About the Efficiency of the Regenerator in the Stirling Engine

27/3/2014 About the Efficiency of the Regenerator in the Stirling Engine

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About the Efficiency of the Regenerator in the Stirling Engine

and the Function of the Volume Ratio V max / V min

Dipl.-Ing. Peter Fette

Am Schaeferloch 16,

D-75045 Walzbachtal / Germany

ABSTRACT:

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The twice double acting Stirling Engine introduced at the 6'th International Stirling Engine Conference ISEC at Eindhoven Netherlands in May 1993 (ReportNo. ISEC-93003) is an engine which can realize realative high volume ratios V max / V min . Whenever a heatsource and a cooling water supply and their

corresponding haetexchangers have enough power for the energy transmission then a higher volume ratio of V max / V min will lead to a higher work output per

revolution. Theoretical work is done with regard to the efficiency of the regenerator, the volume ratio of the engine and the adiabate exponent k = Cp / Cv of

the working fluid. It can be shown, that the efficiency of the regenerator can be lowered for the benefit of a lower loss of pressure in it. For very high volumeratios the regenerator can be a suitable tube only. Formulas and diagrams illustrate the correlation of Carnot efficiency and the thermal efficiency of the

process with the parameters: volume ratio Vmax/V min, k and the regenerator efficiency hreg .

All diagrams and calculationen were made with the program STMOT2 |6|, base of this program is described in |7|

Nonenclature:

Cp Specific heat of working fluid at constant pressure

Cv Specific heat of working fluid at constant volume

k Adiabate exponent; the ratio of the specific heats k = Cp/ CvM GAS Mass of working fluid within the engine.

hC Carnot efficiency of the ideal process hC = (TE-TC) / TE

hreg Regenerator efficiency

RV Loss factor for the regenerator: RV = 1 - hreg htherm Resulting thermal efficiency of the process

Q1-2 Heat rejected by the cooler at the compression phase of the ideal Stirling engine at "TC". For the indexes 1-2-3-4 look to Fig. 3

Q2-3 Isochoric heat supplied at Vmin

Qreg external isochoric heat supplied at V min if the regenerators efficiency is hreg < 1, then Qreg = (1- h reg ) * Q2-3 = RV * Q2-3Q3-4 External heat supplied at the expansion phase of the ideal Stirling engine at "TE"

Q4-1 Isochoric heat rejected at Vmax R Gas constant: R = Cp - Cv S Entropie of the working fluid

TC Constant cold Temperature of the working fluid in the compression space of the ideal Stirling engine

TE Constant hot Temperature of the working fluid in the expansion space of the ideal Stirling engineVE stroke volume of the expansion cylinder

VC stroke volume of the compression cylinder

VG total instantaneous gas volume in the engine inclusive all dead spacesV max is the maximum volume of all working spaces in the engine (including heater, cooler and regenerator)

V min is the minimum volume of all these spaces

V max / V min the volume ratio.

W Usable work output per cycle

WE Work done during the expansion phaseWC Work to be supplied during the compression phase.

The theoretical considerations of Finkelstein |2| were a challenge to make further theoretical and practical investigations for the Stirling engine decribed in |1|.

So this theoretical work is specially done for this engine. The results may not be transfered in all consequences to other Stirling engines, but the tendency ofthese results should be valid for other engines too.



In the engine |1| a change of the volume ratio is easy to be performed by variation of the working liquid within the cylinders below the gas cushion. Insofar thisengine is an optimal testengine too. There are some reasons that a regenerator for this Stirling engine cannot be optimally designed in the common way. E.g.

because of too much loss of pressure in the regenerator, and, for this engine is able to work with compound fluids, a commonly designed regenerator will not

work with condensating steam, it has additional disadvantages too. A regenerator designed for this engine will work at a loss! But the questions to beanswered are: What a loss at the regenerator is tolerable, and what can we do to increase the thermal efficiency with others than an optimal commonly

designed regenerator?

These are the common questions. There have been done a lot of theoretical invetigations on this territory, some described in |3|. This work will not only add

one more, but it makes an attempt to give an other point of view to these questions, naturally with special attention to the engine of |1| for heatsources of lowto medium temperatures.

Going out from an ideal isothermal Stirling process we introduce the effectiveness of the regenerator to this process and then call this process the

"disidealized" isothermal Stirling process having a variable efficiency of the regenerator |5|.

The thermal efficiency of a process is defined as the ratio between "W" the external work done per cycle and "Qext" the external heat supplied per cycle to the

engine.

(1)

Concerning all phases the efficiency of the ideal Stirling process is:

(2)

In this ideal Stirling process it is supposed, the regenerator is of 100 % efficiency; hreg = 1 . Then the isochoric heat supplied by the regenerator

Q2 - 3 at constant volume V min is equivalent to the isochoric heat Q 4 - 1 that is received by the regenerator at constant volume Vmax.

So Q 2 - 3 + Q4 - 1 = 0. and the external supplied heat for the ideal process is: Qext = Q3 - 4 . Now the ideal efficiency is:

(3)

Imagine a disidealized Stirling process with a regenerator at a loss. h reg < 1 . We define a lossfactor RV = 1 - h reg .

Now imagine that the work "W" done per cycle should be the same for the ideal as for the disidealized process. Then for the case of hreg < 1 additional heat

must be supplied by the heater to get the temperature "TE" at the end of the isochoric change of state done by the regenerator and before beginning the

isothermal expansion. And at the other isochoric change of state, -cooling done by the regenerator- additional heat must be rejected by the cooler to get the

temperature "TC" before beginning the isothermal compression phase at Vmax. This part of the energy which the regenerator cannot supply to the process may

be defined as Q reg = RV * Q2-3

With these considerations we now define a thermal efficiency of the disidealized process:

(4)

We now must get this equation in a suitable form by evaluating the above expressions: Q 3 - 4 the heat supplied at the isothermal expansion phase is equal to

the external work done during isothermal expansion:

(5)

for the compression phase:

(6)

The isochoric heat supplied at Vmin is:

(7)

We now get for h therm



(8)

We make further substitutions:

Carnot efficiency h C = ( TE - TC) / TE .

The adiabate exponent k = C p/ C v and the gas constant R = C p - Cv

leads to the term C v / R = 1 / (k - 1).

We now get h therm in the wanted form for computer calculations:

(9)

The meaning of equation (9) is:

The resulting thermal efficiency of a disidealized Stirling process -that is an isothermal Stirling process with a regenerator at a loss of RV= 1 - h reg - is a

function of:

1. its Carnot efficiency h C depending on the maximum "TE" and minimum "TC" temperatures within the process.

2. its regenerator efficiency h reg resp. the regenerator loss: RV = 1 - h reg3. its volume ratio V max / V min4. the adiabate exponent k of the working fluid; where:

k = 1.6 for one-atomic gases like Helium, Argon,

k = 1.4 for two-atomic gases like Hydrogen, Air,

k = 1.3 for three-atomic gases like Carbondioxyd CO 2

Fig. 1 represents the calculation of Equation (9) for 5 different volume ratios:

Vmax / Vmin= 1.2, 1.6, 2.5, 5.0 and 10. and for

2 regenerators:

one regenerator at an efficiency of hreg = 50 %

and one "null" regenerator (hreg = 0 means: The regenerator is a tube only).

The working fluid is air for all cases k = 1.4 .

The abszissa in this diagram is the Carnot efficiency in the range from 5



of the working fluid, which is also important for the efficiency of the process. But on the other hand if You design a slow rotating engine as described in |1|

with an optimal heattransfer to the working fluid, Argon will be the better working fluid than air inspite of its slightly worse thermal conductivity. (Naturally the

more expensive inert gas Helium is the best for its thermal conductivity is atleast 4 times better than that of air !)

For the engine described in |1| a FORTRAN 77 computer program STMOT2 |6| is develloped for the calculation and graphical output of several 100

functions of interrest.

Fig.3 and Fig.4 show two individual T-S diagrams for the same engine:

In Fig.3 the working fluid is Air with k = 1.4 , and

In Fig.4 the working fluid is Argon with k = 1.6 .

The effect of the different k's is best seen in the gradient of the isochoric change of state lines (2-3) and (4-1) in these both figures.

This gradient d T/d S is equal to :

(10)

The "frames" in both T-S diagrams represent the ideal isothermal Stirling process, the graph within the frame is the calculated T-S diagram of the real process

of this a - type engine |1| driven by a crankgear. In both cases the included area of the graphs represent the same external work done per cycle. Have a look

to the different gradients d T/d S of these "frames" which are borders of the isochoric heat.

The isochoric heat exchanged by the regenerator is much less at the "frame" in Fig.4 (Argon) than in Fig.3 with air as the working fluid.

The thermal efficiency htherm of the "calculated real process" is improved from h therm = 20.6 % in the case of the working fluid is Air to h therm = 23.7 % in

the case of Argon.

According to equation (9) the thermal efficiency h therm of the "disidealized" isothermal process -the "frames" in Fig. 3 and Fig. 4- is improved from h therm =

25.6 % in the case of the working fluid is Air to h therm = 29.1 % in the case of Argon.

The calculations |6| of the processes in Fig.3 and Fig.4 are both done with:

Phaseangle d = 90 for the real engines process; pure sinusodial piston movement; Dh=10. Dk=10. R=10. cm; hot and cold deadspaces are 30 % ofeach stroke volume. See input for STMOT2 |6|

Isothermal temperatures TE = 500 K, TC = 300 K.; h C= 40 % ; P0 = 5 bar

The regenerator efficiency in both cases is h reg = 50 %; regenerator volume VR=0.15 l,

The volume ratio in both cases is Vmax/ Vmin= 2.43

There are made 8 additional simulation runs with the computerprogramm STMOT2 to demonstrate the influence oft the idle pressure P0 (this is the gas

pressure within the resting and cold engine), the volumeratio V max / V min, the adiabatic exponent k and the regenerator efficiency hreg to the usable power

and the usable efficiency h_n of the engine. These results are presented in a table (Some more information to the output of STMOT2 see in |6|. The input

datasets for these 8 simulations are described in section "5 of sample calculations" . The reader may copy the input data from here to make his own

calculations with STMOT2)

All values of interest in the table for the working fluid Helium are marked red and are marked blue for the fluid air. Some more remarks are to be made:

In column 1 of the table RUN NO. points to the No. of the simulation run.

In column 7 : ETA_R is the regenerator efficiency hreg

In column 9 : P0 is the idle pressure P0 of the resting and cold engine; P1MEAN is the mean working pressure.

In column 10 : Vmax/Vmin is the volume ratio

In column 13 : ETA_N is the usable efficiency, which is written h_n in the signatures to Fig.(1)(2) and Fig.(5)(6).

In column 15 : POWER USABLE is the mean usable power for the calculated revolution.

In column 16 : DQZU1 MAX is the maximum of the graph for the supplied heat at this revolution. You will find more information to this table output in chapter I.6.2 of the user guide to STMOT2 (in german only).

The first 4 simulation runs concern the increase of usable power "POWER USABLE" as a reaction of the higher volumen ratio; run No (1) and run No (2) are

calculated for air with a k = 1.4 and run No (3) and run No(4) are calculated for Helium with a k = 1.6 . Here a short extract from the table

(1) idle pressure P0 =16 bar, regenerator efficiency hreg = 80 %, Vmax/Vmin = 2.71 ----> POWER = 1637 Watt, h_n =30.46 %


With Helium as the working fluid and equal conditions for the engine:


(4) idle pressure P0 =16 bar, regenerator efficiency hreg = 80 %, Vmax/Vmin = 1.29 ----> POWER = 343 Watt h_n =22.47 %



The strong increase of power from POWER = 343 Watt in simulation runs No. (2) and (4) to POWER = 1637 Watt in runs No (1) and (3) naturally is only

obtained when "heater" and "cooler" can perform the needed high energy transmissions !! The maximum values for the heat supplied "DQZU1 MAX" are in

column 16: of the table. For Helium as the working fluid a smaller maximum value "DQZU1 MAX" is calculated as it is to be expeted in accordance with

equation (9).

Fig.(1)(2) shows as functions of the crank angle the graphs for: supplied heat "DQZU1", the removed energy "DQAB1", the idle pressure P1 and the mean

power for the calculated revolution "POWERN". Here all graphs of runs No (1) and (2) with air as the workind fluid are put together in 1 diagram. The

signals (1) and (2) in Fig.(1)(2) are in accordance with these run No's. 1 and 2 of the table. The values for Helium are shown in the table at RUN NO. 3 and4.

In the next 4 simulation runs (5) and (6) with air and runs (7) and (8) with Helium the usable power of the engine shall be hold constant at 316 to 319 Watt. It

shall be shown here, that this power can be reached with a high volume ratio Vmax/Vmin = 2.71 at a significant lower idle pressure "P0"= 3.3 bar (or a

significant lower mean pressure "P1MEAN") and at a lower regenerator efficiency hreg= 40 %, than the same power is obtained with a lower volume ratio

Vmax/Vmin = 1.29 but with P0=15 bar and hreg = 80%. Next to this, the simulation shows the maximum point for the heat supplied "DQZU1_MAX" is

significant lower, when the engine works with this high volume ratio at this power of 316 - 319 Watt. Here again a short extract from the table

(5) usable power = 316 Watt, idle pressure P0 =3.3 bar, regenerator efficiency hreg = 40 %, volume ratio Vmax/Vmin = 2.71

---->h_n =19.59 % , maximal heat supplied "DQZU1_MAX" = 2496 Watt

(6) usable power = 319 Watt, idle pressure P0 =15 bar, regenerator efficiency hreg = 80 %, volume ratio Vmax/Vmin = 1.29


With Helium as the working fluid and the same usable power the simulation results are:

(7) usable power = 316 Watt, idle pressure P0 =3.3 bar, regenerator efficiency hreg = 40 %, volume ratio Vmax/Vmin = 2.71


(8) usable power = 319 Watt, idle pressure P0 =15 bar, regenerator efficiency hreg = 80 %, volume ratio Vmax/Vmin = 1.29


These simulation results seem to be impossible on the first view. A good way to explain this phenomenon of the results of runs no. (5) and (6) for air as the

working fluid will give the T-S Diagrams in Fig.(5)(6)TS, and for the runs (7) and (8) with Helium the T-S Diagrams in Fig.(7)(8)TS will give an explanation:The work done per revolution, is represented by the area included by the graphs in these diagrams. This work minus the friction losses result in the POWER

USABLE: 316 resp. 319 Watt. The areas included by the "frames" around the graphs, are equivalent to the work of the ideal Stirling process. If we now look

to the ideal Stirling processes for the simulation runs (5) and (6) (or to the runs (7) and (8)), then indeed we find a quite other result. The work done "Wi" of

the ideal Stirling process is equal to the numerator in eq.(8) -see obove:

Wi = M Gas * R * (TE - TC) * ln ( V max / V min )

here the gasmass "M Gas" is proportional to the idle pressure P0. By this the work of the ideal Stirling processes from simulation run (6) with the high idle

pressure P0 = 15 bar is significant higher as in run no. (5) where P0 = 3.3 bar. You easy will see, when comparing the "frames" in both diagrams of Fig.(5)

(6)TS (and in both diagrams of Fig.(7)(8)TS). The ideal Stirling process does'nt know deadspaces, the real Stirling process, in which acts a continuously

working crank gear, must consider the deadspaces. Now in the real Stirling process a high volume ratio -this means small deadspace- results in a high "load

exploitation factor" -here 37.11% of the ideal Stirling process is reached. (for the "load exploitation factor" also look to my unshortened report to the 6#th

ISEC in Eindhoven |1|.) The large deads pace, which is defined in the input data to simulation runs no. (6) and (8), here now leads to a smaller loadexploitation factor -here 8.73% of the maximal possible -the ideal- process, so you will only get nearly the same work done inspite of the higher mean

pressure resp. the higher idle pressure P0 as in runs no. (5) and (7). In column 13 of the table values for AUSN_I are these load exploitation factors.

The total gasmass in run no. (5) is GM01= 1.394851 gr air. This is a significant lower gasmass in the engine as in run no. (6) where the total gasmass is

GM01= 23.520571 gr air (see below columns 17 to 19 in theTabelle). Therefore heat to be supplied to warm up the gasmass in run no. (5) will be much

more lower. The maximal supplied heat you find in column 16 of the table with a value of "DQZU1_MAX" = 2496 Watt, and for the run no. (6) the maximal

heat supplied is "DQZU1_MAX" = 5266 Watt.

Like Fig.(1)(2) now the Fig.(5)(6) shows as functions of the crank angle the graphs for: supplied heat "DQZU1", the removed energy "DQAB1", the idle

pressure P1 and the mean power for the calculated revolution "POWERN". Here all graphs of runs No (5) and (6) with air as the working fluid are put

together in this 1 diagram. The signals (5) and (6) in Fig.(1)(2) are in accordance with these run No's. 5 and 6 of the table. The values for Helium are shown in

the table at RUN NO. 7 and 8.

The usable efficiency ETA_N in column 13 of the table is written in Fig.(1)(2) and Fig.(5)(6) with "h_n". These values can also be found for the Fig.(5)(6) at

the RUN NO. (5) and (6) in the table. Please notice the usable efficiency h_n = 19.59 % in RUN NO. 5 is a bit higher than in RUN NO. 6 where h_n =

17.89 % inspite of a higher regenerator efficiency in RUN NO 6. Here hreg= 40 % is half as large as hreg= 80 % in RUN NO 6.

(The usable efficiency "h_n" and the usable power "POWERN" take into account the mechanical friction losses of the engine. Therefore "h_n" is less than

htherm.)

Conclusion:

Each Stirling engine is wanted to have a high ratio h therm / h C ; this is specially wanted for those engines which are working with low to medium

temperatures. The regenerator of the engine|1| will work at a loss, when it should be designed for working with compound fluids. One possibility of equalizing

the regenerators loss in double acting engines is to design it as a counterflow heatexchanger as described in |1|.

A further improvement for a better h therm is got by a higher volume ratio Vmax / Vmin. This additionally can be achieved by following the rules in |2| with the

ratio of the stroke volumes in expansion and compression spaces made equal to their temperature ratio: VE/VC = TE/TC. See the section "4 of sample

calculations". (Raising the volume ratio Vmax /Vmin at least is limited by the effectiveness of the heatexchangers!)



A third but simple improvement will be to choose an one atomic inert gas rather than a two (or three)- atomic gas as the working fluid. (If in this sense Helium

will be better than Hydrogen -with its twice better thermal conductivity than Helium- is to be tested; but Argon should be better in this sense than air.)

Equation (9) is derived from a "disidealized" Stirling process with isochoric heat transmission at a constant volume. Concerning h therm, Vmax/Vmin and k the

calculations of the crankgear driven engine |1| are similar to the results of equation (9), because of the prerequisites coming from this engine are more qualified

for a comparisation of this process to the "disidealised" isothermal process than the more adiabatic processes of common Stirling engines:

Heater and cooler are not external, they are within the expansion space resp. within the compression space of this engine.

The heattransfer to the working fluid can be made nearly isothermal by irrigating the working fluid with a hot resp. with a cold working liquid |1|.

The deadspaces can be reduced essentially to the regenerator space only.

A new point of view for the calculation of the heatprocess of this engine shall be discussed here:

An isothermal change of state is defined by :

An adiabate change of state is defined by :

A polytrope change of state is defined by :

with the exponent n < k

The change of state in this process |1| may be defined by

The exponent e is less than the exponent for an adiabate or polytrope change of state. This, because the heattransmission here is extremly forced during the

expansion and compression phase; insofar the changes of state in this process are close to isothermal.

So the exponent e will be 1 < e



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Fig.1 The Effect of V max / V min and the Regenerator efficiency hreg on the Thermal Efficiency htherm

The upper black line with 3 blue rectangles stands for h reg = 100 % for all Vmax / Vmin and for all k's

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Fig.2 The Effect of V max / V min and the Adiabatic exponent k = C p / C v on the Thermal Efficiency htherm


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Fig. 3 T-S Diagram for a Stirling Engine with Air as the Working Fluid. The Frame Represents the Ideal Process; TE=500,TC=300 K

Fig. 4 T-S Diagram for a Stirling Engine with Argon as the Working Fluid. The Frame Represents the Ideal Process; TE=500,TC=300 K


-

More significant than the Fig.(1)(2) and Fig.(5)(6) is the following table presenting the results of the 8 simulations. This table is made by the programm

STMOT2.

____________________________________________________________________________________________________________________________________ 1 | 2 | 3 | 4 | 5 | 6 | 7 | 8 | 9 | 10 | 11 | 12 | 13 | 14 | 15 | 16 | 17 | 18 | 19 | 20 ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______ RUN| DKST|KAPA| TEMP.|STROKE| DEAD |REGEN.| DEAD | P0 |VMAX |PMAX | WORK | WORK |- WORK|POWER|DQZU1|DIFFERENCE IN GASMAS|TIME . No.| DH |EXP | TH | VOL. | VOL. | VOL. | VOL. | | / | / | A1 | A2 |LOST |USABL| MAX | EXP. | COMP.| REG. | sec | DK |COMP| TK | EXP. | EXP. | | COMP.| |VMIN |PMIN | |Watt*s | | | | | | | STROKE| |TE_MAX| COMP.| |cm**3 | |P1MEAN| | | | | | | | | | |REVOL. RE-| | |TC_MIN| | | | | | | | | ETA_N | | | | | | |TIME VOL| | | | | | ETA_R| | | | | | AUSN_I| | | | | | | msec | | | | | | | | | | | | AREF_I| | | | | | | |cm | - |Kelvin|cm**3 |cm**3 | % |cm**3 | Bar | - | - |Watt*s | % |Watt*s| Watt| Watt|Gramm |Gramm |Gramm |RPM ---|-----|----|------|------|------|------|------|------|-----|-----|-------|-------|------|-----|-----|------|------|------|------ 1| 2.00|1.00| 500.0| 251.3| 10.1| 100.0| 10.1|16.000|2.710|2.832| 156.8| 154.81|11.146| 1637| 9124| 3.504| 4.173| 2.177| 0.375 | 8.00|1.00| 300.0| 235.6| | | | | | | | | | | | | | | | 8.00| | | | | | | | | | |30.46 %| | | | | | | 374.7 | 5.00| | 500.0| | | 80.0| | 22.58| | | |39.62 %| | | |GM01= 6.762916 Gr | 1| | | 300.0| | | | | | | | |22.40 %| | | |TOTAL GASMASS | 160.2 | | | | | | | | | | | | | | | | | | | ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______ 2| 2.00|1.00| 500.0| 251.3| 502.7| 100.0| 502.7|16.000|1.290|1.297| 35.0| 34.84|11.144| 343| 5618| 3.061| 3.161| 0.465| 0.375 | 8.00|1.00| 300.0| 235.6| | | | | | | | | | | | | | | | 8.00| | | | | | | | | | |17.99 %| | | | | | | 374.9 | 5.00| | 500.0| | | 80.0| | 20.13| | | | 8.78 %| | | |GM01= 25.088609 Gr | 1| | | 300.0| | | | | | | | | 1.27 %| | | |TOTAL GASMASS | 160.0 | | | | | | | | | | | | | | | | | | | ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______ 3| 2.00|1.00| 500.0| 251.3| 10.1| 100.0| 10.1|16.000|2.710|2.832| 156.8| 154.81|11.146| 1637| 8598| 0.484| 0.576| 0.301| 0.375 | 8.00|1.00| 300.0| 235.6| | | | | | | | | | | | | | |



| 8.00| | | | | | | | | | |33.39 %| | | | | | | 374.7 | 5.00| | 500.0| | | 80.0| | 22.58| | | |39.62 %| | | |GM01= 0.933516 Gr | 1| | | 300.0| | | | | | | | |22.40 %| | | |TOTAL GASMASS | 160.2 | | | | | | | | | | | | | | | | | | | ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______ 4| 2.00|1.00| 500.0| 251.3| 502.7| 100.0| 502.7|16.000|1.290|1.297| 35.0| 34.84|11.144| 343| 5308| 0.422| 0.436| 0.064| 0.375 | 8.00|1.00| 300.0| 235.6| | | | | | | | | | | | | | | | 8.00| | | | | | | | | | |22.47 %| | | | | | | 374.9 | 5.00| | 500.0| | | 80.0| | 20.13| | | | 8.78 %| | | |GM01= 3.463093 Gr | 1| | | 300.0| | | | | | | | | 1.27 %| | | |TOTAL GASMASS | 160.0 | | | | | | | | | | | | | | | | | | ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______ 5| 2.00|1.00| 500.0| 251.3| 10.1| 100.0| 10.1| 3.300|2.710|2.841| 32.6| 32.14|11.144| 316| 2496| 0.725| 0.863| 0.448| 0.375 | 8.00|1.00| 300.0| 235.6| | | | | | | | | | | | | | | | 8.00| | | | | | | | | | |19.59 %| | | | | | | 374.9 | 5.00| | 500.0| | | 40.0| | 4.67| | | |37.11 %| | | |GM01= 1.394851 Gr | 1| | | 300.0| | | | | | | | |20.98 %| | | |TOTAL GASMASS | 160.0 | | | | | | | | | | | | | | | | | | | ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______ 6| 2.00|1.00| 500.0| 251.3| 502.7| 100.0| 502.7|15.000|1.290|1.297| 32.8| 32.66|11.144| 319| 5266| 2.869| 2.963| 0.436| 0.375 | 8.00|1.00| 300.0| 235.6| | | | | | | | | | | | | | | | 8.00| | | | | | | | | | |17.89 %| | | | | | | 374.9 | 5.00| | 500.0| | | 80.0| | 18.87| | | | 8.73 %| | | |GM01= 23.520571 Gr | 1| | | 300.0| | | | | | | | | 1.26 %| | | |TOTAL GASMASS | 160.0 | | | | | | | | | | | | | | | | | | | ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______ 7| 2.00|1.00| 500.0| 251.3| 10.1| 100.0| 10.1| 3.300|2.710|2.841| 32.6| 32.14|11.144| 316| 2135| 0.100| 0.119| 0.062| 0.375 | 8.00|1.00| 300.0| 235.6| | | | | | | | | | | | | | | | 8.00| | | | | | | | | | |23.92 %| | | | | | | 374.9 | 5.00| | 500.0| | | 40.0| | 4.67| | | |37.11 %| | | |GM01= 0.192538 Gr | 1| | | 300.0| | | | | | | | |20.98 %| | | |TOTAL GASMASS | 160.0 | | | | | | | | | | | | | | | | | | | ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______ 8| 2.00|1.00| 500.0| 251.3| 502.7| 100.0| 502.7|15.000|1.290|1.297| 32.8| 32.66|11.144| 319| 4977| 0.396| 0.409| 0.060| 0.375 | 8.00|1.00| 300.0| 235.6| | | | | | | | | | | | | | | | 8.00| | | | | | | | | | |22.34 %| | | | | | | 374.9 | 5.00| | 500.0| | | 80.0| | 18.87| | | | 8.73 %| | | |GM01= 3.246650 Gr | 1| | | 300.0| | | | | | | | | 1.26 %| | | |TOTAL GASMASS | 160.0 | | | | | | | | | | | | | | | | | | | ___|_____|____|______|______|______|______|______|______|_____|_____|_______|_______|______|_____|_____|______|______|______|______


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Fig.(1)(2) Influence of volumeratio V max / V min to supplied heat "DQZU1" and the usable Power "POWERN" of the engine


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Fig.(5)(6) The Influence of volumeratio V max / V min, the Regenerator efficiency hreg and the idle pressure P0 to the usable Power "POWERN" of the engine


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Fig.(5)(6)TS T-S diagrams for air: Run (5) with high volume ratio Vmax/Vmin =2.71 and run (6) with low volume ratio Vmax/Vmin 1.29; the "frames" are

equal to the ideal Stirling process. Simulation results see in table at RUN NO. 5 and 6


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Fig.(7)(8)TS T-S diagrams for Helium: Run (7) with high volume ratio Vmax/Vmin = 2.71 and run (8) with low volume ratio Vmax/Vmin = 1.29; the "frames"are equal to the ideal Stirling process. Simulation results see in table at RUN NO. 7 and 8


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About the Efficiency of the Regenerator in the Stirling Engine

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