automatic welding shall adopt welding wire and welding flux

shall conform to strength of main metal.

7.4.2 Riveting material

Generally, riveting material shall adopt ML2, ML3, Q235 and Q215 stipulated in

GB/T 116i.7.4.3 Bolting

1. Common bolt

Materials of bolt and stud shall comply with provisions of GB/T 3098.1 and GB/T

3098.3, and nut material shall comply with provisions of GB/T 3098.2 and GB/T

3098.4.

2. Stainless steel bolt

Materials of stainless steel bolt, screw, stud and nut shall comply with provisions of

GB/T 3098.6.

3. High-strength bolt

Materials of high-strength bolt, nut and washer shall comply with provisions of GB/T



1231 and GB/T 3633.



8. Mechanism

8.1 Hoisting Mechanism

8.1.1 Electromotor

1. Static power of mechanism shall be calculated according to hoisting load, weight of hoisting tools, rated hoisting speed and mechanism efficiency, and electromotor shall

be selected according to static power, working mode, load duration rate and load

duration. Generally, electromotor can not go through verification of overload and

heat-generation.

1. Static power of mechanism can also be calculated according to equivalent hoisting

load, weight of hoisting tools, rated hoisting speed and mechanism efficiency, and

electromotor can also be selected according to static power, working mode, load

duration rate or load duration. In this case, electromotor shall go through verification

of overload and heat generation. For verification methods, see Annex J and K.

2. Except for hydraulic gate hoist, hoisting mechanism is recommended to selectmetallurgy and hoisting motor according to short-term (or intermittent) working

system. Pump unit of hydraulic gate hoist can select asynchronous motor without

speed-regulation requirements according to start with zero load.

3. Except for fast gate hoist, mean acceleration of mechanism shall not be less than

0.3m/s2.

8.1.2 Detent

Each independent drive device shall be equipped with a supporting detent. And

braking safety coefficients are as follows:

1. If there is one set drive device and one detent, braking safety coefficient of the

detent shall not be less than 1.75.

2. If there is one drive device and two detents, braking safety coefficient of each

detent shall be calculated according to total braking moment and shall not be less than

1.25;

3. If there are two sets of drive devices having rigid connection and one detent is set

for each, braking safety coefficient of each detent shall be calculated according to

total braking moment and shall not be less than 1.25.

4. If there are two sets of drive devices having rigid connection and two detents are set

for each, safety coefficient of each detent shall be calculated according to total

braking moment and shall not be less than 1.1.Deceleration caused by common braking shall be less than 0.3m/s2.

8.1.3 Decelerator

Relevant decelerator shall be selected according to calculation load and total

transmission ratio of the hoisting mechanism. Generally, decelerator of winch-type,

chain-type and mobile gate hoist shall be composed of standard decelerator and

open-gear transmission. Single-class transmission ratio of open gear is recommended

not to exceed 6.3.

8.2 Running Mechanism

8.2.1 Determination of static running resistance

Static running resistance includes frictional resistance, ramp resistance and wind



resistance.

Frictional resistance includes resistance caused by friction between wheel and track

during running of gate hoist with load (self weight of gate), frictional resistance in

wheel bearing and additional resistance between wheel rim and track side. Generally,

the aforesaid third resistance is calculated according to the first and second frictionalresistances multiply a additional coefficient.

Ramp resistance refers to the resistance generated during mechanism with full load

travels along a gradient.

Wind resistance refers to resistance caused by calculation wind pressure on exposed

gate hoist in normal working state.

8.2.2 Electromotor

Static power of mechanism shall be calculated according to static running resistance,

running speed and mechanism efficiency. Electromotor shall be selected according to

static power of mechanism, working mode of electromotor and load duration rate.

Where inertia is relative large, inertia force shall also be considered.Generally, electromotor shall go through verification of overload and heat generation,

and value of acceleration shall be controlled. For verification method, see Annex K

and L.

Generally, value of mean acceleration caused during start of mechanism can be

adopted according to Annex B.

8.2.3 Detent

Total braking moment transferred from braking moment of running mechanism and

running minimum frictional resistance (excepting frictional resistance between wheel

rim and track side) to the brake axle shall be able to satisfy that gate hoist or trolley

with running load, down the wind and downhill conditions can be stopped within

specific time limit, but selection of detent shall guarantee that the braking time will

not cause track-slip between drive wheel and track.

8.2.4 Track-slip verification

Generally, main drive wheel shall not slip on track during start or braking of running

mechanism. During verification, adherence coefficient between steel wheel and track

shall adopt 0.12 for outdoor work; 0.15 for indoor work; and 0.2-0.258 when there are

sands on steel track.

8.3 Turning Mechanism

8.3.1 Equivalent static resistance momentEquivalent static resistance moment of turning mechanism includes frictional

resistance moment, equivalent wind resistance moment and ramp resistance moment

in normal working state.

8.3.2 Electromotor

Required equivalent power shall be calculated according to equivalent static

resistance moment, turning speed and mechanism efficiency of turning mechanism,

and electromotor shall be selected according to equivalent power, working mode of

electromotor and load duration rate of the mechanism.

Primarily selected electromotor of turning mechanism must go through verification of

overload and starting acceleration, which shall be within 0.1m/s2 - 0.3m/s2 generally.



8.2.3 Detent

Braking moment of detent of turning mechanism shall be able to stop turning part

under the worst working state and the maximum turning radius, and braking

deceleration shall be within 0.1m/s2 – 0.3m/s2 generally.

8.3.4 Limit moment rotating jointTransmission mechanism that has self-locking possibility shall be equipped with limit

moment rotating joint. If non-self-locking mechanism is not equipped with limit

moment rotating joint, transmission mechanism shall go through verification of static

strength in accident state.

8.4 Hydraulic System

8.4.1 Arrangement of hydraulic system

1. Except for specific components, equipments of hydraulic system shall be arranged

in machine room, where fire protection, ventilation, moisture-proof, insulation,

flood-proof and drainage measures shall be considered.

2. Arrangement of various hydraulic components and valve shall be as neat andconvenient as possible. Indication meter and gauge and hydraulic components

(overflow valve, pressure meter switch and oil filter) requiring adjustment or

supervision shall be arranged at a position where is convenient for observation and

operation.

3. Oil purifier is recommended to be adopted.

8.4.2 Hydraulic system shall go through verification of pressure loss. Where here are

frequent work, heat generation shall be verified, and oil temperature is recommended

not be exceed 50℃.

8.4.3 Hydraulic system shall also go through calculation of leakage and hydrodynamic

shock.

8.4.4 Oil tank:

1. Volume of oil tank shall satisfy working requirements of gate hoist and storage of

hydraulic oil.

2. If electromotor unit of oil pump is arranged on the tope of oil tank, top plate of the

oil tank shall have enough rigidity.

3. Structural design of oil tank shall consider filling and discharging of hydraulic oil

and cleaning of oil tank. Oil pointer shall be set at easily-visible position on tank wall,

and the highest and lowest oil level shall also be marked. Bottom of the oil tank shall

be made into a gradient oblique to oil outlet.4. Oil suction pipe and oil return pipe shall be as far as possible from each other and

shall be isolated by clapboard. Height of the clapboard shall not be lower than 3/4

height from the highest oil level to tank bottom. If sieve is set on the clapboard, the

clapboard shall be higher than the highest oil level.

5. Oil suction pipe and oil return pipe shall be inserted lower than the lowest oil level,

and distance from the oil suction pipe to tank bottom shall not be less than 2 time pipe

caliber, and to tank wall shall not be less than 3 time pipe caliber. The lowest oil level

shall be 100mm higher than the oil suction pipe and shall be larger than 3 times pipe

caliber. Distance from oil return pipe to tank bottom shall be less than 2 times of pipe

caliber. Pipe ends shall be obliquely cut with 45 degree, and oil outlet shall face tank



wall.

6. Oil tank shall adopt stainless steel.

7. Where oil re-filling tank is set, volume, setting elevation, pipeline joint and caliber

of oil re-filling tank shall be able to guarantee sufficient oil filling at upper cavity

when hydraulic cylinder piston drops.8. If hydraulic gate hoist is set in cold region and will be operated in winter, heating

device and thermometer are recommended to be set. During operation of heating

device, local overheating of hydraulic oil shall be prevented.

9. Vent with air filter, oil filling orifice with filter screen and magnetic device shall be

set on oil tank.

8.4.5 Hydraulic oil

1. Requirement of hydraulic oil

1) Hydraulic work oil shall have certain viscosity and favorable viscosity-temperature

characteristics, and petroleum-type hydraulic oil is generally adopted.

2) Hydraulic work oil shall have the following characteristics, such as favorablelubrication, anti-oxidation, corrosion-free, fire resistance, anti-emulsification,

damage-free for sealing material and shall have certain foam-eliminating capacity.

3) Hydraulic work oil shall be pure and shall not have mechanical impurities and

water. Cleanness of hydraulic oil shall reach class 7-9 of NASl638 standard or class

16/13 - 18/15 of GB/T 14039. Servo system shall be selected according to

requirements of valve block.

2. Dynamic viscosity of work oil shall be selected according to type of oil pump,

working temperature and system pressure, see Table 8.4.5.

3. If hydraulic gate hoist is set in low-temperature region and will be used in all

seasons, when oil cylinder is arranged outdoor and there is no equipment to heat oil

liquid, freezing point of hydraulic oil shall be at least 15℃ - 20℃ lower than the

lowest environmental temperature.

Table 8.4.5 Selection of Oil Type and Viscosity according to Working

Temperature Range

Movement

viscosity/(mm2/s)Pump type Pressure

5℃ -

40℃

40℃ -

80℃

Type and viscosity class of

oil applicable

vane pump

Below7MPa

Above

7MPa

30 – 50

50 - 70

40 – 75

55 - 90

HM oil, 32, 46, 68

HM oil, 46, 68, 10

Gear pump 30 - 70 95 - 165

HL oil, (HM for medium

and high pressures), 32, 46,

68, 100, 150

radial-plunger

pump30 – 50 65 - 240

HL oil, (HM for medium


68, 100, 150axial plug pump 40 70 - 150 HL oil, (HM for medium




68, 100, 150

Note: 1. 5℃-40℃ and 40℃-80℃ are working temperature range of hydraulic system.

2. Hv shall be adopted in cold area and Hs shall be adopted in chilliness area.

3. Where there are gunmetal components and silvered components, attentionshall be paid to selection of HM oil, and ashless HM oil or low-zinc HM oil

shall be adopted.

8.4.6 Filter

1. Filtration precision of filter in hydraulic system shall be determined according to

filtration precision requirements of pump and value samples that have been selected.

2. Filter is recommended to be arranged at oil return mouth, and filterability shall be

greater than 3 times oil return capacity of oil pump. If filter is arranged at oil suction

mouth, filterability of oil suction filter shall be greater than 5 times oil suction

capacity of oil pump. Filterability of pressure filter shall be greater than 2 times oil

passing capacity. Filter is recommended to have pressure difference signal transmitter

and bypath relief valve.

3. Air filter set on oil tank shall have de-humidity function.

8.4.7 Hydraulic pipeline

1. Efforts shall be made to guarantee short pipe, less bending and neat arrangement,

and bending degree shall not be less than 90 degree. The minimum curvature shall not

exceed 3 times external caliber generally, and high-pressure and low-pressure pipes

shall be divided by obvious different colors.

2. If hose is adopted, the hose shall not be tensioned or tortured, and shall not abradewith other objects during movement. Length of straight part from end to bending part

shall not be less than 6 times hose caliber, and bending radius shall not be less than 10

times external hose caliber.

3. Oil pipe shall adopt stainless steel seamless pipe. For calculation of relevant

diameter and wall thickness, see Annex H.

4. After installation and before debugging of hydraulic pipeline system, rinsing device

shall be adopted to rinse oil liquid circularly. After circular rinsing, cleanness of

pipeline system shall be able to reach requirements of item 3 of clause 1 in article

8.4.5.

5. Arrangement space among pipes shall be able to satisfy requirements of installation,operation and maintenance of pipe, valve and flange.

6. During arrangement of pipeline, manual stop valve shall be equipped at connection

of pump station and hydraulic cylinder.

8.5 Calculation Principle of Parts

8.5.1 Calculation method

Strength calculation includes static strength calculation and fatigue strength

calculation.

Strength calculation methods refer to permissible stress method and safety factor

method.Some parts (such as screw rod) shall also go through calculation of rigidity and



stability.

Long high-speed transmission shaft shall also go through verification of critical speed.

8.5.2 Calculation load

1. Fatigue calculation basic load:

1) Fatigue calculation basic load borne by parts of hoisting mechanism shall becalculated by 0.6-1 time moment (or force) transmitted by hoisting force to the

calculation parts according to type of gate and working property. And fatigue

calculation basic load of parts on high-speed shaft shall be calculated according to

1.3-1.4 times rated moment of electromotor.

2) Fatigue calculation basic load of parts of running and returning mechanism shall be

the total moment of inertia moment and static resistance moment borne by parts

during starting of mechanism. And it can be estimated according to formula 8.5.2-1:

MImax = (1 2～2.0)Mn (8.5.2-1)

Where,

MIma refers to fatigue calculation basic load moment of calculation part, N·m;Mn refers to moment transmitted from rated moment of electromotor to calculation

part, N·m。

Coefficients 1.2-2.0 refer to rigidity dynamic load coefficients, being related to the

ratio of drive characteristics of electromotor and rotation inertia moment of

calculation part.

2. The maximum working load shall be used to calculate static strength of calculation

part.

1) The maximum load of hoisting mechanism shall adopt 1-1.2 times moment (or

force) transmitted from hoisting force on to calculation part, and part on high-speed

shaft shall adopt the result of rated moment of electromotor multiplying 1.3-1.4. In

special cases, it can be verified according to the maximum running torque of

electromotor, and permissible stress of part can adopt 0.9σs of material.

2) If the maximum working load of running and returning mechanism is adopted

during starting or braking of mechanism, the maximum oscillatory torque borne by

part can be estimated according to formula 8.5.2-2:

MIImax = (1.1 - 1.5)Mnmax (8.5.2-2)

Where,

MIImax refers to the maximum oscillatory torque of calculation part, N●m.

When elastic vibration is considered, the biggest one among augmenting coefficientof moment, system elasticity and damp shall adopt the smallest value.

3. The maximum off-working load shall be determined by combination of maximum

off-working wind load and weight of equipment. maximum off-working load belongs

to non-frequent load and it can be used to verify static strength of some components.

4. Special Load:

1) Buffer impact load: it refers to dynamic load generated during buffer impacts

running mechanism of mobile gate hoist. It can be estimated according to formula

8.5.2-3:

MIIImax = 0.25(R/i)Σ PImax (8 5.2-3)

Where,



MIIImax refers to moment generated during buffer impact on to drive shaft of running

mechanism, N●m;

R refers to wheel radius, m;

i refers to total transmission ratio of running mechanism;

ΣPImax refers to the total maximum wheel pressure during running of drive wheel of calculation transmission mechanism, N.

2) Installation load: it shall comply with provisions of 6.0.8.

3) Test load: it shall comply with provisions of 6.0.12.

8.5.3 Number of stress cycles

During calculation of fatigue strength of transmission parts, number of stress cycles

shall be calculated within required design service life. If stress variation is absolute

value of 10% of maximum stress, number of stress cycles may not be calculated.

Number of stress cycles N can be calculated according to formula 8.5.3:

N = FZ (8.5 3)

Where,F refers to number of stress cycles of part per hour;

Z refers to total design service life of part, h.

Generally, service life of mechanism parts shall be calculated according to design

service life of mechanism. In certain cases, due to economic consideration or

technical limitation, design service life of some parts may be different from design

service life of mechanism.

8.5.4 Strength limitation

During calculation of static strength, yielding limitation of material that has favorable

plasticity may be adopted as yielding point of parts.

If ratio of yielding limitation of material σs to extension strength σ b is greater than 0.7,

in order to avoid brittle rupture due to exceeding yielding limitation of material, it is

stipulated that imagined yielding point shall be calculated according to formula

8.5.4-1 and 8.5.4-2:

8.5.5 Fatigue strength limitation

Generally, fatigue strength limitation is obtained through verification or calculation.Value of fatigue strength limitation of parts depends on:

1. Characteristics of stress cycle (σmin/σmax)

2. Quality of material;

3. Shape and dimension change of parts;

4. size of parts;

5. surface condition of parts.

8.5.6 Strength verification

Mechanical transmission parts must go through strength verification. But due to that

load duration is short and rare and may not cause fatigue damage or excessive wear,

so fatigue and antiwear verification can not be carried out. Strength verification shall



satisfy formula 8.5.6:

Calculated stress≤ tcoefficiensafetystrength

partof limitationstrengthfatigueor pointyielding(8.5.6)

Strength safety coefficient shall be adopted according to provisions of Table 8.5.6.8.5.7 Abrasion

For parts that are often exposed to abrasion in operation, wearing amount of the

frictional face shall be guaranteed within allowed range. For detent, clutch and sliding

bearing, pressure intensity p on unit area of section and characteristic coefficient pv (p

multiply related speed to frictional surface) shall be verified, so as to guarantee its

wearing amount within allowable value. For allowable physical quantity of material

of frictional surface, see Annex E.

Table 8.5.6 Strength Safety Coefficient

Static strength verification

Calculation contentFatigue

verification nI

Maximum

working load

nII

Maximum

off-working load,

special load nIII

Forging and

rolling

pieces

1.6 1.6 1.4Hoisting

mechanismCasting

steel1.8 1.8 1.6

Forging androlling

pieces

1.4 1.4 1.2Returning,

running

mechanisms Casting

steel1.6 1.6 1.4

Note: For gate hoist of special importance, safety coefficient can be appropriately

increased.

8.6 Component Design

8.6.1 Lifting hook, lifting folk and lifting shaft

Generally, lifting hook and lifting folk shall adopt high-quality low-carbon killed steel

or low-carbon alloy steel.

Lifting shaft shall adopt high-quality carbon steel or alloy constructional steel.

During design of lifting hook or lifting folk, plane elasticity bent lever method shall

be adopted for calculation. Generally, lifting hook or lifting folk can be selected

according to hoisting force and working class.

Lifting shaft shall consider the worst condition, and its calculation load shall be the

maximum working load and its working state can adopt static load.

8.6.2 Steel cable, pulley and drum

1. Generally, steel cable of gate hoist shall adopt galvanized steel cable (especially inunderwater working condition), and linear contact lay steel cable shall be adopted



preferentially. Multiple-wound steel cable is recommended to adopt metallic-corer

steel cable; and mono-wound steel cable that is often submerged under water is

recommended to adopt asbestos-core steel cable.

Strength of steel cable shall satisfy requirements of formula 8.6.2-1:

F0 ≥ nS (8.6.2-1)Where,

F0 refers to failure pull of steel cable adopted, N;

n refers to the minimum safety coefficient of steel cable, see Table 8.6.2-1;

S refers to the maximum static working pull of steel cable, N; when lift head is larger

than 50m, weight of steel cable shall also be considered.

The maximum declination angle of steel cable winding in and out from pulley groove

shall not exceed 3.5 degree generally.

Where steel cable is wound in or pulled out from drum, deviation angle of steel cable

from two sides of screw shall not exceed 3.5 degree generally.

For single drum or multiple-wound drum, angle that steel cable deviates from vertical plane of drum is recommended not to exceed 2 degree.

2. Drum calculated according to diameter of steel cable and minimum coiling

diameter of pulley shall be calculated according to formula 8.6.2-2:

D0min = ed (8.6.2-2)

Where,

e refers to coefficient related to working class of mechanism, see Table 8.6.2-2;

d refers to diameter of steel cable, mm.

Diameter of balanced pulley shall adopt 0.8 time D0min.

Table 8.6.2-1 Minimum safety Coefficient of Steel Cable

Table 8.6.2-2 Coefficient of Drum and Pulley e

3. Pulley and drum shall be made of cast iron generally, and its number shall not be

less than HT200 stipulated in GB/T 9439. Gate hoist with large capacity is

recommended to adopt cast steel or welding pulley; drum is commended to adopt

welding drum or progressively-welded cast steel.

4. Strength calculation and stability verification of drum:

If L≤3D, only maximum pressure stress on drum wall surface can be calculated.

If L>3D, besides calculation pressure stress, combined stress generated by bending



moment and torque shall also be verified.

If D≥1200mm and L>2D, besides strength calculation, drum wall shall also go

through stability verification. Where, D refers to bottom diameter of drum groove,

mm; L refers to drum length, mm.

For strength calculation and stability verification of drum, see Annex G.8.6.3 Gear and worm gear transmission

1. Common gear material

Small gear shall adopt high-quality carbon steel or alloy constructional steel; and big

gear shall adopt cast carbon steel or alloy cast steel. Material selection and heat

treatment hardness shall match with gears.

Usual materials of worm gear: worm wheel shall adopt copper base alloy or zinc base

alloy, and small equipment and equipment used to transmit small load can also adopt

cast iron; worm rod shall adopt high-quality carbon steel or alloy constructional steel.

2. Where gear adopts soft tooth surface or half-hard tooth surface, hardness of tooth

surface of small gear shall be 30HB higher than the hardness of big gear; when gear adopts hard tooth surface, hardness of tooth surface of small and big gear shall be

basically identical.

3. Gear transmission shall calculate contact strength of tooth surface and bending

strength of gear. For closed-type gear transmission, tooth surface is recommended to

adopt half-hard tooth surface.

Worm gear is mainly used in mechanism (such as returning mechanism and running

mechanism) having large transmission rate and close structural arrangement. Strength

calculation of gear worm shall be based on calculation contact strength on tooth

surface, bending strength of worm wheel tooth shall go through verification; if worm

rod is also used as transmission shaft, strength calculation and rigidity calculation

shall be carried out on shaft basis.

8.6.4 Shaft

1. Shaft material: usual material of shaft shall adopt medium carbon steel; and the

most-commonly-used material is 45 stipulated in GB/T 699, and 35SiMn, 42SiMn,

40MnB, 40Cr and 40 CrNi alloy steel can also be adopted.

2. Original size of shaft can go through preliminary strength calculation according to

permissible stress method. Shaft structure can be determined according to the

preliminary size obtained and all necessary factors, and then practical safety

coefficient of dangerous section shall be determined and its rigidity shall becalculated.

3. Critical rotation speed of shaft: if rotation speed of long transmission shaft exceed

400r/min, beside calculation of strength and rigidity, critical rotation speed shall also

be verified and shall satisfy requirements of formula 8.6.4-1:

Where,



nmax refers to practical maximum rotation speed of shaft, r/min;

ncr refers to critical rotation speed, r/min;

d1 refers to interior diameter of shaft, mm; when solid shaft is adopted, d 1=0;

d2 refers to exterior diameter of shaft, mm;

L refers to supporting space of shaft, m.4. Calculation of shaft rigidity can adopt the following values:

1) Maximum deflection shall not exceed 0.0003 time space among supporting points

generally.

2) Maximum deflection of shaft with gear shall not exceed 0.01-0.03 time gear

module generally.

3) Maximum deflection angle caused by deflection at supporting point shall not

exceed 0.001 rad generally.

4) Generally, allowable torsion angle shall adopt ψ≤ °5.0 /m.

8.6.5 Decelerator 1. If standard decelerator is adopted, total design service life shall conform to working

class of relevant mechanism where it belongs to. Decelerator shall be selected

according to rated load or rated power of electromotor or working conditions required.

When necessary, maximum radial load at output shaft of decelerator shall be verified.

2. During design of decelerator, load capacities (referring to contact strength of tooth

surface) of each transmission class shall be basically identical. Supporting axle of

decelerator gear shall have enough strength and rigidity, and type and size of gear

shall be selected according to weight and direction of load and application

requirements. Shell of decelerator shall have enough strength and rigidity.

3. Lubrication of decelerator shall adopt oil bath lubrication generally. If special oil

pump lubrication is adopted, high-speed meshing gear shall go through splash

lubrication before starting.

8.6.6 Coupling

If coupling is adopted on gate hoist, type shall be determined according to working

condition and then selection shall be made from standard specification table of

coupling according to transmission moment, shaft size and rotation speed, and

formula 8.6.6-1 shall be satisfied:

Mc ≤ Mt (8.6.6-1)

Mc ≤ nMIImax (8.6.6-2)Where,

Mc refers to calculation moment of coupling, and it shall be calculated according to

formula 8.6.6-1, N·m;

n refers to safety coefficient of coupling; for hoisting mechanism, n = 1.8; for other

mechanism, n = 1.5;

Mt - refers to rated moment listed in specification parameter of coupling, N·m;

MIImax – see clause 2 of 8.5.2.

8.6.7 Bearing

1. Generally, sliding bearing is used in low-speed and heavy-load transmission of gate

hoist, such as movable pulley block of high-lift gate hoist that is usually submerged



underwater, and sliding bearing may also be used to support drum. Bearing shall be

determined according to journal size, and result obtained through maximum unit

pressure P multiplying its relative linear speed against the rotation frictional surface,

namely pv value, shall be verified to not exceed p value and pv value. For p value and

pv value, see Annex E. [2. During selection of rolling bearing, the following items shall be given:

1) Generally, total design service life of bearing can be identical to working class of

mechanism, or one class lower then working class of mechanism where necessary.

2) Rotation speed of rolling part of bearing. rolling bearing whose rotation speed is

less than 10r/min shall only go through rated static load calculation.

3) Radial applied load.

4) Axial applied load.

5) Working condition and working state (property of working load, rotation housing

washer, humidity, type and supply method of lubricant).

6) Structural shape and overall size of bearing.According to the aforesaid conditions, equivalent dynamic load or equivalent static

load can be calculated. After calculation of required rated dynamic load or rated static

load, rolling bearing can be selected.

8.6.8 Load limiter

Gate hoist shall be equipped with reliable and adjustment-convenient hoisting load

limiter. If load on hoisting load limiter exceeds 10% of rated load, overload alarm

signal shall be made and power supply shall be cut off. Normal operation shall be able

to be recovered after correct load is obtained. If necessary, deficient load limiter can

be set.

Standard value of lifting force and holding force (or downward pressure) shall be

adjusted according to requirement of gate. If necessary, lifting force and holding force

(or downward pressure) can be limited separately.

Lever-type and centrifugal-type load limiters are often adopted. Electric protection

device and special electronic apparatus (such as electronic scale) shall be maintained

if they are used as overload protection device.

8.6.9 Indication and position control of lift head (travel)

1. Lift head (travel) indication: mechanical type or electronic type can be adopted, and

detection precision and display precision shall be determined according to operation

requirements and value of lift head (travel).2. Position control: gate hoist shall have extreme-position limiter, and other positions

(such as filling valve of gate) can be controlled according to concrete requirements.

When gate hoist reaches control position, power supply shall be cut off automatically

or alarm signal shall be given out.

Running mechanism shall be equipped with travel limiter. When big and small trolley

reach extreme positions, power supply shall be cut off automatically and alarm signal

shall be given out.

Returning mechanism having rotation angle requirement shall be equipped with

returning limiter, and when mechanism returns to extreme positions, power supply

shall be cut off automatically and alarm signal shall be given out.



8.6.10 Buffer

Buffer shall be designed according to impact kinetic energy (see 6.0.5). Buffer shall

be designed according to the maximum impact force generated during gate hoist runs

in rated speed, and strength safety coefficient shall be 1.15 under such condition.

Gate host can adopt spring buffer, rubber buffer and hydraulic buffer. Small gate hoistadopt spring buffer, but wooden buffer can also be adopted.

8.6.11 Wheel and track

1. Wheel material shall adopt 45, 65Mn stipulated in GB/T 699, ZG 340-640

stipulated in GB/T 11352, and ZG35CrMnSi and ZG34CrNiMo stipulated in JB/ZQ

4297.

2. Generally, diameter of wheel shall not exceed 1.25m. When rated running load is

carried, wheel tread shall be calculated according to fatigue; if maximum load is lifted,

wheel tread shall be calculated according to strength. For calculation of wheel tread,

see Annex G.

3. Medium and small gate hoist shall adopt P-type railway steel track generally, largegate hoist can adopt QU-type crane-special track. For strength calculation formula,

see Annex G. Track of electric block shall adopt rolled I bar.

8.6.12 Lift bolt and nut

Generally, lift bolt of screw rod gate hoist adopts Q275 stipulated in GB/T 700 and 35

and 45 stipulated in GB/T699.

Load bearing nut shall be made of cast bronze generally. And those having low

relative slip speed can adopt cast iron or ductile cast iron.

Screw thread shall adopt trapezoidal thread generally; in order to guarantee

self-locking, angle of lead α of screw middle line is recommended to be °4 ≤a≤ °5.4

1. Lift bolt: slenderness ratio of pressure screw rod λ≤ 200, tension screw rod λ≤250.

Slenderness ratio of important screw rod shall be appropriated reduced.

Conversion coefficient μ of calculation length of screw rod: when one end of screw

rod adopts swing joint and the other end adopts fixed joint, μ=0.7; when both ends of

screw rod adopt swing joint, μ=1.0.

Under pressure working conditions, screw rod shall go through stability verification.

Besides tension and pressure, screw rod also bear twisting moment. Screw rod of

oscillating-type screw rod gate hoist also bears bending moment. For calculation of

bending moment, see Annex G.

2. Load-bearing nut: working height H of nut shall be determined according toallowable bearing stress on screw surface. For relevant calculation, see Annex G.

8.6.13 Chain and chain wheel

Commonly-used load-bearing chain is piece-type hoisting chain. Material of pin and

chain plate of piece-type hoisting chain is recommended to adopt 45# or 50# steel,

and shall go through heat treatment.

Maximum allowable load of chain (including weight of chain) shall be:

Where,

p refers to breaking load of chain, N;



nr refers to safety coefficient; nr =5 - 5.5.

Single-segment chain shall go through breaking load test and assembled chains shall

go through load test. Testing load shall be equal to 50% of breaking load.

Chain wheel of piece-type hoisting chain is integrated with shaft generally, and

number chain wheel tooth is recommended to be 9 - 12. Chain wheel that is usuallyused underwater shall adopt sliding bearing and shall have anti-corrosion measures.

8.6.14 Oil Pump

Type of oil pump shall be determined according to requirements of system on

performance of oil pump. Specification of oil pump shall be determined according to

required maximum working pressure and maximum working flow of oil pump.

For maximum working pressure and maximum working flow of oil pump, see Annex

H.

8.6.15 Hydraulic components

1. Type of hydraulic components shall be determined according to working

requirements of hydraulic system, and its maximum working pressure and rated flowshall satisfy requirements of working conditions.

2. Overflow cock set to guarantee safety of hydraulic cylinder shall adopt

direct-action structure.

3. During selection of throttling valve and speed control valve, relevant characteristics,

such as regulating range and minimum stable flow shall be considered.

4. Electromagnet of electromagnetic directional valve or electro-hydraulic change

valve shall adopt direct-flow wet structure, and its working state is recommended to

be display by indication lamp.

5. Number of pressure gauge shall be determined according to requirements of

hydraulic system. If there are supervisory requirements, pressure sensor shall be

configured according to relevant requirements.

8.6.16 Hydraulic cylinder

1. Strength calculation of cylinder wall. Strength of cylinder wall shall be calculated

according to the following two conditions:

1) Section far enough from flange and supporting flange. Cylinder wall stress at this

position is longitudinal stress and hoop stress generated by working pressure in

cylinder;

2) Section connecting cylinder body and flange. Stress generated by working pressure

in cylinder at this position shall add longitudinal stress and hoop stress generated by bending moment meanly distributed on cylinder wall at flange.

Strength of cylinder wall can be calculated according to Annex H.

2. Main structural parameters of hydraulic cylinder can be determined according to

Annex H. Calculation length of piston rod shall be determined according to fixed

form of hydraulic cylinder, and for conversion coefficient of calculation length, see

Annex H. During calculation of slenderness ratio of piston rod, inertia moment is

recommended to be calculated according to rod having sudden variation, and

allowable slenderness ratio of piston rod is recommended to be less than 200 in

pressure, and shall be less than 250 in tension.

3. Longitudinal stability calculation:



1) For pressure piston rod, when calculation length L is greater than 10 times diameter

d (L refers to distance from supporting center of cylinder body to rod end connection

point when piston rod is fully pulled out), stability calculation shall be carried out.

2) Longitudinal stability of hydraulic cylinder shall be calculated under condition that

piston rod is fully pulled out and bears maximum downward pressure.3) For stability calculation of hydraulic cylinder, see Annex H.

4. Piston rod surface shall adopt chrome-plating anti-corrosion measure, and material

can adopt medium carbon steel, alloy steel and stainless steel.

5. Seal: generally, seal of hydraulic cylinder adopts V-type, O-type and Y-type seal

ring.

1) V-type combined seal rings are used for dynamic seal between piston and inner

wall of cylinder body, and piston rod and end cover.

2) O-type seal ring is generally used for static seal between end cover and cylinder

body, piston and piston rod.

3) Y-type seal ring can also be adopted for dynamic seal between piston and inner wall of cylinder body.

6. Dust ring shall be set at end where hydraulic cylinder piston rod is pulled out. If

necessary, impurity-scraping and ice-scraping rings can be adopted.



9. Structure

9.1 Calculation Principle

Permissible stress method is adopted for calculation in this code. Metallic structure of

gate hoist shall go through strength, stability and rigidity calculations, and shallsatisfy specified requirements. During calculation, plastic influence of material is not

considered generally, and fatigue strength will not be calculated.

Structure shall be calculated according to two load conditions: 1. Strength, rigidity

and stability will be calculated according to maximum working load; 2. Strength and

stability will be calculated according to maximum working load and special working

load.

9.2 Load Combination

Load combination stated in this article is applicable only to structural and connection

calculation of mobile gate hoist; for load combination, see Table 9.2.

Table 9.2 Load and Load Combination

Load combination Class ILoad combination

Class II Name of load

Ia Ib Ic Id Ie Ia Ib Ic Id

Self-weight load √ √ √ √ √ √ √ √ √

Hoisting load of main hoisting

mechanism√

Running load √ √ √

Hoisting inertia force √ √ √

Inertia force of trolley √ Wind load in working state √ √ √ √ √ √ √

Wind load in off-working state √

Lateral force caused by oblique

running√ √ √

Impact load √

Test load √

Earthquake load √

Hoisting load of auxiliary

hoisting mechanism√ √

Note: 1. Different combinations of load are used to calculate different position of

structure.

2. If temperature load, snow load, installation load and gradient load need to be

considered, they can be added to the load listed in this table.

9.3 Permissible Stress

9.3.1 Permissible stresses of structural materials shall be classified according to sizes

listed in Table 9.3.1.



Table 9.3.1 Size Classification of Steel

Thickness or diameter of steelGroup

Q235 Q345

I ≤16 ≤16

II >16-40 >16-25III >40-60 >25-36

IV >36-50

9.3.2 In load condition of class I, permissible stress of structural material shall be

adopted according to Table 9.3.2.

Table 9.3.2 Permissible Stress in Load Condition Class I N/mm

Type of stress symbol Q235 Q345

Tension, pressure,

bending[σ] 160 150 145 230 220 205 190

shear [τ] 95 90 85 135 130 120 110

Local compression

(abrade smoothly

and fix tightly)

[σcd] 240 240 220 350 330 310 290

Local

closely-connected

compression

[σcj] 120 115 110 175 165 155 145

Note: 1. Local pressure bearing refers to the condition where particle surface of

component web plate bears extrusion of local load or end face bears

pressure;2. Local close pressure bearing refers to small-mobility pressure stress hinged

on projection place of contract surface.

9.3.3 In class-I load condition, for permissible stress of welding joint, see Table 9.3.3.

9.3.4 For permissible stress of rivet, bolt and pin connections, see Table 9.3.4.

9.3.5 Permissible stress value of Table 9.3.2 - 9.3.4 shall be 15% higher than values in

the class-II load condition.



Table 9.3.3 Permissible Stress of Welding Joint under Class-I Load ConditionBuried arc automatic,

semi-automatic weldingand manual welding

using E43 welding rod

Buried arc automatic,semi-automatic welding and

manual welding using E50 weldingrod

Q235 Q345

Typeof

weldType of stress symbol

GroupI

GroupII

GroupIII

GroupI

GroupII

GroupIII

GroupIV

compression [σn] 160 150 145 230 220 205 190

Buried arch automaticwelding

[σ1] 160 150 145 230 220 205 190

Precisemethod

[σ1] 160 150 145 230 220 205 190

tension

Examinationof weld qualityof buried archautomatic or

semi-automaticmanualwelding

Commonmethod

[σ1] 135 120 115 200 190 175 165

Buttweld

Shear [τ] 95 90 85 165 130 120 110

corner fillet

Tension,compression

and shear [τt] 115 105 100 160 150 140 130

Note: 1. Common method for examination of welding joint refers to visual examination, measurement and hole-drilling examination; precise method refers to supplement examination by radiant ray, magnetic particle and ultrasonic on basis of commonmethod;

2. Permissible stress of overhead weld shall multiply 0.8;3. Permissible stress of field weld shall multiply 0.9;4. Where single side of single-angle welded component is connected, the connected side shall be any side of equal leg angle

steel and short side of unequal leg angle steel, and permissible stress of welding joint shall multiply 0.85.

Table 9.3.4 Permissible Stress of Rivet, Bolt and Pin Connection N/mm2 Steel grade of componentRivet, bolt, pin steel

grade Q235Type of connection

Type of stress symbolML2,ML5

Q235, 35 Group I Group II Group III

Shear [τ] 135 - - - -

Bearing [σc] - 320 300 290

Rivetconnection(type-I hole) Nail-head pulling [σ] 85 - - - -

Tension [σ] 125 - -

shear [τ] 125 - -

Finished bolt(type-I hole)

Common bolt

connectioncompression [σc] 290 275

Tension [σ] 125 - -

shear [τ] 90 - -Common bolt

connectioncompression [σc] 190 185

Bending [σ] 150 - -

Shear [τ] 90 - -Pin connection

Compression [σc] 190 185



Table 9.3.4 (Continue)

Steel grade of componentRivet, bolt, pinsteel grade

Q345Type of connection Type of stress symbol

ML2,ML5

Q235,35

Group I Group IIGroup

IIIGroup

IV

Shear [τ] 135 - - - -

Bearing [σc] 460 440 410 380

Rivetconnection(type-I hole) Nail-head pulling [σ] 85 - - - - -

Tension [σ] 125

shear [τ] 125

Finished bolt(type-I hole)

compression [σc] 420 395 370 345

Tension [σ] 125 - - - -shear [τ] 90 - - - -

Common boltconnection

compression [σc] 280 265 250 235

Bending [σ] 150 - - - -

Shear [τ] 90 - - - -Pin connection

Compression [σc] 280 265 250 235

Note: 1. Holes whose wall quality belong to the following conditions shall be classified as class I:- hole that is drilled on assembled structure according to design aperture;- holt that is drilled by drill jig on single part or component according to design aperture- hole that is firstly drilled or punched into a small hole on a single part and then is drilled on assembled

component to the design aperture.2. If sunk rivet or semi-sunk rivet is adopted, values listed in this table shall multiply 0.8;

3. For field-installed connection rivet, values listed in this table shall multiply 0.9.

9.4 Calculation of Strength of Structure and Connection Component

9.4.1 General structural calculation

Under tension, pressure, bending and torque condition, strength of structural

components of gate hoist can be calculated according to general strength calculation

formula, and calculation stress shall not be less than permissible stress.

When there is concentrated load on top flange of girder, local pressure stress of web

plate shall be calculated according to formula 9.4.1-1.

Where,

σm refers to local compression stress, N/mm2;

p refers to concentrated load, N;

δ refers to thickness of web plate, mm;

a refers to action length of concentrated load; a shall be block length for slide block

and be 50mm for wheel;

hy refers to distance from component top (without track) or track top (with track) to

upper edge of calculation height of web plate, mm.

When there are large positive stress σ, large shear stress τ and local pressure stress σm on the same calculation position, conversion stress shall also be verified according to



formula 9.4.1-2.

Where,

σ and σm shall carry their positive and negative sign separately.9.4.2 Strength calculation of structural component connected by high-strength bolt

Strength of axial tension and axial pressure structural components connected by

high-strength bolt shall be calculated according to formula 9.4.2-1.

Where,

N refers to axial force of component, N;Z refers to number of high-strength bolt through which component is connected to one

end of node plate or jointed plate;

Z2 refers to number of high-strength bolts on calculation section (bolts on the outmost

line);

A refers to net area of verification section, mm2.

9.4.3 Calculation of connection strength

1. Welding connection: when there is positive stress and shear stress at butt-welding

position, connection strength shall be calculated according to formula 9.4.3-1:

Where,

σh refers to conversion stress of weld, N/mm2;

[σ] refers to permissible stress of weld, N/mm2, see Table 9.3.3.

2. High-strength bolt connection

1) During anti-shear connection, permissible bearing force of each bolt shall be

calculated according to formula 9.4.3-2:

[P] = 0.7ZmfPg (9.4.3-2)

Where,[P] refers to permissible bearing force of each high-strength bolt, N;

Zm refers to frictional coefficient, and it shall be selected from Table 9.4.3-1;

Pg refers to pre-tension of high-strength bolt, N; it shall be selected from Table

9.4.3-2.

Coefficient 0.7 is multiplied so as to reduce impact of compression deformation of

connection component on pull.



Table 9.4.3-1 Frictional Coefficient f

Steel grade of

componentProcessing method of contract face of component at

connection positionQ235 Q345

Sandblast 0.45 0.55Painting inorganic zinc rich paint after sandblast 0.35 0.40

Red rust is generated after sandblast 0.45 0.55

Eliminating superficial rust with steel brush or rolling surface

without any treatment0.30 0.35

Table 9.4.3-2 Pre-pull of Each High-strength Bolt Pg kN

2) When high-strength bolt connection bears shear force on frictional surface and

external pull along stud shaft direction, permissible bearing force on each

high-strength bolts shall be calculated according to formula 9.4.3-2, but Pg shall be

substituted by (Pg-1.4Pt), where Pt refers to external pull borne by each high-strength

bolt along its axial direction, and this external pull shall not exceed 70 of pre-pull

Pg. )

3) Number Z of high-strength bolt required for connection shall be calculatedaccording to formula 9.4.3-3:

Z=N/[P] (9.4.3-3)

Where,

N refers to axial force on connection, N;

[P] refers to permissible load of one high-strength bolt, N.

9.5 Stability Calculation

9.5.1 Axial pressure component

1. Besides strength and rigidity conditions, axial pressure components shall also verify

whole stability and local stability.

2. Slenderness ratio of component:

1) Permissible slenderness ratio of components shall not exceed values listed in Table

9.5.1-1.

Table 9.5.1-1 Permissible Slenderness Ratio of Component (λ )

Name of ComponentTension

component

Compression

component

For chord member

of truss150 120Primary bearing structural

componentFor whole structure 180 150

Secondary bearing structural component (such asother rod of main truss and chord of auxiliary

200 150



truss)

Other component 350 250

2) When yielding point σs of steel material is higher than 350N/mm2, imagined

slenderness ratio λF of component can be adopted for calculation, and λF can becalculated according to formula 9.5.1:

Where,

σsrefers to yielding point of material, N/mm2.

3) When component is of composite cancelled structure, conversion slenderness ratio

of whole structural component can be calculated according to formulas listed in Table

9.5.1-2. For single piece of lacing-bar combined compression component, when

slenderness ratio is greater than conversion slenderness ratio, stability shall also be

calculated.

Table 9.5.1-2 Calculation Formula of Conversion Slenderness Ratio λ h of

Cancelled Component

ItemSurface shape of

component

Type of

lacing

material

Calculation formulaMeaning of

symbol

1Lacing

plate

λy refers to

slenderness ratio

of imaginaryaxis;

λ1 refers to

slenderness of

single-limb to 1:1

axis, its

calculation shall

adopt net

distance between

lacing plates

(rivet connection

component shall

adopt distance

between edge of

lacing plate and

center of rivet).

2Lacing

bar

A refers to total

gross sectional

area of all chord

rods cut fromsection of



component;

A1 refers to total

gross sectional

area of all

oblique lacing bars cut from

section of

component.

3Lacing plate

λ1 refers to

slenderness of

single-limb to 1:1

axis, its

calculation shall

adopt net

distance betweenlacing plates

(rivet connection

component shall

adopt distance

between edge of

lacing plate and

center of rivet).

4Lacing

bar

A1x refers to total

gross sectionalarea of all

oblique lacing

bars within plane

which is cut from

section of

component and

which is vertical

to x-x axis;

A1y refers to total

gross sectionalarea of all

oblique lacing

bars within plane

which is cut from

section of

component and

which is vertical

to y-y axis;



5Lacing

bar

θ refers to angle

between plane

where lacing bar

is and x axis.

Note: 1. Single limb slenderness ratio of lacing plate combination component shall not

exceed 40, and size of lacing plate shall comply with the following

provisions: width of lacing plate along longitudinal direction of column

shall not be less than 2/3 of distance between axial lines of limb component,

and thickness shall not be less than 1/40 of the distance, and shall not be

less than 6mm;

2. Obliquity between oblique lacing bar and axial line of structural component

shall be kept within 40-70 degrees.

9.5.2 Double-direction or single-direction compression-bending structural component

When structural components bear axial force and double-direction moment of strong

axis (X-axis) and weak axis (Y-axis), besides strength verification, stability shall also

be verified, and for calculation method, see Annex J.

9.5.3 Calculation of Whole Stability of Bending Structural Component

1. Whole stability of bending structural component can not be calculated, if one of the

following conditions is satisfied:

1) For structural component with box section, when ratio of sectional height andwidth between two web plates is not greater than 3; or the section can guarantee

lateral stiffness (such as space truss) of structure;

2) Rigid plates are laid on compression flange plate thickly and can resist against

torsion and horizontal displacement;

3) Ratio of free length l to width b of compression flange plate of freely-supported

beam with I-shaped cross is not greater than values listed in Table 9.5.3.

Table 9.5.3 l/b Value without Whole Stability Verification

h/δ b=100 h/δ b=50

h/b

Load is

added on

upper

flange

plate

Load is

added on

lower

flange

plate

No matter

where load

is added, if

there is

lateral

supporting

point in

span

Load is

added on

upper

flange

plate

Load is

added on

lower

flange

plate

No matter

where load

is added, if

there is

lateral

supporting

point in

span

2 6/13 25/2l 19/16 17/14 26/22 20/17

4 15/12 23/19 17/14 16/13 24/20 18/1 5

6 13/1l 21/17 16/1 3 15/12 22/18 7/14



Note: 1. Meaning of symbols in this table: h refers to full height of structural

component. l refers to free length of compression flange plate. l may also

refer to span of structural component without lateral supporting point within

span and to spaces among lateral supporting points of compression flange

plate for structural component with lateral supporting point. B refers towidth of compression flange plate of structural component; δ b refers to

thickness of compression flange plate of structural component.

2. Structural measure shall be adopted at end supporting position of structural

component to prevent torsion of end section.

3. In this table, numerator is applicable to Q235 and denominator to Q345.

2. Where bending member fails to comply with the aforesaid conditions, its whole

stability shall be verified. For details, see Annex J.

9.5.4 Local Stability of Plate

1. Local stability of web plate1) When ratio of height of web plate h0 to thickness δ (h0/δ)≤70 (60) (including

number in the bracket is applicable to Q345 and number out of the bracket is

applicable to Q235), transverse ribbed stiffener can be determined according to

structure. In order to support steel track, short transverse ribbed stiffener or

track-bearing beam shall be adopted. In this case, space among short ribbed stiffeners

shall be determined according to local bending stress conditions of steel track and

flange plate. Generally, space among short ribbed stiffener shall not exceed 750mm

and height is about 0.3h.

2) When 70 (60) < (h0/δ) ≤ 160 (135), transverse ribbed stiffeners shall be set andverification shall be carried out.

3) When 160 (135) < (h0/δ) ≤ 240 (200), besides transverse ribbed stiffeners,

longitudinal ribbed stiffener shall also be set at (1/5 - 1/4)h height of compression

edge, and verification shall be carried out.

4) When 240 (20) < (h0/δ) ≤ 320 (270), besides transverse ribbed stiffeners, two lines

of longitudinal ribbed stiffeners shall be set at compression area, where the first line

shall be set at (0.15-0.20)h to compression edge of web plate, and the second line

shall be set at (0.35-0.40)h to compression edge of web plate, and verification shall be

carried out.

5) When (h0/δ) > 320 (270), calculation shall be carried out according to local stabilityrequirements of high web plate.

2. Local Stability of Compression Flange Plate:

1) When ratio of out-extending width of compression flange plate with I-shaped

section along each side to thickness of compression flange plate with I-shaped section

is not greater than 15 for Q235 and not greater than 12 for Q345, local stability of

compression flange plate may not be calculated.

2) For box section, local stability may not be calculated if ratio of central distance of

web plate b0 to thickness of compression web plate δy satisfies the following

requirements: For Q235 (b0/δ

y)≤ 60 and for Q345 (b

0/δ

y)≤ 50.

Where flange plate is wide, one or more pieces of longitudinal ribbed stiffener shall



be set, to satisfy the aforesaid (b0/δy)≤ 60 (50). Stability may not be calculated when

inertia moment Iz3 of longitudinal ribbed stiffeners can satisfy clause 2 of 9.5.6.

9.5.5 For calculation of local stability of plate, see Annex J.

9.5.6 Requirement of structural side of ribbed stiffener

1. When local stability of web plate can be satisfied, spacing n among transverseribbed stiffener of web plate shall not be less than 0.5h, and shall not exceed the

bigger one of h0 and 2m, where ho refers to height of web plate.

Size of transverse ribbed stiffener of web plate shall be determined according to

formula 9.5.6-1 and 9.5.6-2:

Where,

b1 refers to out-extending width of transverse ribbed stiffener, mm;δ1 refers to thickness of transverse ribbed stiffener, mm.

When web plate has both transverse ribbed stiffener and longitudinal ribbed stiffener,

besides the aforesaid provisions, transverse ribbed stiffener shall also satisfy:

Izl ≥ 3h0δ3 (9.5.6-3)

Where,

Izl refers to inertia moment of section of transverse ribbed stiffener to central line of

thickness of web plate, mm4;

δ refers to thickness of web plate, mm.

For ribbed stiffener with box section, when transverse ribbed stiffener is jointed by 4

pieces of plates, inertia moment Izl of longitudinal plate against contact line shall not

be less than 1.5h0δ3.

In addition, longitudinal ribbed stiffener of web plate shall also satisfy requirements

of formula 9.5.6-4 and 9.5.6-5:

Where,

Iz2 refers to inertia moment of section of longitudinal ribbed stiffener of web plateagainst central line of web plate thickness, mm4;

a - see Fig. 9.5.6 Spacing among Transverse Ribbed Stiffener, mm.

Figure 9.5.6

When transverse or longitudinal ribbed stiffener doesn't adopt batten but adopt mold

steel, the part (whose width is 20δ) welded to the ribbed stiffer can be included in the



section of ribbed stiffener, and practical inertia moment against center-of-gravity line

of the section can be calculated, and requirements of formula 9.5.6-4 and 9.5.6-5 shall

be satisfied.

2. Longitudinal ribbed stiffener of flange plate shall satisfy requirements of formula

9.5.6-6:

Where,

fIz3 refers to inertia moment of section of longitudinal ribbed stiffener of flange plate

against central line of flange plate thickness, mm4;

b0 - see Fig. 9.5.6 Center Distance of Web Plate, mm;

δy - see Fig. 9.5.6 Thickness of Flange Plate, mm;

m refers to number of longitudinal ribbed stiffener of flange plate.

9.6 Rigidity RequirementRigidity can be divided into static rigidity and dynamic rigidity. Static rigidity is

expressed by static elastic deformation value of structure and structural components at

certain position when specified load is added on certain position; generally, for gate

hoist, dynamic rigidity of vibration system is only verified when there are relevant

requirements.

Static rigidity requirements of bridge-type, platform-type and gantry hoist are as

follows:

When rated load is added at midspan or at worst position (at lifting-start position for

platform-type and single-direction gantry hoist), due to vertical static deflection yL

caused by rated hoisting load and weight of trolley at midspan, the following

requirements shall be satisfied:

Midspan deflection of bridge-type and bi-direction-type gate hoists:

When working class is Q1 and Q2, yL≤ L/700 (9.6-1)

When working class is Q3 and Q4, yL≤ L/800 (9.6-2)

Where,

L refers to span of gate hoist.

For gantry hoist with cantilever, when trolley with full load is at effective working

position of cantilever, vertical static deflection at this position:

yL≤ Lc/350 (9.6-3)Where,

Lc refers to effective working length of cantilever.

Generally, horizontal midspan displacement value of bridge-type and platform-type

gate hoist is recommended to be controlled at:

ys≤ L/2000 (9.6-4)

For gantry of gantry hoist, the horizontal displacement along the two directions is

recommended to be less than 1.5H‰ under the worst load combination. Where H

refers to height from track level (upper flange of main girder for single-direction hoist)

of big trolley to track level of small trolley.

When small trolley gantry and mechanical equipment are installed directly on



platform trolley bracket and gantry of single-direction hoist shall be appropriately

strengthened. When the maximum vertical static deflection is used as component of

freely supported beam, it is recommended to be controlled to be:

ye≤ L/2000 (9.6-5)

Where,L refers to span of trolley, platform trolley and single-direction gantry hoist.

For cantilever, L is recommended to be controlled to be

ye≤ Lc/1000 (9.6-6)

Where,

Lc refers to effective working length of cantilever.

9.7 Gantry Structure

9.7.1 Structural type of gantry

According to operating requirements, gantry structure can be designed into without

cantilever, single-cantilever, double-cantilever and semi-gantry type. According to

different sectional structure, gantry structure can be designed into box section, plategirder and lattice section type (truss and strut).

Generally, connection between gantry leg and main girder shall be of rigid connection,

namely rigid leg.

9.7.2 Calculation principle of internal gantry force

1. Within gantry plane: for gantry having two rigid legs, calculation figure of static

structure shall be adopted for calculation of internal force of main girder, and

calculation figure of once hyperstatic structure shall be adopted for calculation of

internal force of leg.

2. Within plane of leg: for connection between leg and lower transverse girder, when

ratio of leg rigidity to beam rigidity is greater than 0.6, the internal force shall be

calculated according to triple hyperstatic structure; when the ratio is less than or equal

to 0.6 and other section of leg is larger this area, the internal force shall be calculated

according to once hyperstatic structure. For simple calculation figure, see Figure

9.7.2.

3. Combination of various loads added on gantry hoist during running shall be used as

conditions to verify internal force of gantry structure.

4. For large gantry hoist, the internal force is recommended to be calculated by

computer according to space system.



Figure 9.7.2 Calculation Figure for Gantry in Leg Plane

9.8 Constructional Requirement9.8.1 General principle

1. Efforts shall be made to guarantee simple structure, definite force bearing of main

bearing structure, and impact of concentrated stress shall be reduced.

2. Structural design must be convenient for manufacture, examination, transportation,

installation and maintenance. Exposed and underwater structures (such as hooking

beam) must avoid water accumulation.

3. Thickness of steel plate and mold steel limb of main bearing structure shall not be

less than 5mm.

4. Main bearing structural components can adopt different connection methods at

different positions, but two different connection methods shall not be adopted at the

same position.

5. For welded beam, besides position close to bearing position, lower part of

transverse ribbed stiffener shall not be directly welded on tension flange plate, and

shall break at position not less than 50m far from inner surface of tension flange plate.

For wide flange (such as where people can pass) box beam or single-web plate beam,

in order to avoid deformation of tension flange plate during construction and

transportation, lower part of transverse ribbed stiffener can be welded to 10mm -

16mm thick tie plate. And then tie plate can be welded together with tension flange

plate with longitudinal weld, see Fig. 9.8.1-1.6. Butt welds of web plate and flange plate of welded beam are recommended not to

be arranged on the same section, and spacing among them shall not be less than

200mm; transverse ribbed stiffener shall be departed from butt weld of parallel web

plate, and spacing among them shall not be less than 200mm.

7. When track is laid on compression flange plate of welded beam and wheel pressure

is added, if track just faces web plate, web plate and compression flange plate are

recommended to adopt successive penetrated weld, and transverse ribbed stiffener

must be chamfered at connection between ribbed stiffener and web plate (see Figure

9.8.1-2). In condition where wheel pressure is transmitted by transverse ribbed

stiffener or by participation of transverse ribbed stiffener, the transverse ribbed



stiffener shall also be welded tightly with compression flange plate. Length of weld

under bearing surface of track shall not be less than 1.4 times bearing width of track.

In addition, double-side weld shall be adopted and double-side stagger weld or

single-side intermittent weld can be adopted on other positions.

Figure 9.8.1-1 Arrangement of Welded Box Beam and Single Web Plate Transverse

Ribbed Stiffener

Figure 9.8.1-2

8. Thickness of truss gusset plate shall be selected from Table 9.8.1 according to

internal force of web rod.

Table 9.8.1 Thickness of Gusset Plate

9. Generally, for main beam of gantry hoist and bridge-type hoists, midspan camber

shall be 0.001L, where L refers to span. Upwarp degree of cantilever end shall be

Lc/350, where Lc refers to effective working length of cantilever.

9.8.2 Weld connection



1. Weld metal: weld metal is recommended to match with body metal. If different

types of steel with different strengths are welded, welding material that matches with

low-strength steel can be adopted.

2. Butt weld: groove type of butt weld shall comply with provisions of GB/T 985 and

GB/T 986.In main bearing structures, if butt weld between plates with different thicknesses or

widths, transit gradient not exceeding 1:4 shall be made from one or both sides, see

Figure 9.8.2-1.

Figure 9.8.2-1

3. Fillet weld:1) For minimum height hwmin of fillet weld, see Table 9.8.2 (when thickness of

welding piece is less than 4mm, minimum height of weld shall be the same as welding

piece). Generally, maximum height of fillet weld shall not exceed 1.2 times thinner

welding piece.

2) For main structure bearing dynamic load, surface of fillet weld shall be made into

concave arch or straight line. Ratio of right-angle side of weld to side weld shall be

1:1, and to end weld shall be 1:1.5. Overlapped length shall be equal to or longer than

5 times thickness of thinner welding piece, see Figure 9.8.2-2.

Figure 9.8.2-2

3) Minimum calculation length of fillet weld at side or end shall be 8h w. Maximum

calculation length of side weld shall be 40hw when bearing dynamic load, shall be

60hw when bearing static load. Overlong part will not be considered in calculation.

4. In primary welding connection, intermittent welding with small thickness can be

adopted, net distance among intermittent welding shall not exceed 15δmin incompression component and shall not exceed 30δmin in tension component.

Table 9.8.2 Minimum Height of Fillet Weld(hwmin) mm

9.8.3 Rivet connection and bolt connection



1. In main bearing structure, cup head rivet shall be adopted, and diameter d of the

rivet shall be 13mm - 22mm generally, and sunk rivet is only adopted in special

conditions, but sunk rivet shall be adopted in nail rod tension connection.

2. Total thickness of rivet steel plate shall not exceed 5d. Where the total thickness

exceeds 5d, bolt connection is recommended to be adopted.3. When rivet or bolt connection is adopted, each component shall have at least two

rivets or bolts at one side of node or joint. Number of rivet or bolt in each line is

recommended not be exceed 5, but the number determined by strength calculation

shall be satisfied.

4. If reamed-hole bolt connection is adopted and component bears dynamic load,

aperture shall be less than d+ (0.2-0.3)mm, where d refers to nominal diameter at bolt

matching position. If component bears repeated load, match of hole and bolt shall not

be less than H11/H9.

5. When high-strength bolt is adopted for connection, in order to prevent connection

piece from local damage caused by head of nut and bolt, high-strength steel washer shall be set at the two position.

6. Aperture of high-strength bolt shall be 1mm - 2mm larger than diameter of bolt.

7. Common bolt can only be adopted in connection between less important

components.

8. Permissible distance from rivet and bolt shall comply with values listed in Table

9.8.3.

9.8.4 Laying of track

1. If trolley track is fixed by pressure plate, fixing position of pressure plate shall just

face transverse ribbed stiffener.

2. Height difference and transverse dislocation of track level at joints shall not exceed

1mm. Connection joint of trolley track shall not exceed 2mm, and connection joint of

big trolley shall be 1mm - 3mm generally (excepting temperature joint).

Table 9.8.3 Permissible Distance of Rivet and Bolt

Name Arrangement and direction

Maximum

permissible

distance (lesser one

between the two

values)

Minimum

permissible

distance

Outer row 8d or 12δ Compression

component12d or 18δ

Distance

between

centersMiddle row

Tension

component16d or 24δ

3d

Along direction of internal

force2d

Cutting edge 1.5dDistance from

center to edge

of component

Vertical to

direction of

internalforce

Rolling edge

4d or 8δ

1.2d



Note: d refers to aperture, δ refers to thickness of thinnest plate among connection

components.

9.8.5 Landing, Ladder, Handrail and Cab

1. Ladders leading to driver's cab, electric equipment room, landing, mechanical andelectric equipment installation platform must be safe, convenient and reliable.

Minimum width of ladder is recommended not to be less than 500mm. Erect ladder

shall be equipped with safety loop over 3m from the ground, spacing among safety

loops shall not exceed 800mm, and shall have longitudinal connection bar. Number of

safety loop shall not be less than 3. Distance from ladder to top of loop shall be less

than 700mm and shall not exceed 800mm.

2. When height of working inclined ladder exceeds 10m, the ladder shall be connected

by segments, and rest platform must be set at each connection part.

3. Laying plates of landing and working platform are generally made of checkered

steel plate with anti-skid property. For gantry hoist and bridge-type hoist with trolley,distance from out-extending part of trolley to handrail of landing shall not be less than

500mm.

4. Firm handrail must be set at landing, working platform and inclined ladder, and

vertical height of handrail shall not be less than 1m. Middle handrail shall be set at

about 450mm to plate, and baffle plate shall be set at place not less than 70 mm at

bottom. If there are limitations, height of handrails on trolley platform of bridge-type

hoist and gantry hoist may be less than 1m.

5. Design of net space size, operation device, display instrument and chair in cab shall

comply with relevant provisions of labor protection and safety.6. Cab shall have favorable visibility, and tempered glass or other shatter-proof glass

shall better be adopted for the cab.

7. When big difference exists between working temperature in cab and temperature of

working environment, cooling or heating measures shall be adopted in the cab.

8. Where there are special requirements (such as working at termite region), relevant

protective measures shall be adopted in the cab.



10. Electrics

10.1 Electromotor

Winch-type, screw-rod-type, chain-type, gantry-type, bridge-type and platform gate

hoist shall adopt hoisting metallurgy asynchronous motor YZ-type and YZR-typegenerally, and hoisting metallurgy DC electromotor and other types that can meet

requirements of gate hoist can also be adopted. Generally, hydraulic gate hoist shall

adopt asynchronous electromotor without speed-adjustment requirement.

Rated power of electromotor shall be selected according to static power of structural

calculation, working mode of electromotor, load duration rate or load duration. Where

design limit has requirements, maximum moment or locked rotor moment of

electromotor shall satisfy starting requirements of mechanism. Under design rated

working condition, temperature rise of components of electromotor shall not exceed

specified value.

For verification formula, see Annex K, L, M, N and P.10.2 Drive Component of Detent

Drive component of detent must be selected according to volatge of power supply,

frequency, ambient conditions and corresponding mechanism working condition.

For AC transmission system, running mechanism shall adopt hydraulic push-rod

generally, and short-travel braking electromagnet may be adopted. For DC

transmission system, efforts shall be made for hoisting mechanism to adopt

serial-connected electromagnet and for running mechanism to adopt

parallel-connected electromagnet.

DC serially-connected electromagnet shall verify holding force of electromagnet of

starting pull and minimum load during starting of first-step electromagnet.

10.3 Resistor

10.3.1 Electromotor with different load duration rate are recommended to adopt

general resistor of different parameters; when load duration rate may be different but

close to each other, resistors of the same type can be adopted.

10.3.2 Resistor used for starting shall be selected through calculation, and tolerance

between calculated value and adopted value shall be ±5%. In order to reduce number

of resistance box, tolerance of resistance of specific class can be ±10%, but tolerance

of total resistance of each box shall not exceed ±8%; tolerance of commonly-adopted

serial-class resistor can be expanded appropriately, but the error shall not exceed 1.5%of rated resistance of electromotor.

10.3.3 Load duration rate of resistance of different classes shall be selected according

to different connection conditions, and allowable current value of resistor shall not be

less than rated current of electromotor, but specific class is allowed to be 5% lower.

Commonly-serial-class resistor shall be selected according to long-term working

system, and allowable current of components adopted shall not be less than rated

current of electromotor. Generally, hoisting mechanism shall not adopt frequency

sensitive rheostat, if adopted, requirements of working conditions shall be considered.

10.3.4 resistor with 4 or less boxes can be stacked up; spacing among boxes of

resistors with over 4 boxes shall not be less than 80mm, and thermal baffle resistor



bracket can be adopted among boxes.

10.3.5 External connection wire of resistor with connectors shall have a nude part and

measures shall be adopted to prevent the nude part from short-circuit. If resistors are

used outdoor, a cover shall be set for heat elimination and rain proof.

10.4 Protection DeviceGenerally, gate hoist shall be equipped with the following electric protection devices:

short-circuit protection, over-current protection, no-voltage protection, null-position

protection, open-phase protection, position-limit protection, overload protection, main

isolation switch and emergency switch that can cut main power supply off. If DC

transmission system is adopted, field-loss protection and over-speed protection shall

be set.

Gantry, bridge-type and platform-type gate hoist shall also be equipped with travel

protection and channel-mouth switch.

Exposed current-carrying parts of electric equipments that may be touched shall be

equipped with protection measures shall be adopted to prevent electric shock. Other electric protection devices may also be adopted according to design requirements and

user's requirements.

10.5 Transmission System

10.5.1 Transmission scheme

Generally, transmission system of gate hoist shall adopt AC transmission system.

Where there are special requirements, DC transmission system can also be adopted.

Hoisting mechanism of wire-wound-type asynchronous electromotor controlled by

control panel shall have at least one low-speed step during descending, and electric

braking shall be set during deceleration of descending. But where there are special

conditions (such as grab bucket), exception can be allowed.

10.5.2 Control mode

Control mode shall be selected according to requirement of transmission system to

operational performance and operational mode, type and capacity of electromotor,

load duration rate, switching times, expected service life of controller and type and

position of operational device.

Generally, control mode of wire-wound asynchronous electromotor transmission

system can be selected according to provions of Table 10.5.2.

Table 10.5.2 Control Mode of Transmission by Wire-wound Asynchronous

ElectromotorControl mode

Capacity of

electromotor, kWswitching times

150

switching times

300

switching times

600

≤22 K K K (P)

>22 P (K) P P

Note: 1. Electromotor capacity refers to rated power of electromotor in basic load

duration rate of intermittent periodic duty (S3), kW.

2. K refers to direction control by cam-operated controller; P refers to control

by command controller and control panel; symbols out of bracket refer totypes adopted generally, and symbols in bracket refer to types that can be



adopted.

DC system shall adopt control by master controller and control panel generally.Multiple fixed gate hoists can adopt centralized control and separate control; fixed

gate hoist can also adopt remote control and field control according to concrete

working requirements. If possible, field control of gate hoist can adopt programmable

controller.

10.6 Conducting Wire and Feeder Device

10.6.1 Conducting wire

Conducting wire of gate hoist must adopt copper-core stranded conductor. Type of

conducting wire shall be selected according to laying method, ambient temperature

and voltage class. Generally, rubber insulation wire, cable and plastic insulated cable

can be adopted, and conducting wire with small section may also adopt plastic

insulated wire.

Wiring on gate hoist must adopt multi-strand single-core conductor whose sectional

area shall not be less than 1.5mm2 and multi-core conductor whose sectional area

shall not be less than 1mm2. Sectional area of conduction can not be considered for

connection wires of electric devices, oil-pressure servo mechanism and sensor

components.

Generally, wires shall be laid in grooves or metallic ducts. Where it is inconvenient to

lay wires in grooves or metallic ducts or there is relative displacement, wires can be

laid in flexible tubes. Cable can be laid directly. Protective measures shall be adoptedat place where there are mechanical damage, chemical corrosion and oil corrosion.

Wires of different mechanism, AC and DC and different voltage classes shall be laid

in different tubes, illuminating wires are recommended to be laid separately.

Single-core conducting wire whose AC current capacity is over 25A shall not be

allowed to be laid in metallic duct. Junction box shall be set at connection and branch

point of conducting wires, junction box installed outdoor shall have rain-proof

measures and wire holes shall have covers.

Bending radius of cable laying shall not be less than 10 times external diameter of

cable.

10.6.2 Feeder device

1. Feeder device of trolley: cable, copper wire, mold steel or other conducting

material can be adopted. Selection of type and specification shall satisfy requirements

of current capacity and voltage loss in gate hoist. Diameter of copper slide wire shall

not be less than 6mm, and size of angle steel shall not be less than

40mm×40mm×4mm. Feeder device of trolley shall be set at place where is convenient

for maintenance. If nude conducting material is adopted as feeder device of trolley,

safety protection measures shall be set near the device.

Rigid slide wire shall be installed on fixer of isolated slide wire. Spacing among fixer

bracket shall not exceed 3m, length of slide wire extending out of bracket shall notexceed 0.8m; distance between adjacent slide wire shall not be less than 130mm



vertically and shall not be less than 270mm horizontally. Current collector of rigid

slide wire shall be weighted by self weight or spring, so as to guarantee favorable

connection with slide wire during running, and current collector shall not incline or

decline during running.

Flexible slide wire shall be equipped with middle support, insulation of middlesupport shall be installed on rigid bracket, and tension devices shall be adopted at both

ends of slide wires. Selection of current collector: low capacity and common electric

segment can adopt current collector of single pulley type; failure may be caused by

temporary break of current collector with high capacity, so double-pulley folk-type

bracket shall be adopted.

If mobile cable is adopted for feeder device of trolley, fixed contact box shall be set

on brackets of big trolley and small trolley, and cables shall be arranged tightly. In

addition, cable shall be abraded or shall not bear over tension during running of

trolley and mobile bracket shall be able to move flexibly.

2. Feeder device of big trolley: cable drum or slide wire device can be adopted. Whentravel distance is long, capacity is large and cable-drum wound cable must be adopted,

high-voltage power supply can be adopted, and power supply can be transferred to all

mechanism after being stepped down by transformer installed on gate hoist.

10.7 Voltage Loss

Where AC power supply is adopted, voltage loss from low-voltage busbar of power

supply transformer to any terminal of electromotor shall not exceed 15% of rated

voltage during peak current. Generally, voltage loss in gate hoist may be 4%, and may

be 6% for gate hoist that is not often operated.

If power is supplied by cable drum, voltage loss of cable drum shall not belong to

internal voltage loss of gate hoist.

10.8 Lighting, Single and Communication

10.8.1 Lighting

Appropriate lighting shall be available in machine room, electric room, passage,

ladder and cab of gate hoist, and shall comply with relevant standards. Design and

arrangement of working lighting shall not affect visual field of operating personnel in

normal operation. Voltage of fixed lighting power supply shall not exceed 220V, and

metallic structure must not be used as lighting circuit.

If single accumulator is adopted for power supply, voltage shall not exceed 24V, and

supply voltage of portable lighting device shall not exceed 36V.10.8.2 Signal and communication

State of main power supply of gate hoist shall have obvious signal indication in

operation room. Malfunction signal and alarm signal can be set according to

requirements. Signal device can adopt audible signal and signal lamp, and these

devices shall be set within visual and audible field of relevant personnel.

Telephone, wireless interphone and loudspeaker can be adopted as dispatching and

working communication facilities at power plant.

10.9 Earthing

Reliable earthing shall be made to all electric equipments, metallic enclosure not

carrying current under normal condition, metallic wire tube and metallic cover of



cable and step-down side of safety lighting. Unreliable electric connection between

wheel and track can be caused by non-conducting deposited dust, so mobile gate hoist

shall be equipped with special earthing wire, and earthing trunk is recommended to be

adopted to steel structure where there are many weld.

Users shall be responsible for earthing of big track and fixed gate hoist, and theearthing shall comply with requirements of relevant codes.

Earthing branch of single low-voltage electric equipment shall adopt copper wire, and

according to mechanical strength, allowable minimum section area shall be 4mm2 for

exposed nude wire, and shall be 1.5mm2 for insulated wire.

Sectional area of earthing wire shall be reviewed according to possible earthing

short-circuit current and thermal stability, and shall not be less than the following

value generally: steel: 800mm2; copper: 50mm2.

When cab of mobile gate hoist is connected with main structure by bolt, number of

earthing point shall not be less than two. Earthing wire must not be used as

current-carrying zero line.10.10 Miscellaneous

For electric equipments of gate hoist used in humid tropic zone, dry heat zone and

high-altitude zone, design and selection shall satisfy relevant requirements.

10.11 Working Scope of Electric Design

Working scope of electric design shall include the following content: instruction and

calculation letter, electric principle figure, panel arrangement figure, terminal

installation and wiring figure, field installation and wiring figure, list electric

equipments and materials, as well as structure and manufacture figure of fixed electric

equipments.



Annex A (Informative Annex) Hoisting Force, Lift Head, Span and Speed Series

of Gate Hoist Date and Example of Working Class of Gate Hoist

A.1 Hoisting Force Series

Table A.1 Hoisting Force Series kN

A.2 Lift Head Series

Table A.2 Lift Head Series m

A.3 Span Series of Mobile Gate Hoist

Table A.3 Span Series m

A.4 Speed Series

Table A.4 Speed Series m

Hoisting speed of screw rod gate hoist shall be 0.2m/min - 0.5m/min;

Hoisting speed of winch hoist shall be 1m/min - 2.5m/min.For mobile gate hoist, running speed of trolley shall be 5m/min - 10m/min, and

running speed of big trolley shall be 10m/min - 25m/min.

Hoisting speed of hydraulic gate hoist shall be 0.2m/min - 1m/min; closing speed of

fast hydraulic gate hoist is recommended not to exceed 5m/min when the gate is

closing to the bottom sill.

A.5 Example of Working Classes

Table A.5 Example of Working Classes

Type of gate hoist Working class

Hoisting maintenance gate Q1-lightWinch hoistHoisting emergency

Lift head Q1-light, Q2-light



<40m

gate Lift head

≥40mQ2-light, Q3-medium

Lift head

<40m

Q2-light, Q3-medium

Hoisting working gateLift head

≥40m

Q3-medium,

Q4-heavy

Hoisting emergency gate Q1-light, Q2-light Screw-rod gate

hoist Hoisting working gate Q2-light

Chain gate hoist Hoisting working gate Q2-light, Q3-medium

Lift head <40m Q1-light, Q3-medium

Mobile gate hoistLift head ≥40m

Q2-medium,

Q4-heavy



Annex B (Informative) Recommended Values of Acceleration (Deceleration) of

Running Mechanism and Corresponding Acceleration (Deceleration) Time

Table B.1 Recommended Values of Acceleration (Deceleration) of Running

Mechanism and Corresponding Acceleration (Deceleration) Time

Low-speed and medium-speedgate hoist with long running

distance

Commonly-used medium-speedgate hoist

Running speed

m/s Acceleration

(deceleration)

time t (s)

Acceleration

(deceleration)

a (m/s2)

Acceleration

(deceleration)

time t (s)

Acceleration

(deceleration)

a (m/s2)

l.00 6.6 0.15 4.0 0.25

0.63 5.2 0.12 3.2 0.19

0.40 4.1 0.098 2.5 0.16

0.25 3.2 0.078

0.16 2.5 0.064



Annex C (Informative) Calculation Method of Horizontal Lateral Force Ps

during Oblique Running of Gate Hoist

Horizontal lateral force during oblique running of gate hoist can be proximately

calculated according to the following formula:

Where,

∑P refers to total wheel pressure that may appear on the hoist side where lateral force

is added frequently (it is related trolley position), see Figure C.1;

λ refers to horizontal lateral force coefficient, and it shall be determined according to

Fig. C.2.

L refers to span of gate hoist, m;

B refers to spacing among gate hoists, m; where there are 4 wheels on one track, B

shall adopt spacing among exterior wheel axles; when there are 8 wheels on one track,

B shall adopt distance between two central lines of wheels; if horizontal guide wheel

is adopted, B shall adopt horizontal distances among wheels.

Figure C.1 Position of Trolley of Gate Hoist and Wheel Pressure during Running

Figure C.2 Relation between λ and L/B



Annex D (Informative) Calculation Data of Wind Load

D.1 Windward Area

Windward area of gate hoist structure and object shall be calculated according to the

worst windward direction, and projection area on plane vertical to wind direction shall

be adopted.D.1.1 Windward area A of signal-piece structure of gate hoist:

Where,

A1 refers to overall area of structure or object, A1 = h×l, see Figure D.1;

φ refers to solidity ratio of structure, namely, φ=A/A1, see Figure D.1.

Figure D.1 Overall Size of Structure or Object

D.1.2 For two parallel structures with same height and type, wind-shielding action of

the front piece to the back piece shall be considered, and total windward area A = A1

+ηA2 (D.2)

Where,

A1 refers to windward area of the front structure, A1=φ1Al1;

A2 refers to windward area of the back structure, A2=φ

1A

l2;

η refers to wind-shielding conversion coefficient of the front piece to the back piece

between two pieces of adjacent truss; it is related to the solidity ratio of the front (first)

piece and spacing ratio a/h between the adjacent two pieces (see Figure D.2).

D.1 For 3 pairs n-pieces parallel structures with the same type, same height and same

spacing, under action of longitudinal wind power, overlapping wind-shielding effect

of multiple-pieces structure shall be considered, and total windward area of structure

shall be determined according to the following formula:

Where,

φ1 refers to solidity ratio of the front (first) structure;

AII refers to overall area of the front (first) structure, m2.

If formula D.3 is adopted to calculated windward area A and formula 6.0.6-1 is

adopted to calculated total wind load, due to different types of each structure, wind

coefficient of one structure shall be multiplied.



Table D.1 Solidity Ratio of Structure φ

Solid structure and object 1.0

Mechanism 0.8-1.0

Truss made of mold steel 0.3-0.6

Windward structural type

and object

Steel pipe truss structure 0.2-0.4

Table D.2 Wind-shielding Conversion Coefficient η of Truss Structure

φ 0.1 0.2 0.3 0.4 0.5 0.6

1 0.84 0.70 0.57 0.40 0.25 0.15

2 0.87 0.75 0.62 0.49 0.33 0.20

3 0.90 0.78 0.64 0.53 0.40 0.28

4 0.92 0.81 0.65 0.56 0.44 0.34

5 0.94 0.83 0.67 0.58 0.50 0.41

Interval

ratio a/h

6 0.96 0.85 0.68 0.60 0.54 0.46

Note: Wind-shielding conversion coefficient of other structure can be selected

according to Annex D.2 hereof.

D.1.4 Windward Area of Object

Windward area of hoisted object shall be determined according to practical projection

of the object on plane vertical to wind direction. If overall size of object is not definite,

approximate method can be adopted to estimate the value.

Figure D.2 Relation of Spacing among Parallel Structures

D.2 Wind-shielding Conversion Coefficient

D.2.1 Wind-shielding conversion coefficient η of components with I-shaped cross

section, box section and trapezoidal closed section can be approximately adopted

from values listed in the following tables:

D.2.1.1 For wind-shielding conversion coefficient of component with I-shaped cross

section, see Figure D.3 and Table D.3.

Table D.3 Wind-shielding Conversion Coefficient of I-shaped Cross Section



Figure D.3 Parallel Structure Size Relation of Components with I-shaped Cross

Section

D.2.1.3 For wind-shielding conversion coefficient of mixed structure of beam with

I-shaped cross section and truss (mixed structure for short), see Figure D.4, Table D.4

and Table D.5.Table D.4 Wind-shielding Conversion Coefficient η of Mixed Structure

Table D.5 Wind-shielding conversion coefficient η, when solidity ratio of truss φ

＝0.3-0.4

Fig. D.4 Relation of Section Construction Size of Mixed Structure

D.2.1.3 For wind-shielding conversion coefficient of component (beam) with

box-type or trapezoidal section, see Fig. D.5 and Table D.6.

Table D.6 Wind-shielding Conversion Coefficient η of Component (Beam) with

Box-type Section and Trapezoidal Section

Figure D.5 Size Relation of Component with Box Section and Trapezoidal

Section

Figure D.7 Wind-shielding Conversion Coefficient of Truss Structure

D.2.3 In truss-type tower frame with square section or like-square section, if oblique

web rod within the same segment of current parallel truss is arranged reversely,

wind-shielding conversion coefficient of the next truss is about 2 time value when

web rod is arranged along the same direction (for values of truss web rod arranged

along the same direction, see Table D.2).

D.2.4 Wind coefficient C of component (beam) with single trapezoidal section under

action of lateral wind power shall be 1.2.



Annex E (Informative) Permissible Physical Quantity of Commonly-used

Friction Surface Material

Table E.1 Maximum Permissible Physical Quantity of Detent and Clutch Surface

[pv] N.m/(mm

2.s)

[p] N/mm

2

For support For controlof decline

Without lubricationMaterial of frictionalsurface

For support

For control

of decline

Block type

Belttype

Block type

Belttype

Frictioncoefficient

Allowabletemperature℃

Asbestosrubber

rolling bestagainst steel

0.8 0.4 5 2.5 2.5 1.5 0.42-0.48 220

Asbestossteel wire

braking beltagainst steel

0.6 0.3 5 2.5 2.5 1.5 0.35 220

Table E.2 Maximum Permissible Physical Quantity of Copper Alloy Bushing

Material



Annex F

(Informative)

Friction Coefficient and Efficiency

Table F.1 Friction Coefficient

Name of frictional material Frictioncoefficient

Rolling bearing:

ball-type or column-type

Taper roller type

0.015

1.02

Sliding bearing

Rolling friction force arm between wheel and steel track

Steel wheel - diameter (φ400mm-φ1000mm) flat champignon

rail

End with arch steel track

Cast iron wheel - diameter (φ400mm-φ1000mm) flat

champignon rail

End with arch steel track

0.05-0.07

0.06-0.12

0.06-0.09

0.07-0.14

Rail clamping device mouth and steel track

Clamp mouth without thread

Clamp mouth with thread (HRC≥55)

0.12-0.15

0.25

Table F.2 Approximate Value of Mechanical Transmission Efficiency

Transmission part Efficiency

Sliding bearing Rolling bearingCylindrical gearingOpen-type cylindrical gear pair (grease

lubrication)

Closed-type cylindrical gear pair (oil lubricant)

0.90-0.92 0.92-0.94

0.96-0.98

Sliding bearing Rolling bearingBevel gear transmission

Open-type bevel gear pair (grease lubrication)

Closed-type bevel gear pair (oil lubricant)

0.90-0.92 0.92-0.94

0.95-0.97

Chain wheel of chain gate hoist

Rolling bearing

Sliding bearing

0.90-0.93

0.88-0.91

Intermediate axle

Rolling bearing

Sliding bearing

0.97-0.99

0.95-0.97

Drum

Sliding bearing

Rolling bearing

0.94-0.96

0.96-0.98

Pulley

Sliding bearing

Rolling bearing

0.95

0.98

Gear coupling 0.96Decelerator



Monopole cylindrical gear decelerator

Bipolar cylindrical gear decelerator

Monopolar bevel gear decelerator

Double-reduction bevel-spur gear

0.97

0.95

0.95

0.94

Pulley block Sliding bearing Rolling bearing2

3

4

5

6

7

Reeving of

pulleyblock

8



Annex G (Informative) Relevant Calculation Data of Parts and Track

G.1 Drum

G.1.1 Calculation of Drum Wall

When L≤3D, compression stress of drum wall shall be calculated according to

formula G.1:

Where,

A refers to multi-layer wound coefficient related to winding layers of steel cable; its

value shall be selected from Table G.1;

Smax refers to maximum pull of steel cable, N;

δ refers to thickness of drum wall (for cast iron δmin≥12mm, for cast steel δmin≥15mm),

mm;t refers to pitch spacing of screw grooves on drum, mm;

[σ p] refers to permissible compression stress, N/mm2;

for steel: [σ p]=σs/1.5 (σs refers to yielding point)

for cast iron: [σ p]=σ b/4.25 (σ b refers to compression intensity).

]

Table G.1 Multi-layer Wound Coefficient

When L>3D, conversion stress generated by bending moment and torque shall be

calculated according to formula G.2:

Where,

MF refers to conversion moment, N·mm;

Mw refers to bending moment borne by drum, N·mm;Wn refers to torque moment borne by drum, N·mm;

W refers to resistance moment of drum section, mm3;

[σ] refers to permissible stress, N/mm2;

For steel: [σ]=σs/2.5;

For cast iron: [σ]=σ b/6 (σ b refers to tension intensity).

When D≥1.2m, L>2D, stability shall be calculated according to formula G.3:

Where,



K refers to stability coefficient;

pw refers to critical stress of stability, N/mm2;

For sSteel:

For cast iron:

R=D/2, R refers to radius of groove bottom of drum, mm;

p refers to unit compression stress of drum wall, N/mm2;

G.1.2 Calculation of Drum Shaft (Fig. G.1)

Main load of drum shaft with large gear shall include: Smax (maximum pull of steel

cable), P j (weight of drum and drum shaft), Pc (weight of large gear), Po (periphery

force of large gear) and Pr (radial force of large gear). Pal and P bl refer to counter force

under action of Smax and P j. Horizontal bending force, vertical bending moment and

relevant bending stress of each sections can be calculated separately according toforce calculation diagram of drum shaft.

G.1.3 Calculation of connection between large gear and drum

Figure G.1 Calculation Diagram of Force Borne by Duplex Drum Shaft

If torque is transferred between drum and large gear through sheet, connection bolt

bears no shear, and only plays as connection effect, see Figure G.2. Shear force of

sheet shall be calculated according to formula G.4:

Where,

M refers to torque transferred by sheet, N·mm;

n refers to number of sheet;

d1 refers to exterior aperture of sheet, mm;

d2 refers to interior aperture of sheet, mm;

D refers to diameter of center circle among sheets, mm.

Torque is directly transferred by bolt between drum and large gear through reamed

hole, and it also plays connection role. Shear stress of bolt used for reamed hole shall



be calculated according to formula G.5:

Figure G.2 Connection Figure between Drum and Large Gear

Where,d1 refers to diameter of stick part of bolt used for reamed hole, mm;

For meaning of other symbols, see relevant definition stated above.

Extrusion stress shall be calculated according to length Lφ of bolt used for sheet or

reamed hole transferring torque and according to formula G.6:

Where symbols have same meaning as stated above.

For 45# steel sleeve that is processed, [τ]=85N/mm2, [σcm] = 280N/mm2。

G.1.4 Calculation of Bolt of Pressure Plate

Steel cable shall be fixed on to the drum by pressure plate, see Figure G.3.

Figure G.3 Figure for Fixing of Steel Cable

Tension stress of pressure plate bolt shall include tension stress generated by driving

force and tension force generated by bending of bolt caused by friction between

washer and pressure plate.

Calculation of tension stress of pressure plate bolt is related to wrap angle a of steel

cable on drum and shape of groove of pressure plate.

When a = 3π:

If groove of pressure plate is of trapezia, tension stress of pressure plate bolt shall be




Where,Smax refers to maximum pull of steel cable;

n refers to number of bolt of pressure plate; it shall not be less than 2;

L refers to force arm of friction action (see Figure G.3).

[σ1] refers to permissible tension stress,[σ1]=σs/2.5

If groove of pressure plate is round, tension stress of pressure plate bolt shall be



When a = 4π:

If groove of pressure plate is of trapezia, tension stress of pressure plate bolt shall be



If groove of pressure plate is round, tension stress of pressure plate bolt shall be



Figure G.4 Forging Single-hook Structure

G.2 Lifting tools



G.2.1 Forging single hook

Structure of single forging hook is show in Figure G.4.

G.2.1.1 Strength calculation of hook body

Tension stress at internal side of A-A section shall be calculated according to formula

G.11:

Where,

P refers to calculation load of hook, N;

e1 refers to distance from center of gravity of section to interior side of section, mm;

K refers to shape coefficient of A-A section; A-A section is usually used as trapezoidal

section (see Figure G.4), h≈D、 b1≈0.67h、 b2≈0.4b1, K ≈0.1;

A refers to area of A-A section, mm2;

D refers to diameter of lifting hole of hook, mm.G.2.1.3 Strength calculation of thread and screw rod of hook head.

(1) Tension stress of screw rod neck shall be calculated according to formula (G.12)

Where,

d0 refers to diameter of screw rod neck, mm.

(2) Bending stress of screw rod neck shall be calculated according to formula G.13:

Where,

d refers to exterior diameter of thread, mm;

d1 refers to interior diameter of thread, mm;

n refers to number of working thread;

h refers to height of thread root, mm.

(3) Extrusion stress of contact surface of thread shall be calculated according toformula G.14:

Where,

t refers to spacing among thread, mm;



Figure G.5 Relation Figure for Size of Lifting Folk

H refers to height of thread contact surface, mm.

G.2.2 Lifting folk

G.2.2.1 Strength calculation of folk body:Tension stress at internal side of A-A section shall be calculated according to formula

G.15:

Where,

P refers to calculation load of lifting folk;

a refers to conversion coefficient of stress; it shall be selected according to

in Figure G.6.

Interior stress of axle hole on B-B section shall be calculated according to formula

G.16:

Where, for h2, d and a, see Figure G.5.



Figure G.6 Relation Figure between a and .

Exterior tension stress of C-C section shall be calculated according to formula G.17:

Where,

K refers to shape coefficient of C-C section; for rectangular section

, for b, D and h3 see Figure G.5.

G.2.3 Lifting plate

Size relation of lifting plate is shown in Figure G.7.

Figure G.7 Size Relation of Lifting Plate

(1) Bearing stress of hole wall of lifting plate shall be calculated according to formula

G.18:



Where,P refers to load borne by one lifting plate, N;

δ refers to thickness of lifting plate, mm;

d refers to diameter of axle hole of lifting plate, mm;

(2) Tension stress on horizontal section of axle hole of lifting plate can be calculated

according to formula G.19:

Where,

B refers to width of lifting plate, mm;

a refers to stress concentration coefficient; it shall be selected according to d/B and

Figure G.8.

Figure G.8 Relation between a and d/B

(3) Tension stress on vertical cross-section of axle hole of lifting plate can be


Where,

R=B/2, mm。

G.3 Wheel Trolley

G.3.1 Calculation of fatigue strength of wheel tread

Calculation load Pc of fatigue strength on wheel tread shall be calculated according to

formula G.21:



Where,

Pmax refers to maximum wheel pressure of big trolley or small trolley during runningwith load, N;

Pmin refers to minimum wheel pressure of big trolley or small trolley during running

with load, N.

Line fatigue strength of line contract on wheel tread shall be calculated according to

formula G.22:

Where,

K 1 refers to permissible line contract stress constant related to material,

N/mm2; steel wheel K shall be selected from Table G.2;D refers to diameter of wheel tread, mm;

b refers to effective contact width between wheel tread and track, mm;

c1 refers to rotation speed coefficient, see Table G.3;

c2 refers to working class coefficient, see Table G.4.

Line fatigue strength of point contract on wheel tread shall be calculated according to

formula G.23:

Where,

K 2 refers to permissible point contact stress constant related to material, N/mm2; steel

wheel K2 shall be selected from Table G.2.

R refers to larger value of curvature radius of wheel tread and track, mm;

m refers to coefficient determined according to ratio of curvature radius of track head

and wheel tread (r/R); it shall be selected from Table G.5.

G.3.2 Contact strength calculation of wheel tread

Calculation load P b of contact strength of wheel tread shall be maximum wheel

pressure of gate hoist under maximum hoisting load.

Line fatigue strength of line contract on wheel tread shall be calculated according to

formula G.24:Pb≤2.2K 1D b (G.24)

Table G.2 K1 and K2 Values

σ b K 1 K 2

500 3.8 0.053

600 5.6 0.1

650 6.0 0.132

700 6.6 0.171

>800 7.2 0.245

Note: 1. σ b refers to tension strength of material that has not be treated, N/mm

2

.2. Generally, steel wheel may need to go through heat treatment; line contact



can adopt HB = 300 - 340, point contract can adopt HB = 340 - 380, and

depth of heat treatment can be 15mm - 20mm. During determination of

permissible value of K1 and K2, σ b of material that has not be treated shall

be adopted.

3. When ductile cast iron is adopted,σ b≥500N/mm

2

, K 1 and K 2 shall beselected according to σ b=500N/mm2.

Table G.3 Value of Rotation Speed Coefficient C1

Rotation speed of

wheel r/min

C1 Rotation speed of

wheel r/min

C2

22.4 1.04 11.2 1.12

20 1.06 10 1.13

18 1.07 8 1.14

16 10.9 6.3 1.15

14 1.1 5.6 1.16

12.5 1.11 5 1.17

Table G.4 Working Class Coefficient C2

Working class of running mechanism Q1 Q2 03 Q4

C2 1.25 1.12 1.0 0.0

Where, meaning of symbols are same with those defined in formula G.22.

Line fatigue strength of point contact on wheel tread shall be calculated according to

formula G.25:P b≤3.3K 1D b (G.25)

Where, meaning of symbols are same with those defined in formula G.23.

Table G.5 Value of Coefficient m

r/

R

1.0 0.9 0.8 0.7 0.6 0.5 0.4 0.3 0.2 0.15 0.10 0.05

m 0.38

8

0.40

0

0.42

0

0.44

0

0.46

8

0.49

0

0.53

6

0.60

0

0.41

6

0.80

0

0.67

0

1.28

0

Note: 1. When r/R adopts other values, m value can be calculated according to

interpolation method;

2. r shall be smaller curvature radius of two surface contacted, mm.

G.4 Track

For track under action of strength calculation load Pb of wheel, see Figure G.9.



Figure G.9 Track Wheel Strength Calculation

G.4.1 foundation bearing stress of track bottom plate can be calculated according to

formula G.26. When center distance between two adjacent rolling wheels is less than

3hk , approximate calculation can be made according to formula G.27:

Where,

σ b refers to wheel strength calculation load, N;

hk refers to track height, mm;

Bk refers to width of bottom plate of track, mm;

L refers to middle distance between two adjacent rolling wheels, mm.

If track foundation is made of concrete, permissible bearing stress [σ0] shall be

adopted according to Table G.6.

Table G.6 Permissible Stress of Concrete [σ0] N/mm2

Concrete gradeSymbol

150 200 250 300

[σ0] 5 7 9 11

G.4.2 Bending stress of track section can be calculated according to formula G.28:

Where,

Wk refers to resistance moment of track section, mm3;

Meanings of P b and Hk are same with definition stated above.

B.4.3 Local bearing stress of track neck can be calculated according to formula G.29:

Where,



δ refers to distance from track neck to track level, mm;

t refers to thickness of track neck, mm.

G.4.4 Bending stress of bottom plate of track can be calculated according to formula

G.30:

Where,

c refers to length of cantilever of bottom plate, mm;

δ refers to thickness of bottom plate, mm;

G.5 Calculation of load-bearing nut of hoisting screw rod

G.5.1 strength calculation of hoisting screw rod:

Due to that hoisting force is usually greater than closing force, so hoisting force shall

be adopted as strength calculation load of P1.Twisting moment Mk borne by hoisting screw rod can be calculated according to

formula G.31.

Where,

P1 refers to hoisting force, N;

a refers to lifting angle of thread;

p' refers to equivalent frictional angle,

f refers to sliding frictional coefficient between screw rod and nut; it is related to

material and processing precision; it shall adopt 0.07-0.15 generally, or average value

0.12 can be adopted;

β refers to section angle of thread, for rectangular thread β=0 degree, for trapezoidal

thread β=30 degrees.

d2 refers to diameter of thread, mm.

Torsional shearing stress τk of hoisting screw rod can be calculated according to

formula G.32:

Where,

Mk refers to twisting moment,

d1 refers to interior diameter of thread, mm.

Bending moment borne by hoisting screw rod can be calculated according to formula

G.33:

Where,

μ refers to frictional coefficient of gantry pillars;



d0 refers to diameter of pivot shaft of gantry pillar, mm.

Bending stress of hoisting screw rod can be calculated according to G.34;

Where,M refers to bending moment,


Axial stress of hoisting screw rod can be calculated according to formula G.35:

Where,

P1 refers to hoisting force, N;


Combined stress of hoisting screw rod can be calculated according to formulaG.36:

Where,

refers to bending stress, N/mm2;

refers to axial stress, N/mm2;

refers to yielding point of material, N/mm2;

refers to shearing stress, N/mm2.

G.5.2 Stability verification of hoisting screw rod:

When slenderness ratio of hoisting screw rod stability can be verified

according to formula G.37.

Where,P2 refers to closing force, N;

E refers to elastic modulus of material, N/mm2;

n refers to stability safety coefficient; it shall be 1.8 - 3 generally;

Conversion coefficient of length; ；

L refers to practical length of tension calculation of hoisting screw rod, mm;

d1 refers to interior diameter of thread of screw rod, mm;

When slenderness ratio of hoisting screw rod and there is additional bending

moment action, calculation shall be made according to formula G.38:



Where,

P2 refers to closing force, N;

refers to stability coefficient of eccentrical compression; it shall be adopted

according to Table G.7;

A refers to sectional area of interior diameter of screw rod, mm2;

Table G.7 Value of Stability of Eccentric Compression



Table G.7 (Continue)

Note: 1. eccentricity refers to resistance moment of section of screw rod whose interior diameter is d1;

2. Slenderness ratio

G.5.3 Strength Calculation of Load-bearing Nut:

Working height H of load-bearing nut shall satisfy requirements of bearing stress on

contact surface of thread, and can be calculated according to formula G.39:



Where,

P1 refers to hoisting force, N;t refers to thread distance, mm;

d refers to exterior diameter of thread, mm;


H refers to height of nut, mm; H/t refers to number of working teeth of thread, it shall

adopt 10 when it exceed 10;

[q] refers to permissible bearing stress, N/mm2; it can be selected from Table G.8.

Bending strength of thread root can be calculated according to formula G.40:

Where,

Z refers to number of working teeth of thread; it shall adopt 10 when it exceeds 10;

h refers to height of thread;

b refers to thickness of tread root, for trapezoidal thread

refers to permissible bending stress, N/mm2; it shall be selected according

to Table G.7.

Shearing strength of thread root shall be calculated according to formula G.41:

Where,

refers to permissible shearing stress, N/mm2; it shall be selected from Table

G.8;

Meanings of other symbols have same meaning with those defined above.

Table G.8 Permissible Stress of Commonly-used Material of Load-bearing Nut

N/mm2

Material nameBearing stress [q]

Bending

stress

Shearing

stress

ZcmSm5Pb5Zm5 6-8 50-40 25-30

ZCuSn10Pb1 10-13 40-55 30-41

ZCUAl10Fe3 15-20 66-78 50-58

HT250 4-6 46-48 30-38

Note: sand casting material shall adopt small value, and die cast metallic material

shall adopt the bigger one.



Annex H (Informative) Calculation Data for the Hydraulic Gate Hoist

H.1 Calculation of Oil Pump Electric Machine Unit

H.1.1 Calculation of Maximum Working Pressure and Maximum Working Flow of

the Oil Pump

The maximum working pressure of the oil pump shall be calculated according to

Formula :

Where,

The rated working pressure of the oil cylinder;

: The total pressure loss of the system; it is usually selected 5%-10% of

the rated working pressure.

The maximum working flow of the oil pump can be calculated according to:

Where:

: The maximum working flow of the oil cylinder working at the same

time;

K: the leakage coefficient of the system; 1-1.3;

The rated pressured of the hydraulic pump shall be greater than or equal to 1.25P 1. If

there are test behaviors, the requirements on the test pressure shall be met.

H.1.2 Calculation of the Electromotor Power

The driving power (P) of the hydraulic pump shall be calculated according to:

Where,

: The driving power of the hydraulic pump, kW;

: The maximum working pressure of the oil pump, MPa;

: The maximum working flow of the oil pump, L/min;

: The total efficiency of the hydraulic pump; it shall be selected according to

Table H.1.

Table H.1 The Total Efficiency of the Hydraulic Pump

Type of the

Hydraulic Pump

Gear Wheel Pump Vane Pump Plunger Pump

Total Efficiency

H.2 Calculation of the Diameter and Wall Thickness of the Oil PipeH.2.1 Calculation of the Diameter of the Oil Pipe



The internal diameter (d) of the oil pipe shall meet requirements on the flow and flow

speed. It shall be calculated according to:

Where:

: The internal diameter of the oil pipe, mm;

: Working flow, L/min;

: the permissible flow speed, m/s (for the oil suction pipe,

, for the pressure oil pipe, , for

the stub pipe, and for the short pipes and partial

shrinking place, .

H.2.2 Calculation of Wall Thickness of the Oil PipeThe wall thickness ( ) of the oil pipe shall be calculated according to:

Where:

Wall thickness of the oil pipe, mm;

: The maximum working pressure of the oil pipe, MPa;

: The internal diameter of the oil tube, mm;

: The permissible stress of the oil piper; it shall be calculated according to

Formula (H.6). For the copper pipe,

: Tensile strength, N/mm2;

: Safety factor;

H.3 Calculation of the Sealed Frictional Resistance

The frictional resistance (Pv) of the lock ring shall be sum of the plunger sealing and

piston rod sealing frictional resistances. It shall be calculated according to:

Where,

Frictional resistance, N;



The pressure difference on both sides of the piston packing, Mpa;

: The pressure difference on both sides of the piston rod packing, Mpa;

: the internal diameter of the oil cylinder, mm;

The external diameter of the piston rod, mm;

: the effective height of the plunger sealing;

: The effective height of the piston rod packing, mm;

The friction factor of the lock ring; it shall be 0.06-0.2;

The frictional compensation coefficient of the piston packing;

The frictional compensation coefficient of the piston rod packing ring; for

the O-type lock ring, For the impaction lock

ring,: For the lip lock ring,:

H.4 Main structural dimensions of the oil cylinders are recommended as follows:

H.4.1 The length (l) of the rod bush shall be 0.8-1.5 times of the diameter of the piston

rod. If it is tilt or horizontally arranged, the larger value shall prevail. The guide

distance (under the full extension state of the piston rod, the distance from the center

of the guide sleeve of the plunger to the center of the rod bush) of the tilt or

horizontally allocated oil cylinder shall be greater than (D/2+H/20), But shall be no

less than three times of the diameter of the piston rod. D is the diameter of the plunger

and H is the journey of the hydraulic cylinder.

H.4.2 The width (b) of the plunger shall be 0.6-1.0 time of the internal diameter of the

oil cylinder.

H.4.3 During the initial selection, the diameter of the piston rod shall be 0.4-0.6 time

of the internal diameter of the oil cylinder. Then, the strength calculation and stabilitycalculation is carried out.

H.5 Strength Calculation of the Cylinder Wall

H.5.1 The cylinder wall thickness (d) shall be calculated according to the moderate

thickness of

Where,



The cylinder wall thickness, mm;

The rated working pressure of the oil cylinder;

The internal diameter of the hydraulic cylinder, mm;

The specific strength; for the seamless steel pipe,

The additional thickness considering the wall thickness tolerance and the

corrosion; commonly, it is rounded up to the nominal thickness;

The permissible stress of the cylinder material; MPa;

Where,

The tensile strength of the cylinder material; MPa;

safety coefficient

H.5.2 Conversion stress of section where is far enough from

flange and bearing flange shall be calculated according to:

where,

longitudinal stress,

Hoop stress,

The rated pressure in the cylinder.

Other symbols shall refer to Figure H.1.



Figure H.1 Calculation Schedule of the Cylinder Flange Strength

At the section of the cylinder and the flange joint, the strength calculation of the

cylinder wall shall be carried out by overlaying with the longitudinal stress and hoop

stress due to the evenly-distributed bending moment (M0). The reduced stress

shall be calculated according to:

Where,

The longitudinal principal stress;

Where, M0 is the evenly-distributed bending moment.

Hoop stress principal stress.

The Poisson ratio of the steel:

Other symbols shall refer to Figure H.1.

H.6 Calculation of the Piston Rod

H.6.1 The calculation of the piston rod with the single-action cylinder installed on

the rigid mount:

H.6.1.1 If there is no lateral displacement for the gate and the piston rod receives the

pull. The tension force can be calculated according to:

Figure H.2 Calculation Schedule of the Single-action Cylinder Rigid Mount Piston

Rod

Where,

The pull of the piston rod, N;



The maximum diameter of the piston rod section, mm.

H.6.1.2 If the lateral displacement happens to the gate (as shown in Figure H.2), the

piston rod will receive the pull and being moment. The stress of the piston rod shall be

calculated according to:

Where,


The minimum diameter of the piston rod section, mm;

The calculated bending moment of the piston rod;

The bending moment acting on the piston rod,

If the lateral displacement ( ) generated on the end of the piston rod, the

relevant horizontal force (the piston rod at the upper limit position), N;

Where,

The elastic modulus of the piston rod materials,

The moment of inertia of the piston rod section, mm4;

see Figure H.2, mm;

The bending moment due to the friction in the gate ear, It shall

be calculated according to:

Where,

The ax diameter of the gate ear, mm;

The friction factor at the piston rod ear; it shall be selected according to Table

H.2.

H.6.2 The calculation of the piston rod with the single-action cylinder installed on the

rotation mount:



The piston rod of the single-action cylinder installed on the rotation bearing, the

bending moment (Figure H.3) due to the friction between the rotation bearing and the

ear as well as the pull shall be received. The stress shall be calculated according to:

Where,


The minimum diameter of the piston rod section, mm;

The calculated bending moment of the piston rod critical section;

Where,


be calculated according to:

The bending moment due to the friction i the oil cylinder cylinder body

cylinder body rotation bearing,

Where,

The friction factor in the rotation bearing of the oil cylinder body shall be

selected according to Table H.2.

The supporting ax diameter of the rotation bearing, mm;

shall refer to Figure H.3; mm,



Figure H.3 Calculation Schedule of the Single-action Cylinder Rotation Mount PistonRod

Table H.2 Friction Factor (f) in Rotation Bearings

Friction Factor Bearing Type

Without lubrication Grease lubrication

Sliding Bearing Steel Vs Steel

Steel Vs Pig Iron

Steel Vs Gunmetal

Antifriction

Bearing

Ball bearing

Roller bearing

H.6.1 The calculation of the piston rod with the double-acting cylinder installed on the

rigid mount.

H.6.3.1 If there is no lateral displacement in the gate and the piston rod receives the

pull or pressure, the pull and compressive stress shall be calculated according to

Formula (H.11).

Where,

The pressure of the piston rod,N;

The diameter of the piston rod,mm;

the longitudinal bending coefficient. According to the flexibility ( ), it shall

be selected according to Table H.3



Where,

The reduced length of the piston rod, mm; it is related with the fixed form of

the oil cylinder body, as shown in Figure H.4.

Table H.3 The Longitudinal Bending Coefficient ( ) of the Piston Rod ReceivingPressure in the Center

Flexibility

λ

Material

0 10 20 30 40 50 60 70 80 90 100

1.00 0.99 0.97 0.95 0.92 0.89 0.86 0.81 0.75 0.69 0.60

1.00 1.00 0.98 0.95 0.93 0.90 0.84 0.80 0.74 0.66 0.59

Flexibility

λ

Material

110 120 130 140 150 160 170 180 190 200

0.52 0.45 0.40 0.36 0.32 0.29 0.26 0.23 0.21 0.19

0.43 0.38 0.32 0.28 0.27 0.24 0.21 0.19 0.17 0.15

Figure H.4 Calculation Schedule of Reduced Length of the Piston Rod

Figure H.5 Calculation Schedule of Stability of the Piston Rod

H.6.3.2 If the gate possible has the lateral displacement, the piston rod will receive the

pull (pressure) and the bending moment, considering the behavior (Figure H.5) of the

protruded oil cylinder of the piston rod. The stress shall be calculated according to

Formula (H.16). The stability shall be calculated according to Formula (H.17).

Where,

: the pull of the piston rod, N;

The calculated bending moment of the piston rod;



The bending moment acting on the piston rod,

the lateral displacement ( )generated on the end of the piston rod, N;

The elastic modulus of the piston rod materials, MPa;The moment of inertia of the piston rod section, mm4;


be calculated according to Formula (H.13):

please refer to Figure H.5, mm;

Where,

the permissible stress reduction coefficient during the longitudinal bending of

the piston rod. According to the conditions, the flexibility and the reduced

eccentricity rate ( ) shall be selected according to Table H.4.

The pressure of the piston rod,N;

The conditional flexibility shall be calculated according to:

Where,

Piston rod flexibility, The value shall be selected as

shown in Figure

The yielding point of the piston rod materials, N/mm2,

The safety factor of the piston rod materials, n=1.1-1.2;

The reduced eccentricity rate (m0) shall be calculated according to:

Where,

The influence coefficient of the sectional form; If If

,

Table H.4 Permissible Stress Reduction Coefficient Under the Longitudinal Bending

of the Piston Road Eccentrically Compressed



H.6.4 The piston rod of the double-acting cylinder installed on the rotation bearingsreceives the pull (pressure) force and the bending moment. The stress on the piston

rod shall be calculated according to Formula (H.14). Also, the stability shall be

checked according to Formula (H.10).

During the stability calculation, the conditional flexibility ( ) shall be calculated

according to Formula (H.18).

The reduced length (L0 shall be decided according to Figure H.6 and Formula (H.20):

If ,

If b>0.4m,



Figure H.6 Calculation Schedule of Double-acting Cylinder Rotation Bearing

Where,

: The inertia moment of the piston rod and the oil cylinder body section,

mm4;The reduced eccentricity (m0) shall be decided according to the bending moment

diagram feature (Figure H.3) of the piston rod, the ratio between bending moments on

both ends, the conditional flexibility and the relative eccentricity rate (m)

according to the Table H.5.

The relative eccentricity shall be calculated according to Formula (H.21):

Where,

The larger value between M1 and M2, the end bending moments.

The influence coefficient of the sectional form;

The stress of the piston rod, N;

During the calculation of the K=Mmin/Mmax, the smaller value of the M1 and M2, end

bending moments (absolute value) shall be Mmin and the larger, Mmax.The calculation of the piston rod of the horizontal type double-acting cylinder:

H.6.4 The piston rod of the double-acting cylinder installed on the rotation bearings

receives the pull (pressure) force and the bending moment. The stress on the piston

rod shall be calculated according to Formula (H.14). Also, the stability shall be

checked according to Formula (H.10). The load diagram and the bending moment

diagram of the piston rod shall refer to Figure H.7.

The bending moment M1 due to the friction in the ear shall be calculated according to

Formula (H.13):

The bending moment M2 due to the friction in the oil cylinder bearing shall be

calculated according to Formula (H.22):



Table H.5 Converted Eccentricity m0



Figure H.7 Horizontal Type Oil Cylinder Calculation Schedule

(a) Oil Cylinder Arrangement Plan

(b) When the door rotates the angle of , the load diagram and the bending moment

diagram.

(c) When the door rotates the angle of , the load diagram and the bending moment

diagram.

Where,

The bending moment due to the friction on the shaft neck of the rotation

bearing beam;

The moment to the oil cylinder rotation center from the friction of the tail

bracket.

The gross weight of the oil cylinder including the hydraulic oil.The diameter of the end weight bearing wheel, mm;

The diameter of the wheel and axle of the end weight bearing wheel, mm

The force arm of the rolling friction; it shall be 0.5mm-0.6mm;

The friction factor of the rotation shaft neck; it shall be selected according to

Table H.1.

The radius from the tail weight bearing wheel to the oil cylinder rotation

center, mm;



During the stability calculation, the conditional flexibility ( ) shall be calculated

according to Formula (H.21).

The reduced length (L0) shall be decided according to Figure H.6 and Formula (H.20):

The relative eccentricity shall be calculated according to Formula (H.21):the converted eccentricity (m0) shall be decided according to the bending moment

diagram feature (Figure H.7), the ratio between bending moments on both ends, the

conditional flexibility ( ) and the relative eccentricity (m) in Table H5.

H.7 Pollution Class of Hydraulic Oil

Pollution Class of Dubbing Solid Particles in ISO4406, please refer to Table H.6.

H.7 Pollution Class of Dubbing Solid Particles in NAS1638 shall refer to Table H.7.

Pollution Class of Actuating Medium Actuating Medium Solid Particles for the

Hydraulic Pressure System in GB/T 14039 shall refer to Table H.8.

Table H.6 Pollution Class of Dubbing Solid Particles in ISO4406



Table H.7 Pollution Class of Dubbing Solid Particles in NAS1638

(granularity in 100ml)

Table H.8 Pollution Class of Hydraulic Pressure System Hydraulic Pressure System

Actuating Medium Solid Particles

Table H.8 (continued)





Annex J (Informative) Materials for Calculating Stability of Two-way or

One-way Bending Members

J.1 Materials for Calculating Stability of Two-way or One-way Bending Members

The stability of the two-way or one-way bending members shall be calculated

according to Formula (J.1), (J.2) and (J.3). It shall also be in accordance with:

Where,

The calculated axial pressure, N;

The axial compression member stability factor selected according to the

maximum length-diameter ratio of the structure or the maximum presumed one; it

shall look up in Table J.1 and J.2.

The compensation factor for the axle load stability shall be calculated

according to Formula (J.4) or looked up in Table (J.3) and Table (J.4). The

smaller value of the Euler critical load Nex and Ney. They shall be calculated according

to the following formula:

The gross sectional area of the structure, mm2;

refers to bending moment of end of structural component,



refers to maximum bending moment caused by transverse load in

structure; when Mh is reverse against M0 and , shall adopt

zero,

Wx and Wy refer to resistance moment of section of structural component, mm3;

refers to ingral stability coefficient of bending component; components that

comply with conditions listed clause 1 of 9.5.3 , shall be 1, those that fail to

comply with the conditions, value of can be selected according to Table J.8 and

formula J.9.

refers to conversion coefficient of different end bending moment; it

can be calculated according to formula J.5 and J.6;

refers to ratio of end bending moment borne by two ends of

component; they shall carry their own signs and their absolute value shall not exceed

1.

refers to bending coefficient of transverse load; when transverse load is a

concentrated force, And it shall be 1 in other conditions;

refers to influence coefficient of end bending moment winding strong shaft

to end bending moment winding weak shaft; when section is of closed type,

slenderness ratios of section or structural component with strong

anti-twisting performance are same, can adopt 1; in general condition,

shall be greater than 1, and it can be calculated according to formula J.7;

refers to coefficient, see Table J.5 and J.6;

refers to coefficient; it shall adopt 0.15 for section with common open.



Table J.1 Stability Coefficient of Q235 Steel Axial Central Compression Component



Table J.2 Stability Coefficient φ of Q345 Axial Central Compression Component



Table J.3 Correction Coefficient ψ of Axial Compression Stability of Q235 Steel



Table Correction Coefficient ψ of Axial Compression Stability of Q345 Steel



Table J.5 a Value of I-shaped Section



Table J.6 a Value of Groove Section

for space truss component, can adopt 1 during calculation; and

additional bending moment formed by primary displacement of

structural component caused by manufacturing error can be added into second

bending moment and the third bending moment in formula J.1.

J.2 Whole Stability Calculation of Bending Component

When bending component can not comply with condition of clause 1 of 9.5.3, whole

stability of component can be verified according to formula J.1 and J.2; value can

be selected according to Table J.7 or be calculated according to formula J.8 and J.9.

of bending component with I-shaped combination section

If component section is of I-shaped combination section, whole stability coefficient of

bending component can be calculated according to formula J.8:

Table J.7 Whole Stability of Double-end Simply-supported Structure of Common

Rolled I-shaped Steel

Free lengthLoad condition Grade

of

I-shaped

2 3 4 5 6 7 8 9 10



steel

10-20 2.0 1.30 0.99 0.80 0.68 0.58 0.53 0.48 0.43

22-32 2.4 1.48 1.09 0.86 0.72 0.62 0.54 0.49 0.45

Upper

flange

36-63 2.8 1.60 1.07 0.83 0.68 0.56 0.50 0.45 0.4010-20 3.1 1.95 1.34 1.01 0.82 0.69 0.63 0.57 0.52

22-40 - 2.80 1.84 1.37 1.07 0.86 0.73 0.64 0.56

Component

without

lateral

supporting points

within span

Action

position of

concentrated

loadLower

flange

45-63 - - 2.30 1.62 1.20 0.96 0.80 0.69 0.60

10-20 1.7 1.12 0.84 0.68 0.57 0.50 0.45 0.41 0.37

22-40 2.1 1.30 0.93 0.73 0.60 0.51 0.45 0.40 0.36

Upper

flange

45-63 2.6 1.45 0.97 0.73 0.59 0.50 0.44 0.38 0.35

10-20 2.5 1.55 1.08 0.83 0.38 0.56 0.52 0.47 0.42

22-40 - 2.20 1.45 1.10 0.85 0.70 0.60 0.52 0.46

Component

without

lateral

supporting

points

within span

Action

position of

evenly

distributed

load

Lower

flange

45-63 - - 1.80 1.25 0.95 0.78 0.65 0.55 0.49

10-20 3.2 1.39 1.10 0.79 0.6 0.57 0.52 0.47 0.42

22-40 3.0 1.80 1.24 0.96 0.76 0.65 0.56 0.49 0.43

Component with lateral supporting

point within span, no matter where

load is added. 45-63 - 2.20 1.38 1.10 0.80 0.66 0.56 0.49 0.43



Note:

1. Note: Concentrated load refers to the condition where a few concentrated loads are added

within 1/3 scope of midspan; loads in other conditions shall be considered as evenly

distributed load.

2. of tolled I-shaped steel shall be adopted according to this table; when is

greater than 0.8, shall be selected according to Table J.8 to substitute .

3. This table is only applicable to Q235 steel; when values listed in this table are used in steel of

other grades, selected from table shall multiply ( , N/mm2).

4. when is not less than 2, whole stability needs not to be verified; if values are

greater than 2.5 times values listed in this table, they shall be converted. Values of

that are not listed in this table are greater than 3.60.

Where,

refers to whole stability coefficient; when calculation result is greater than 0.8,

its value shall be selected from Table J.8;

K2 and k3 refer to coefficients, and their values shall be selected from Table J.9 and

Table J.10;

K1 refers to coefficient, and its value shall be selected according to the following

provisions:

For double-end simple supported member with axially-symmetrical combination

sections:

When ,

When ,

For double-end simple-supported components having reinforced compression flange

plate and axial-symmetric web plate:

When ,

When ;



For double-axle symmetrical cantilever component with combined section k1 = 1;

Where,

refers to thickness of web plate, mm;

refers to thickness of compression flange plate, mm;

y refers to distance from axel to fiber bearing maximum pressure, mm;

I1 and I2 refers to inertia moment of compression flange and tension flange to y axis,

mm4;

l refers to free length of compression flange of component, mm;

b refers to width of compression flange, mm;

h refers to height of component, mm;Ix and Iy refer to inertia moment of section to x axis and y axis, mm4;

refers to yielding point of steel material, N/mm2, Q235 shall adopt 240N/mm2.

Table J.8 Stability Coefficient



Table J.9 Coefficient K 2 and K 3 of Double-end Simple-supported Component with

I-shaped Section

Component without lateral

supporting points within spanConcentrated

load

Evenly

distributed

load

Component with lateral

supporting point withinspan, no matter where

load is added.

Coefficient

Along

upper

flange

Along

lower

flange

Along

upper

flange

Along

lower

flange

Double-axle

symmetrical

section

Single-axle

symmetrical

section

K2 1480 4750 1350 360 2360 1970

K3 1200 1200 1040 1040 1180 980

K2 460 3730 460 2710 1450 1210

K3 2400 240 2080 2080 2240 1870

Note: Concentrated load refers to the condition where a few concentrated loads are added

within 1/3 scope of midspan; loads in other conditions shall be considered as evenly

distributed load.

Table J.10 Coefficient k1 and k2 of Component with I-shaped Equal-section

Cantilever Action position of concentrated load K1 K2

480 1330Upper

flange

-300 2890

Section center 2650 2500

Lower flange 5690 1350

Note: this table is applicable conditions where free end of

component is fixed due to that concentrated load is added.

J.2.2 φw Value of Rolled Groove Steel with Simple Support

If the terminal of component section is made of rolling channel steel, the calculation

of the steadiness coefficient of load type and holding position shall base on Formula

J.12, but the steadiness coefficient shall not more than 1.0.

Symbols as above.

J.3 Local stability calculation of steel plateJ.3.1 The calculation on the critical stress of compression stress (σ1), shearing strength



(τ) and local crushing stress ( ) shall according to Formula J.13, Formula J.14, and

Formula J.15:

Where:

Critical compression stress

Critical shearing stress

Critical local crushing stressPlate edges elastic coefficient. From the range of 1 to 1.26, while one side

under the transverse pressure of marginal plate or the longitudinal extended

end-plate, choose the maximum value.

The flexion coefficient of simply supported on four sides plate,

depend on the side ratio (a/b) and the side load, base on Table J.11 to calculate out the

flexion coefficient, and the ribbed plate refer to Table J.12.

Euler stress calculation shall base on Formula J.16:

Where:

Thickness of plate, mm；

Width or height of plate, mm。

If the ribbed stiffener conform to the requirements of dimension, that can calculate the

stability of partial section, as well as the stability of partial section and the ribbed plate.

J.3.2 The calculation on the critical combined stress of compression stress (σ1),

shearing strength (τ) and local crushing stress () shall according to Formula J.17

Where:



The signification of ψ refer to Table J.11

Particular case：

While local pressure affect on the fringe of plate, during calculation, the value of

or will set down as o. If the critical combined stress (include the particular

case as above) over 0.75σ5, according to Formula J.18 to calculate the reduced critical

combined stress.

Where:

Yield point of materials

J.3.3 Allowable stress of local stability and the calculation of local stability:

The calculation of allowable stress of local stability base on Formula J.19 or Formula

J.20. when ,

If , then

Table J.11 Flection coefficient of local clapboard

No. Load condition a＝a/b K

1 uniform or

nonuniformity

compression

2 uniform or

nonuniformity

compression

3 flexion

mainly caused

by pressure Flexion coefficient (No. 1) while

Flexion coefficient (No. 2) while



4 Pure shear

5 single side

partial

compression

Note: if a>3, base on a＝3b to

calculate the value of α, β and

K m

6 double side

partial

compression K m ——base on No.5 to

calculate the value of K m’

Notes: 1 is the maximum crushing stress of plate, is the stress ratio of two

terminals; respective with the value of positive or negative.

2 To the lengthways ribbed stiffener whose web plate under the partial pressure, the flection

coefficient of above section can refer to the No.6 item of Table J.11; the flection coefficient of

bellow section can refer to the No.5 item if the extended width of partial pressure is confirmed.

For two or more lengthways ribbed stiffeners, the calculation of flection coefficient also refer to

above principles.

Table J12 Flection coefficient of sheet with ribs

No. Load condition K

1 Compression

2 Pure shear Table K τ

While the width of plate was



divided equally by stiffening ribs

3 Partial

compression

K m’——base on No.5 to calculate

the value of K m’

Note: , ——the inertia moment of ribbed stiffener to the central

axial of plate, ；

——cross-sectional area of ribbed stiffener, ；

r——The quality of compartments of ribbed stiffener ；

（μ is the Poisson ratio of materials）

Where:

n——safety factor, set down as 1.5 for I type load and 1.3 for II type load;

σq ——Imaginary proportional limit, chooseσ5.

The calculation of partial stability shall base on Formula J.21.

Annex K (Informative Annex) Overload check of motor

K.1 Hoisting mechanism motor

Where:

Pn ——Motor rated power while adjusting the load duration factor, kW；

P——Hoisting load, N;v——Raising speed, m/s；

η ——Total efficiency of mechanism；

λm ——Allowable overload multiples of motor torque while adjusting the load

duration factor (rated value or actual value of technical provision).

H——Coefficient; base on the voltage loss (alternating current motor is 15%, without

regard to continuous current motor), allowable error of maximum running torque or

locked-rotor torque (winding type asynchronous motor is 10 ％ , cage type

asynchronous motor is 15％ and without regard to continuous current electromotor),

and hoisting 1.25 times of rated load, the H of winding type asynchronous motor setdown as 2.1, cagy type asynchronous motor set down as 2.2 and continuous current



electromotor set down as 1.4;

m——Quality of motor 。

K.2 Running mechanism motor

（K.2）

Where:

PgΣ ——The gravitation of all motion parts, N；

ω ——Coefficient of friction drag, see Table 5.6.7；

m0 ——Coefficient of slope drag, the roadway laying on reinforced beam or steel

beam set down as 0.001;

Pw——Wind resistance, N, according to the maximum calculated wind pressure (qII)

of working order as detailed in Item 6.6, indoor Pw set down as 0;

——Total flywheel moment of mechanism. The sum of each flywheelmoment on the mechanism of motor shaft, kg·m2

v0 ——Velocity of gate hoist (or trolly), m/s;

n——Rated speed of motor, r/min；

ta ——Mechanism starting time, s;

λa ——Average per unit value of pull-in moment (relative to the rate moment while

adjusting the load duration factor), winding type asynchronous motor set down as 1.7

(or 1.0 while adopt frequcncy sensitive rheostat); cage type asynchronous motor set

down as 0.9λm; series excitation continuous current electromotor set down as 1.9;

D.C. compound generator set down as 1.8, independent excitation DC motor set down

as 1.7. The value of λa can be improved while adopt current self-adjusting system.

Other symbol as shown in Formula K.1

K.3 Rotation gear motor

Where: H——Coefficient, winding type asynchronous motor set down as H＝1.55,

cage type asynchronous motor set down as H＝1.6 and DC motor set down as H＝1;

Mf ——Rotating frictional resistance moment, N·m

Mi ——Maximum rotating slope moment of resistance, N·m； Mw——The maximum wind resistance moment caused by calculated wind pressure,

N·m；

Ma ——The rotating horizontal resisting moment which caused by the swing angle a1

(see Item 6.4.2) of carrying rope, N·m

i——Mechanismic resultant gear ratio.

Other symbols as shown in Formula K.1 and Formula k.2.



Annex L (Informative Annex) Heating inspection of winding-type asynchronous

motor

L.1 The calculation formula of each parameter

L.1.1 Average power of steady stateL.1.1.1 Electromotor for hoisting mechanism

Where

P5 - Average power of steady state, kW;

G - Mean coefficient of steady-state load,G1＝0.7, G2＝0.8, G3＝0.9, the

rating of G see Table N.1 of Annex N;

The rest symbols are the same with the formula (K.1) in Annex K.

L.1.1.2 Electromotor of running mechanism

Where:

G - Mean coefficient of steady-state load, G1＝0.75, G2＝0.80, the rating of

G see Table N.1 of Annex N;

Pw - Wind resistance, N, Calculated as the wind pressure of the gate hoist

under the normal operating status;


L.1.1.3 The electromotor of traversing mechanism

Where:

G - Mean coefficient of steady-state load, G1＝0.60, G2＝0.60, The rating of G

see Table N.1 of Annex N;

M1 - The resistance torque of the equivalent ramp caused by inclination, N·m;

Mw - Equivalent wind resistance torque calculated according to the calculating

wind pressure q1 (see Article 6.6.3); N·m;


L.1.2 Dynamic power

Where

Pa - Dynamic power, kW

Ta - The mechanism starting time under normal operating conditions, s;

The rest symbols are the same with the formula (N.2) in Annex N.

L.1.3 CZ value

L.1.3.1 Converted to the full start times



Where

Z - Converted full start times per hour;

d0 - Full start times per hour;

di - Startup or incomplete startup times per hour;

f - Electric retarding times per hour;g, τ- Conversion factor, generally take the values stated in Table L.1;

Table L.1 g, τ

Coefficient g τ Winding-type asynchronous motor 0.25 0.5

L.1.3.2 Inertia increment rate

Where:

C - Inertia increment rate,

-Flywheel torque of electromotor, kg·m2;

-Flywheel torque converted to the motor shaft from the moving quality and

rotating quality out of electromotor, kg·m2。

L.1.3.3 CZ value

CZ value, the result of the inertia increment rate C multiplying the converted full start

times per hour, is the important parameters impacting the heating of electromotor under startup and braking status.

L.2 Heating verification

For the convenience of application, Annex M lists the allowable output power of

YZR series winding-type asynchronous machine under different load duration

factors (FC values) and under different CZ value. If P ≥ Pa (average power of

steady state), then heating checkout of electromotor is eligible.



Annex M (Informative Annex) The allowable output capability (P) of YZR series

electromotor under different load duration factor (FC value) and under different

CZ values (the average startup multiples K= 1.7)











Annex N (Informative Annex) The electromotor of gate hoist



mechanism FC, CZ and G values in the capacity selection calculation

N.1 The load duration factor FC value, CZ value and mean coefficient of steady-state

load G of each components of different gate hoists shall be calculated according

to the actual load. If the details of the load condition is not available, then it can be selected from Table N.1.

Table N.1: FC value, CZ value and G value

Chain-type fixed winding type MobileType

Hoisting device

Revolution hoisting

mechanism

Trolley running

mechanism

Cart running

mechanism

Traversing

mechanism

Note: the load duration factor of mechanism PC value is designed for the occasions that the working

cycle length shall not be less than 10 min, and calculated according to the following formula:

％100running

×=cycleworkingaof timetotal

cycleworkingainmechanismof timeFC



Annex P (informative annex) Current-carrying capacity of conducting w

P.1 The computing formula of current-carrying capacity of conducting wire

Where:

Iz - Current-carrying capacity of conducting wire, A;

Ka - The laying correctness factor of cables or tube-through wires, generally, the correctness factor of tu

cable is 0.8;

Kt - The ambient temperature correctness factor and normal value see Table P.1. Kt value can be calcula

T1 - The maximum operating temperature of wire core; ;℃

T0 - Working environment temperature, ;℃

T2 - Rated working environment temperature, 25℃（or 45℃）;

Kj - The load duration factor correctness factor of repeated short-time duty system, the working cycle tim

value see Table P.2. Kj value can be calculated according to Formula (P.3);

FC - Load duration factor;

T - The heating time constant of conducting wire, the accepted value see Table P.3; s;

Ig - The baseline value of wire current-carrying capacity, the accepted value see Table P.3, A.



Table P.1: the temperature correction factor Kt of the current-carrying capacity of con

Working environment tRated working

environment

temperature,℃

The maximum operating

temperature of wire core;

℃

+25 +30 +35 +40 +45 +50

+60 1.000 0.926 0.845 0.756 0.655 0.535

+65 1.000 0.935 0.865 0.791 0.707 0.612 0+25

+70 1.000 0.943 0.882 0.816 0.745 0.667 0

+65 － 1.323 1.225 1.118 1.000 0.866 0

+70 － 1.265 1.183 1.095 1.000 0.894 0

+75 － 1.195 1.134 1.069 1.000 0.926 0+45

+80 － 1.173 1.118 1.061 1.000 0.835 0

Table P.2 the load duration factor correctness factor of conducting wire,

Wire core section mm2 Conducting wire model

Load

continuity 1.5 2.5 4 6 10 16 25 35

25% 1.313 1.417 1.477 1.50 1.614 1.678 1.754 1.790 1BX, BXR copper core, rubber

thread 40% 1.149 1.212 1.249 1.296 1.336 1.377 1.425 1.448 1

25% 1.250 1.304 1.324 1.398 1.461 1.520 1.604 1.645 1CYYCW, CF, CFR

single-core cable 40% 1.111 1.143 1.155 1.200 1.240 1.277 1.330 1.356 1

25% 1.490 1.531 1.590 1.640 1.696 1.750 1.808 1.803 1YC, YCW, CF, CFR

three-core cable 40% 1.258 1.284 1.321 1.353 1.388 1.422 1.460 1.456 1



Table P.3 baseline value of current-carrying capacity of conducting wire

Copper core cable Heavy type cabtyre cable

BX, BXR copper

core, rubber thread

BV, BVR copper

core plastic wire

YC, YCW

single-core cable

YC, YCW three-core

cable

CF,

Current-carrying capacity A at 25℃

Heating timeconstant, s

Wire

core

section

mm2

Ope

n

layi

ng

Tube-thro

ugh b

Ope

n

layi

ng

Tube-thro

ugh

Ope

n

layi

ng

Tube-thro

ugh

Current-carr

ying

capacity A

at 25℃

Heatin

g time

consta

nt, s

Current-carr

ying

capacity A

at 25℃

Heatin

g time

consta

nt, s

Curr

y

cap

at

1.5 27 18 24 17 86 184 －－－－

2.5 35 25 32 24 116 248 37 179 26 347

4 45 33 42 31 138 295 47 190 34 419

6 58 43 55 41 172 368 52 235 43 497

10 185 60 75 57 212 453 75 282 63 613

16 110 77 105 73 267 571 112 336 84 774

25 145 100 138 95 370 791 148 438 115 1050

35 180 122 170 115 442 945 183 506 142 1020

50 230 154 215 146 573 1230 226 626 176 1270

70 285 193 265 183 641 1370 289 746 224 1540 2

96 345 235 325 225 797 1700 353 917 273 1870 2

120 400 270 375 260 820 1750 415 1040 316 2180 2

150 470 310 430 300 980 2090 －－－－



a The aforesaid figures are abstracted from section 26, Electrical Engineering Manual (1979, Probation version), taking c

current-carrying capacity at +25 (or +45 ) ambient temperature as bas℃ ℃ eline values.

B. In the table, the current-carrying capacity of tube-through wires is based on that three single-core wire pass through the

procedure, the cable used in gate hoist, no mater its wiring mode, laying position, generally adopt three single-core wire tothree, the adopted section shall properly decrease the current-carrying capacity.



Annex Q

(Informative Annex)

Explanations on the Text Description

Q.1 Wording explanation

Table Q.1 Wording explanationExtent Positive Negative

Very strict Must Strictly prohibit

Strictly do under normal

condition

Shall "shall not" or "be request

not to"

Allow a few of selections,

but can do so under the

available conditions firstly

"it's appropriate to" or

"generally"

It's not inadvisable to

It shall do under general

conditions but it has some

difficulties to do so due to

the technical-economic

reasons

As much as possible

Can do under some

conditions

It's approved to

Q.2 In the context, the specified standards, specifications or the other relevant

regulations shall be carried out, the statement is "carry out ...according to", or

"meet the requirements of ..."; for the non-compulsive enforcement of the

specific standards, specifications and the other provisions, the statement is "makereferences to".

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Design Specification of Hoist for Water Resources and Hydropower Engineering

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