US3812682A

US3812682A - Thermal refrigeration process and apparatus

Info

Publication number: US3812682A
Application number: US00135490A
Authority: US
Inventors: K Johnson
Original assignee: Individual
Current assignee: Individual
Priority date: 1969-08-15
Filing date: 1971-04-19
Publication date: 1974-05-28
Anticipated expiration: 1991-05-28

Abstract

Process and apparatus for producing refrigeration, or refrigeration and work directly from thermal energy. The thermal energy input can also be supplemented by work input to enhance the refrigeration effect.

Description

United States Patent 1191 Johnson 1 May 28, 1974 [54] THERMAL REFRIGERATION PROCESS 2,127,286 8/1938 Bush 62/6 AND APPARATUS 2,567,454 9/1951 Taconism. 62/6 2,657,552 11/1953 Jonkersm. 62/6 6] n en Kenneth J nso 124 Castle 2,657,553 11/1953 JOnk81'S.... 62/6 Crest Rd., Walnut Creek, Calif. 3,115,014 12/1963 Hogan 62/6 94529 3,145,527 8/1964 Morgenroth 62 6 3,296,808 1/1967 Malik 62/6 1 Flledi i 1971 3,379,026 4/1968 Cowans 62/6 [21] Appl. No.: 135,490

Primary Examiner-Wi11iam J. Wye a Application Attorney, Agent, or Firm-Flehr, Hohbach, Test, A1- [63] Contmuation-m-part of Ser. No. 850,439, Aug. 15, brittongz Herbert 1969, abandoned. 1

[52] US. Cl. 62/6, 62/467 57 ABSTRACT [51] Int. Cl. F25b 9/00 [58] Field 61 Search 62/6, 467 Pmess and apparatus Pmducmg efngeratm, 1 refrigeration and work d1rect1y from thermal energy. [56] References Cited The thermal energy input can also be supplemented v UNITED STATES PATENTS by work mput to enhance the refr1gerat1on effect. 1,275,507 Vui11eumier 62/6 38 Claims, 28 Drawing Figures memsnmz 1914 $812,682

SHEEI. 2 0f 8 I INVENTOR.

KENNETH P. JOH NSON PATENTEDIIAY 28 1914 saw 3 or 8 INVENTOR.

KENNETH P. JOHNSON mimcnm 2a 1914 3 Q 8 12,6 82

saw a or 8 INVENTOR.

KENNET H P. JOHN SON PATENTEBmesmn 3.812.682

SHEEI 5 0f 8 FIG 7 FIG 7A A B c o A C D 1 EXP 1 COMP B Vs: vH

I V52 VRF VT VD P v I I I Ni/ o I I I 1 0 I80 360 FIG 8A Q VH m IN 5 (HOT) H D C VH 94 'g- P B A FIG 88 P A B RF fT XP FIG 8C QIN VRF (RF) D C VRF A,B 7 8 Nil M o,c P

INVENTOR.

KENNETH P. JOHNSON Z Z4,/%[Z;?f

PATENTED n 23 m4 SHEEI 6 0F 8 VRF FIG1O INVENTOR.

KENNETH P. JOHNSON %4,%M7J/af s w PATENTEBIAY 28 m4 SfliEI'IUF 8 IG H B C D FIG 11/-\ EXP k-i-flcow Vc A B C D I I l 4 VC [0' I I I O I I I 60 I I l I I e A B FIG 12A 0 c VH A FIG 12B c D E Vc 27 FIG 12c COMP B "Ki FIG 120 w VRF A,B v

w 12E INVENTOR.

KENNETH P. JOHNSON 1- v1- ZQflMZZLzf THERMAL REFRIGERATION PROCESS AND. APPARATUS CROSS-REFERENCE TO-RELATED APPLICATION This is a continuation-in-part of copending application Ser. No. 850,439, filed Aug. 15, 1969, now abandoned.

BACKGROUND OF THE INVENTION This invention pertains generally to thermodynamic processes and machines and more particularly to a process and apparatus capable of producing either refrigeration or refrigeration andwork output from thermal energy. The thermal energy may also be supplemented by work energy to produce refrigeration.

Refrigeration systems heretofore provided have included absorption type refrigeration systems,electric motor driven compressor-systems, and certain thermal refrigeration systems.

Absorption type refrigeration systems generally include a refrigeration loop. and a heat engine loop in a closed thermodynamic cycle. Limited'by the natural limits of the absorption process, the heat engine loop operates over only a narrow temperature range. Heat rejection requirements are high in absorption type systems, with the heat rejected from the engine loop typically being three times greater than-that which is re jected from the refrigeration loop. This poor thermodynamic performance leads to'high'equipment first cost as well as high operating costs.

Conventionalelectric motor driven compressor systerns have inherently high-performance, resulting in a minimum of heat rejection components and low first cost. However, because of the high costof electricity, as compared-with the cost of natural gas, the operating costs of electrically motor driven compressor systems are relatively high. W-hilethe refrigeration operating temperature range can be extended by cascading compressor stages. the coefficient of performance of the system is decreasedsignificantly by the compressor losses per stage.

In thermal refrigeration systems heretofore provided, such as disclosed in US. Pat. No. 2,657,553, coefficient of performanceis low because it-is necessary to produce work output in order to also produce refrigeration.

SUMMARY AND OBJECTS OF THE INVENTION process may be applied over a broad temperature range. i.e., air conditioning through cryogenic applications, with high'performance and low cost over the entire range.

It is in generaltan object of the invent-ionto provide a new and improved thermalrefrigeration process and apparatus- Another object of the invention is to' provide a process and apparatus of the above character in which either refrigeration alone or refrigeration and work can be produced directly fromthermal energy.

Another object of the invention is to provide a process and apparatus of the above character in which the thermal energy input can be supplemented by work energy input.

Another object of the invention is to provide a pro cess and apparatus of the above character which can be utilized over a broad temperature range.

Another object of the invention is to provide a process and apparatus of the above character which'can be economically constructed and operatedv with high power density.

Additional objects and features of the invention will appear from the following description in which the preferred embodiments are set forth in detail in conjunction with the accompanying drawing.

BRIEF DESCRIPTION OF THE DRAWING FIG. 1 is a diagram showing volumetric relationships during one cycle of a thermodynamic process embodying the present invention. I

FIG. 1A is a diagram illustrating the relationship between working fluid pressure and crankshaft rotation for the cycle illustrated in FIG. I. I

FIG. 2 is a schematic diagram illustrating the interconnection of the volumes shown in FIG. 1.

FIGS. 2A through 2D are diagrams showing the relationship between pressure and volume during the cycle of operation illustrated in FIG. 1.

FIG. 3 is a sectional view, partly in diagrammatic form, of one embodiment of apparatus incorporating the present invention. i

FIG. 4 is a diagrammatic,. exploded view with portions indicated as A through E corresponding to section lines 4A through 4B of FIG. 3, respectively.

I FIG. 5 shows diagrammatically another embodiment FIG. 6 shows diagrammatically another embodiment I of apparatus incorporating the present invention.

FIG. 7 is a diagram showing the volumetric relationships during an operating cycle of the apparatus shown in FIG. 6.

FIG. 7A is a diagram showing the relationship between working fluid pressure and crankshaft rotation for the apparatus of FIG. 6.

FIG. 8 is a schematic diagram illustrating the interconnection of the volumes shown in FIG. 7.

FIGS. 8A through 8D show the relationships between v pressure and volume in the apparatus of FIG. 6.

FIG. 9 diagrammatically shows another embodiment of apparatus incorporating the present invention.

FIG. 10 diagrammatically illustrates another embodiment of apparatus incorporating the present invention.

tween working fluid pressure and crankshaft rotation inthe apparatus of FIGS. 9 and 10.

FIGS. 12A through 12E illustrate the relationships between pressure and volume in the apparatus of FIGS.- 9 and 10.

FIG, 13 shows diagrammatically. another embodiment of apparatus incorporating the present. invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS panding the working fluid; and adding low temperature thermal energy to and simultaneously subtracting high temperature thermal energy from the working fluid while again maintaining the volume and pressure of the fluid substantially constant. It has been found that these steps can be advantageously performed ina closed system comprising a hot expander chamber of variable volume V a refrigerator expander chamber of variable volumegV f, a compressor chamber 'of variable volume V a first heat exchanger assembly 11, connected intermediate the hot expander chamber and the compressor chamber, and a secondiheat exchanger assembly 12 connected intermediate therefrigerator expander chamber and the compressor chamber. The interconnection of the expander and compressor ch'am bers and the heat exchangers is illustrated in FIG. 2. In the pre ferredembodiments, an ideal gas is used as the working fluid. 3

The

heat exchanger assemblies

11 and 12 are made up of conventional units. The exchanger assembly 11 includes a heater H which is connected to the hot expander volume V a-cooler C connected to the compressor volume Va, and a regenerator R connected intermediate the heater and cooler. The exchanger assembly 12 includes a refrigerator heat exchanger R connected to the refrigerator expander volume V a cooler C connected to the compressor volume V and a regenerator R intermediate the refrigerator and cooler/The function of the heater H and refrigerator heat exchanger R is to add thermal energy to the working fluid. The coolers C function as a heat sink for removing thermal energy from the working fluid. The regeneratorspro'vide transitory storage and release of thermal energy to the wo'rking fluid; thus establishing thermal gradients between the heater and cooler and between the refrigerator heat exchanger and cooler.

FIG. l'illustrates the relationships among the vol- 'umes in the system duringone complete cycle of operation. corresponding to 360 of crankshaft rotation. The crankshaft rotation 8 is plotted in degrees on the abscissa. and the volumetric variations are plotted on the ordinate. where Y i V Refrigerator expander volume V Hot expander volume V; Total expander volume (V V V Compressor volume v V Dead volume (volume of the heat exchangers and flow passageways), V1- =T0ta| System, volume (VHF V" V(' VD) As illustrated. the hot expander volume V and the refrigerator expander volume V vary substantially harmonically and substantiallyin phase with each other. Thus, in 360 of crankshaft rotation, they each vary from a minimum value to a maximum value and back to the minimum value. The-difference between the maximum and minimum volumes of a chamber is hereinafter referred to as the workingvolume of that chamber. The volume V of the compressor chamber also varies substantially harmonicallyfrom a minimum value to a maximum value and back to the minimum value in 360 of crankshaft rotation. The variation of the compressor volume V is not, however, inphase with that of the expander chambers. For reasons that will appear hereinafter, it has been found that the best results are obtained when the changes in the expander volumes lead the changes in the compressor volume by an angle on the order of 1 10 to From FIG. 1 it can also be seen that when the total expander working volume V is made approximately equal to the working volume Vg of the compression chamber, the total volume V is substantially constant during the phases of the cycle between A and B and between C and D. Between B and C the total volume undergoes an expansion phase, and between D and A it undergoes a compression phase. I

During the first substantially constant volume phase, that is from A to B, the expander volumes are increasing and the compressor volume is decreasing. Hence, during this phase, working fluid is transferred from the compressor. volume to the expander'volumes. The fluid passing from the compressor volume to the'hot expander volume flows through the first heat exchanger as sembly 1'] wherein high temperature thermal energy is added to the fluid by the regenerator R and heater H. Also, during this constant volume phase, thermal energy is extracted from the working fluid bythe cooler C and second regenerator R as it passes through the second heat exchanger assembly 12.,Additional heatis added at low temperature by the refrigerator heat exchanger R The amount of thermal energy removed from the working fluid in the second heat exchanger assembly is substantially equal to that added to the working fluid in the first heat exchanger assembly, with the result that the pressure of the working fluid remains substantially constant during'the first constant volume phase.

Duringthe expansion phase, that is from. B to C, the working fluid is expanded substantially is entropically in the expander chambers and in a mixed isothermal and isent'ropic process in the compressorchamber.

During the second substantially constant volume phase, that is from C to D, working fluid is shifted from the expander chambers to the compressor chamber. As

thermal energy is extracted from the fluid by th cooler 4 in'this first exchanger. The thermal energy extracted from the fluid in the first heat exchanger assembly 11 is substantially equal to the thermal energy added in the second exchanger assembly 12, and the pressure of the working fluid remains substantially constant during the second constant volume phase.

During the compression phase, the working fluid is compressed isothermally and isentropically in the expander and compressor chambers.

FlG. 1A shows the pressure changes in the system during the operating cycle. For clarity, the pressure changes shown reflect ideal constant volume shifts. As is more .fully discussed hereinafter, the coefficient of performance of the process is significantly enhanced by maintaining the pressure of the working fluid substantially constant during the constant volume phases since the working fluid AT in each working chamber is thereby minimized.

FIGS. 2A, 2B, and 2C are P-V diagrams which describe the thermodynamic processes occurring in the volumes V V and V respectively. As canbe seen in these figures,,the.working fluidin each of the two expander volumes passesthrough anexpansion cycle, and the working fluidhin the compressor volume passes through a compression cycle. Energy is extracted from the working fluid in the hot expansion chamber and resupplied thereto at high temperature as it passes through the heater in thefirst heat exchanger assembly 11. Energy is extracted from .the'working fluid in the refrigerator .expander volume and is re'supplied thereto at a low temperature as it passes through the refrigerator heat exchanger in theheat exchanger assembly 12. Energy is added to the .working fluid in the compressor chamber and removed therefrom as it passes through the coolers. 1

As will be apparentto those familiar with the art, the conditions required for a closed cycle heat engine and a closed cycle refrigerator have been combined into a single process. Athermal machine operating according to this process may produce refrigeration alone, refrigeration and work, or itmaybe designed to produce refrigeration from thermal energy with a supplemental input of work.

As can be seenin FIGS. 2C and 2D, the expansion cycle of the refrigerator chamber is one quarter cycle out of phase with the net power cycle, and with no pressure change during the constant volume strokes, the process can produce refrigeration without producing net work. Thermal energy input may be supplemented by work energy input to thesystem. This is to be contrasted with thermal refrigeration systems heretofore provided in which refrigeration is produced in a refrigerator'expander volume arranged in phase with the net power cycle ofengine components. With the net power cycle and refrigeration volume in phase, the engine cycle must be an expansion cycle and thus produce net work in order to drive the refrigerator working fluid in an expansion cycle to produce refrigeration. Further, with the net power cycle in phase with the refrigerator volume. supplemental work input will generate a net engine compression cycle and thus a compression cycle in the refrigerator. volume which-is the opposite of what is required to produce refrigeration.

The refrigeration produced is equal to the expansion cycle work of the working fluid in the refrigerator expander chamber, and the high temperature heat input to the system is equal to the expansion cycle work of the working fluid in the hot expander chamber. Therefore, the coefficient of performance of a machine operating according to the process can be expressed by the relationship.

RCfL/Q Where:

CF. Coefficient of performance,

Refr. Work done by gas in the refrigerator cham ber,

Qm Work done by gas in the hot expander chamber.

Since the volumes of the expander chambers vary in phase, the working fluid pressure is equal in both chambers for the same percentage of volumetric displacement in each chamber. Therefore, the average AP in the hot expander chamber is equal to the average AP in the refrigerator expander chamber. Since the work done in each chamber is equal to the volume of the chamber multiplied by the average AP in the chamber, it follows that Cl. Var/V Based on Carnot cycle limits, where no work is produced, thecoefficient of performance can be expressed ar/ n) u c)/( c arn Where:

T Average absolute temperature of gas in refrigerator expander volume, T Average absolute temperature of gas in hot expander volume, T Average absolute temperature of gas in compressor volume. Therefore, in the ideal machine where there is no friction or net work produced, ar/ 11 ar n) u c)/( c arnln order to produce a constant pressure during the constant volume strokes, as defined in this process, the volumetric ratio (VHF/V") is dependent on the specific working fluid temperature entering or leaving each chamber. Refrigeration and work are produced when the total expansion net work is greaterthan the compression work, and the expansion work can be increased relative to the compression work simply by'decreasing the ratio V /V while holding temperature conditions fixed. Input work is required in addition to thermal energy to produce refrigeration when theexpansion workis less than the compression work. With temperature conditions fixed, expansion work can be decreased relative to compression work by increasing the ratio VRF/VH. Thus, by adjusting the relative volumes of the expander chambers, the process can be adapted for producing refrigeration alone, refrigeration and work, or for producing refrigeration from thermal energy supplemented by work input. In practical systems, volumetric ratios must be selected which will result in sufficient work to overcome internal friction and leakage losses in the system.

FIG. 2D is a P V diagram of the process occurring in the total working volume V of an ideal system where expansion work is equal to compression work and no net work is being produced. If the ratio V /V is decreased, while holding temperature conditions fixed, the P-V process in FIG. 2D will become an expansion cycle producing work. If the ratio is increased, the process will become a compression cycle, and work input will be required as well as thermal energy to produce refrigeration.

The constant pressure process occurring during the volume changes in each working chamber results in maximum chamber power density combined with a minimum working fluid AT. This is particularly significant when consideration is given to the temperature relationships which define overall coefficient performance, i.e., C.P. (Tnr/T )[(T T T T O]. Be-

cause the temperature in theforegoing relationship are average chamber working fluid temperatures, the coefficient of performance is significantly enhanced by minmimizing the working fluid AT in each chamber.

This process is applicable at refrigeration temperatures ranging from standard air conditioning tempera tures down into thecryogenic range. For the standard air conditioning temperature range of T 45F. and T 120F., a practical system (utilizing the machine geometry shown in FIG. 6) operating on this process could have a volumetric ratio Vmv/VH 1.5 and average chamber working fluid temperatures of T 475R, T 640R and T 1,595R. An ideal or process C.P. of 1.72 is indicated and the ideal machine (no friction or thermal losses) will also produce net work. When mechanical and thermal losses are considered it is estimated that the CF. will be about 1.]. This coinpares with domestic thermal absorption type air conditioning systems which exhibit a GP. ranging from 0.3 to 0.4.

This process has been .compared, from the standpoint of power density, with the Stirling cycle engine and refrigerator process and machines. The hot expander power density is about equal to the power density in the hot expander of a Stirling engine. The refrigerator expander volume power density in this process however is greater than the Stirling refrigerator expander process by about 85 percent at +40F. and a factor of ten at cryogenic temperatures (-320 F.)'The increase in refrigerator chamber power density is due to the optimum shape of the P-V diagrams and a more pronounced isentropic expansion, i.e., a constant pressure admission, followed by an isentropic expansion, followed by'a constant pressure and then mixed isothermal and isentropic exhaust stroke. This process will thus result in producing more compact'machines in this class than have been heretofore possible. The economic advantage afforded by using thermal energy as a source of power will apply over the entire temperature range. i

In a practical system embodying the process, the

thermal energy for driving the system is supplied to the working fluid through the heater in the heat exchanger assembly 11. The actual heatremoval is performed by the refrigerator heat exchanger R, in the heat exchanger assembly 12. Although this refrigerator heat exchanger has heretofore beendescribed only as adding low temperature thermal energy to the fluid, it will be appreciated that the extraction of thermal energy from the environment of the refrigerator reduces the temperature of that environment. Heat is removed from the system by the coolers'C, both of which can conveniently be connected to a single heat sink.

The thermal refrigeration process described hereinbefore can be practiced in a variety of machine configurations. The necessary volumetric relationships can be provided in both oscillating vane and reciprocating piston machines, and several embodiments of apparatus incorporatingthe invention are described hereinafter.

FIGS. 3 and 4 illustrate one embodiment'of an oscillating vane machine incorporating the present invention. The oscillating vane type of machine is described in detail in by co-pending application Ser. No. 691 ,054, filed Dec. 15, 1967, now US. Pat. No. 3,460,344. Briefly, an oscillating vane machine includes means forming one ormore cylinders each containing a pair of arcuate chambers, an oscillating shaft coaxially disposed within the cylinders, and a pair of diametrically disposed vanes carried by the shaft within the chambers. Oscillation of the shaft causes the vanes to sweep back and forth, forming in each arcuate chamber a pair of altemately enlarging and diminishing volumes adapted to receive and discharge a working fluid. Ports are provided in the chambers on opposite sides of each vane in communication with the enlarging and diminishing volumes. The oscillating shaft is operably connected to a crankshaft which rotates through 360.

The embodiment illustrated in FIGS. 3 and 4 includes a hot expander cylinder 16, a refrigerator expander cylinder 17, and a compressor cylinder 18. The hot expander cylinder contains a pair of

arcuate chambers

19 and 21, each extending through an angle on the order of 1 10. An oscillating vane assembly 22, including diametrically disposed

vane members

22a and 22b, is coaxially disposed in the cylinder 16. The

vane members

22a and 22b divide the

chambers

19 and 21 respectively, into pairs of alternately enlarging and diminishing

volumes V Ports

23 and 24 are provided at each end of the

chambers

19 and 21, each of said ports being influid communication'with one of the volumes V The refrigerator expander chamber 17 likewise contains a pair of

arcuate chambers

26 and 27, each extending through an angle on the order of 1 10. An 05- cillating vane assembly 28, including

vane members

28a and 28b, is disposed coaxially in the cylinder. The vane members 284 and 28b divide the

chambers

26 and 27, respectively, into pairs of alternately enlarging and diminishing

volumes V Ports

29 and 30 are provided on opposite sides of the vane members in communication with the volumes V The compressor cylinder 18 also contains a. pair of

arcuate chambers

31 and 32, each extending through an angle on the order of 1 10. An oscillating vane assembly 33, including vane members 33a and33b, is co axially disposed .in the cylinder. These vane members divide the

chambers

31 and 32 into pairs of alternately enlarging and diminishing

volumes V Ports

34 and 35 are provided on opposite sides of the vane members in fluid communication with each of the volumes V The expander vane assemblies 22- and 28 are mounted on an upper oscillating shaft 36, and the compressor vane assembly 33 is mounted on a lower oscillating shaft 37. The upper oscillating shaft is operably connected to a crankshaft 38 by means of

cranks

41 and 42 and a connecting rod 43. The cran k 41 is fastened to the oscillating shaft 36, the crank 42 is secured to the crankshaft 38, and the connecting rod is pivotally mounted on crank

pins

41a and 42a carried bythe cranks. The lower oscillating shaft 37 is similarly connected to the crankshaft 38 by means of'cranks 47 and 48 and a connecting rod 49. The oscillating shafts and crankshaft are mounted in conventional bearings and provided with suitable seals, such as those described in application Ser. No. 691,054, now US. Pat. No.

As illustratedin FIG. 4, the

expander vane assemblies

22 and 28 are constrained to move substantially in phase with each other. Hence, the variations of the hot expander volumes V and'refrigerator expander volumes V are substantially in phase with each other. The phase relationship between the volumetric variations of the expander chambers and the compressor chamber is determined by the positions of the

cranks

41, 42, 47 and 48. In the preferred embodiment of the oscillating vane apparatus, these cranks are arranged in such manner that the expander volumes lead the compressor volumes by an angle on the order of 110 to 140, although the machine will operate with phase angles ranging from about 80 to 160.

First flow passage means 51 is provided for connecting one of the hot expander volumes V in free and open communication with one of the compressor volumes Vg. This means includes a first heat exchanger assembly 52 comprising a heater H, a regenerator R, and a cooler C. The heater is connected to the port 23 in communication with the volume V the cooler isconnected to the port 34 in communication with the volume V and the regenerator is connected intermediate the heater and cooler.

Second flow passage means 53 connects a refrigerator expander volume V with the compressor volume V This means includes a second heat exchanger assembly 54 comprising a refrigerator heat exchanger R and regenerator R, and a cooler C. The refrigerator heat exchanger R is connected to the port 29 in communication with the volume V the cooler C is connected to the port 34 in communication with the volume V and the regenerator is connected intermediate the refrigerator and cooler.

The oscillating vane machine is double acting, and additional flow'passageways 56 and 57 are shown connected to the

ports

24, 30 and 35. These passageways provide fluid communication between the expander and compressor volumes which are formed in the same chambers as the volumes which are interconnected through the

passageways

51 and 53. The

passageways

56 and 57 include heat exchanger assemblies which are similar in construction and connection to the

heat exchanger assemblies

52 and 54.

Both sides of this double acting machine perform the thermal refrigeration process described hereinbefore in connection with FIGS. 1 through 2D. Thus, FIGS. 1 through 2D illustrate the operation of the individual sides of the double acting oscillating machine. Like reference characters'have been used for the expander and compressor volumes, and the

heat exchanger assemblies

52 and 54 correspond to the

heat exchanger assemblies

11 and 12, respectively, in FIG. 2. Further, it should be noted that since the working volumes of the double acting machine are formed by single vangn bers, the two sides of the machine operate TtTldegrees out of phase with each'other.

The diametrically opposed working volumes in each of the expander and compressor cylinders operate in phase with each other and are interconnectedby passageways. as indicated by dashed lines59. This interconnection doubles the effective working volume of each of the expander and compressor chambers and further enhances the balance of the machine.

In FIGS. Sand 4, the hot expander chamber and refrigerator expander chamber have been illustrated adjacent to each other in order to clarify the operation of the mchine. However, in an' actual machine, these chambers should preferably be isolated from each If desired, work input can be added to the oscillating vane machine to supplement the thermal energy input. This is conveniently done by connecting a drivin motor to the crankshaft 38.

FIG. 5 illustrates one embodiment of a reciprocating piston machine incorporating the present invention. This machine includes means forming a hot expander cylinder 61, a refrigerator expander cylinder 62, and a compressor cylinder 63.

Expander pistons

64 and 65 are slidably disposed in the

expander cylinders

61 and 62, respectively, for varying the volume V and V of these cylinders. A compressor piston 66 is slidably disposed in the cylinder 63 for varying the volume V of the compressor cylinder. The expander and compressor pistons are operably connected together by linking means comprising a crankshaft 68 and connecting rods 69. e phase relationships between the pistons are thus determined by the angles between the cranks on the crankshaft. In the preferred embodiment, as illustrated, the cranks are arranged so that the expander pistons are substantially in phase with each other and lead the compressor piston by an angle on the order of 1 10 to The machine will still operate, however, with phase angles ranging from about 80 to Means forming a first flow passage 71 is provided for connecting the hot expander volume V in free and open communication with the compressor volume V This means includes a first heat exchanger assembly 72 comprising'a heater H, a regenerator'R, and a cooler C. The heater is connected adjacentto the hot expander chamber, the cooler is connected to the compressor chamber, and the regenerator is intermediate the heater and cooler.

Second flow passage means 73 is provided for connecting the refrigerator expander volume V in free and open communication with the compressor volume V This means includes a second heat exchanger assembly 74 comprising a refrigerator heat exchanger R a regenerator R, and a cooler C. The refrigerator heat exchanger is connected adjacent to the refrigerator expander volume, the cooler is connected to the compressor volume, and the regenerator is intermediate the refrigerator heat exchanger and cooler.

High temperature thermal energy Q, is supplied to the working fluid through the heater H in the first heat exchanger assembly 72, and low temperature thermal energy is added through the refrigerator heat exchanger R This machine operates according to the process described hereinbefore in connection with FIGS. 1 through 2D. Accordingly, these figures illustrate the operation of the reciprocating piston machine, with the heat exchanger assemblies 72 and. 74 corresponding to the

heat exchanger assemblies

11 and 12, respectively, in FIG. 2.

If desired, the thermal energy input to the machine illustrated in FIG. 5 can be supplemented by work input by connecting a driving motor 76 to the crankshaft 68.

FIG. 6 illustrates oneembodiment of a reciprocating piston machine with balancing chambers incorporating the present invention. This machine includes

means forming cylinders

77, 78 and 79. Pistons are slidably disposed in each of these cylinders. Thus, a displacer piston 81 forms a hot expander chamber 82 and a balancing chamber 83 of variable volumes V and V,,,, respectively, in the cylinder 77. Similarly, a displacer piston 84 forms a

refrigerator expanderchamber

86 and 1 1 a balancing chamber 87 having variable volumes V and V respectively, in the cylinder 78.

Thedisplacer pistons

77 and 78 are provided with elongated head portions because of the thermal differences existing on the opposing sides of these pistons. A power piston 88 forms a power chamber 89 of variable volume Vp in the cylinder 79.

The displacer and power pistons are operably interconnected by means of a crankshaft 90, connecting rods 91, and piston rods 92. The piston rods associated with the displacer pistons are provided with conventional seals where they pass through the walls of the balancing chambers. The phase relationship among the pistons is controlled by the phase angles between the cranks on the crankshaft. In the preferred embodiment, the cranks are arranged in such manner that the displacer pistons are substantially in phase with each other and lead the power piston 88 by-an angle on the order of about 60 to 1 Thus, the hot expandervolume V and refrigerator expander volume V are substantially inphase with each other andlead the power volume V, by an angle on the order of 90. The balancing chamber volumes V, and V are 180 out" of phase with the ex-.

pander volumes and act ascompressor volumes.

First flow passage means 93 is provided for connecting the volumes 'V V and Vp in free and open communication with each other. This means includes a heat exchanger assembly 94 comprising a heater H, a regenerator R, and a cooler C. The heater is connected adjacent to the hot expander volume V and the cooler is connected to the balancing volume V and to the power volume Vp. The regenerator is connected'intermediate the heater and cooler..

Second flow passage means 96 is provided to connect the volumes V V,,,, and. V in free and open communication with each other. This means includes a heat exchanger assembly 97, comprising a refrigerator heat exchanger R a regenerator R, and a cooler C. The refrig'erator heat exchanger Rfis connected to the refrig erator expander volume V, and the cooler is connected to the balancing volume V and to the power volume V High temperature thermal energy is-supplied to the working fluid in this machine througli the heater Hin the heat exchangerassembly94, and low temperature thermal energy is supplied through therefrigerator heat exchanger R V v 7 The relationships among the volumes in the machine during one complete cycle-of operation are illustrated in FlG. 7. The total volume V is equal to the sum of the expander, power, balancing, and dead volumes. Because the sum of the expander and balancing volumes is constant. as is the dead volume, the total volume V varies in phase with the power volume V This volume V, passesthrough substantially constant volume phases between A and 'B and between C and D. Between B and C the total volume undergoes an expansion'phase, and between D and A it undergoes a compression phase.

Since the volumetric variations in the expander chambers are offset by simultaneous variations in the balancing chambers, the constant volume shifts inthe total working volume are not dependent upon the relative volumes of the expander and power chambers. Hence, the ratio of power volume to total expander volume is not critical in this machine. v

Pressure changes in the working fluid during the constant volume shifts are cancelled by the interaction of simultaneous heat addition and removal in the heat exchangers associated with the two displacer piston assemblies. Thus, the pressure of the working fluid remains substantially constant during the constant volume shifts. FIG. 7A describes the pressure changes in the machine through a complete cycle, or 360 of crankshaft rotation. For the sake of clarity, the pressure changes shown reflect perfect constant volume shifts.

FIGS. 8A and 8C are P-V diagrams showing the expansion cycles occurring in the hot expander chamber V and the refrigerator expander chamber V respectively. FIG. 8B shows the compression cycle occurring in the balancing volumes V and V FIG. 81) is a P-V diagram of the process occurring in the power volume V As illustrated, the machine is producing only refrigeration, and FIG. 8D therefore reflects no net work. The machine can be made to produce work as well as refrigeration by increasing the ratio V /V as described hereinbefore, to make the process shown in FIG. 8D an expansion cycle. Likewise, the ratio V /V can be decreased to make the process in FIG. 8D a compression cycle, in which case work input will be required as well as thermal energy to produce'r'e'frigeration..

If desired, the thermalenergy input to the machine illustrated in FIG.'6 can be supplemented with work input by connecting a driving motor 98 to the crankshaft 90. a

FIG. 9 shows a reciprocating piston machine having only one displacer pistonand one balancing chamber. This machine includes

means forming cylinders

101, 102, and 103.

Pistons

104 and 106 form a hot expander chamber 107 of variable volume V}, and a compression chamber 108 of variable volume V respectively, in the

cylinders

101 and 103. A displacer piston 109 is slidably disposed in the cylinder 102 to form a refrigerator expander chamber 111 and a balancing chamber 112 Y of variable volumes V and V respectively. v

The pistons are operably interconnected by means of a crankshaft 113 and connecting rods 114. As in the previous machines, the phase relationship among the pistons is controlled by the phase angles between the cranks on the crankshaft. In the preferred embodiment, the cranks are arranged in such manner that the

pistons

104 and 109 are substantially in phase with each other and lead the piston 106 by an angle on the order of I20 to I40". Thus, the hot expander volume V and the refrigerator expander volume V are substantially in phase with each other and lead the compressor volume V by an angle on the order of I20 to I40". Although the preferred phase angle is on the order of to the machine will still operate with phase angles ranging from about 80 to The balancing chamber volume V, is out of phase with the expander volumes.

First flow passage means 1 16 is provided for connecting the hot expander volume V in free and open communication with the compressor volume V This means includes a heat exchanger assembly 117 comprising a heater, a refrigerator, and a cooler. The heater is connected to the hot expander volume V the cooler I is connected to the compressor volume V and the regenerator is intermediate theheater and the cooler.

Second flow passage means 118 is provided for interconnecting the volumes V V,,, and V in free and open communication with each other. This means in cludes a heat exchanger assembly 119 comprising a refrigerator heat exchanger R regenerator R, and a cooler C. The refrigerator heat exchanger R is connected to the refrigerator expander volume V the cooler is connected to the balancing volume V and to the compressor volume V and the regenerator is intermediate the refrigerator and cooler.

The operation of this machine is illustrated in FIGS. 11 through 12E. FIG. 11 described the volumetric shifts which occur in the machine during one complete cycle, corresponding to 360 of crankshaft rotation. As with the other machines, it can be seen that the total 'volume V of this machine undergoes substantially'constant volume phases between A and B and between C and D. Likewise, between B and C the total volume undergoes an expansion phase, and between D and A it undergoes a compression phase;

The phase of the working fluid'remains substantially constant during the constant volume phases, and the pressure changes during one cycle of operation are shown in FIG. 11A. Again for the sake of clarity, the pressure changes shown reflect perfect constant vol ume shifts.

FIGS. 12A through 12D are P-V diagrams showingthe thermodynamic processes occurring in the volumes V V V and V respectively. The processes occurring in the volumes V V and V are similar to the processes occurring in the corresponding volumes in the phase, machines. Thebalancing volume V undergoes a compression cycle.

FIG. 12E is a'P-V diagram illustrating the thermodynamic process for the entire working volume V As illustrated, the machine is producing only refrigeration, and FIG. 12E therefore reflects no net work. This machine, like the others, can be made to produce net work as well as refrigeration by increasing the ratio V /V to make the process shown in FIG. 12E an expansion cycle. Likewise, the ratio V /V can be decreased, as described hereinbefore, to make the process a compression cycle, in which case w'ork input will be required as well as thermal energy to produce refrigeratron.

FIG. illustrates another embodiment of a reciprocating piston machine witha balancing chamber incorporating the present invention. A well known arrangement of displacer piston and power piston mounted in a common cylinder is combined with a displacer piston mounted in a second cylinder. A typical linkage is shown to illustrate how the two assemblies may be arranged to operate together.

This machine includes means forming two

cylinders

121 and 122. Both a displacer piston 123 and a power piston 124. are slidably mounted in the cylinder 121, forming a hot expander chamber 126 and a compressor chamber 127 of variable volumes V and V respectively. As is described hereinafter, the

pistons

123 and 124 move out of phase with each other, and the compressor chamber 127 'is formed between them. A displacer piston 128 isslidably mounted in the cylinder 122 to form a refrigerator expander chamber 129 and a balancing chamber 131 of variable volumes V and V respectively.

This displacer and power pistons are operably interconnected by means of a crankshaft 132 and connecting

rods

133 and 134. As in the other machines, the phase relationship among the pistons is controlled by the angles between'the cranks on the crankshaft. In the preferred embodiment, the cranks are arranged so that the displacer piston cranks are substantially in phase with each other and lead the power piston crank by an angle on the order of 60 to I00". Thus, the expander chambers V and V are substantially in phase with each other and lead the compressor chamber volume V by an angle on the order of 120 to 150 The machine will still operate, however, if the expander chambers lead the'compressor chamber by an angle ranging from about to 180. The balancing chamber volume V is 180 out of phase with the expander volumes.

First flow passage means 136 is provided forconnecting the hot expander V in free and open communication with the compressor volume V This means includes a heat exchanger assembly 137 comprising a heater H, a regenerator R, and a cooler C. The heater is connected to the hot expander chamber, the cooler is connected to the compressor chamber, and the regenerator is intermediate the heater and the cooler.

Second flow passage means 138 is'provided for connecting the refrigerator expander volume V in free and-open communication with the balancing volume V This means includes a heat exchanger assembly 139 comprising a refrigerator heat exchanger R a regenerator, and a cooler. The refrigerator heat exchanger R is connected to the refrigerator expander volume, the cooler is connected to the balancing volume, and the regenerator is intermediate the refrigerator heat ex changer and cooler.

Additional flow passage meansv 141 is provided for connecting the compressor volume V in free and open communication with the balancing volume V The operation of this machine is substantially the same as that of the machine shown-in FIG. 9 and is, therefore, illustrated in FIGS. 11 through 12E.

FIG. 13 shows another embodiment of a two cylinder reciprocating piston machine incorporating the present invention. This machine includesmeans forming

cylinders

142 and 143. A displacer'piston and a power piston are slidably mounted in each of these cylinders. Thus, displacer piston 144 and a power piston 146 forms a hot expander chamber 147 and a compressor chamber 148 of variable volumes V and V respectively, in the cylinder 142. Likewise, a displacer piston 151 and a power piston 152 form a refrigerator expander chamber 153 and a compressor chamber 154 of variable volumes volumes V and V respectively, in the cylinder 143.

The pistons are operably interconnected by means of a crankshaft 156 and connecting

rods

157 and 158. The phase relationship among the pistons is determined by the angles between the cranks on the crankshaft. In the preferred embodiment, the cranks are arranged in 'such manner that the

displacer pistons

144 and 151 are substantially in phase with each other and lead the

power pistons

146 and 152 by a crank angle on the order of 45 to Thus, the hot expander volume V and refrigerator expander volume V vary substantially in phase with each other and lead the compressor volumes V by an angle on the order of 90 to The machine will still operate, however, with phase angles between the expander and compressor volumes ranging from about 80 to First flow passage means 161 is provided for connecting the hot expander volume V in free and open communication with the volume V of the compressor chamber 148. This means includes heat exchanger assembly 162 comprising a heater H, a regenerator R, and a cooler C. The heater is connected to the hot expander volume V the cooler is connected to the compressor volume V and the regenerator is intermediate the heater and the cooler.

Second flow passage means 163 is provided for connecting the refrigerator expander volume V in free and open communication with the volume V of the compressor chamber 154. This means includes a refrigerator heat exchanger R a regenerator R, and a cooler C. The refrigerator exchanger R is connected to the refrigerator expander volume V the cooler is connected to the compressor volume V and the regenerator is intermediate the refrigerator and cooler.

Additional flow passage means 164 is provided for connecting the volumes of the

compressor chambers

148 and 154 in free and open communication with each other. v

The operation of this machine is similar to the operation of the machines shown in FIGS. 3 through 5, and

reference is made to FIGS. 1 through 2D and the asso ciated disclosure for a description of this operation.

it is apparent from the foregoingthatanew and improved thermal refrigeration process and apparatus has been provided which can produce either refrigeration or refrigeration and work directly from thermal energy. In additiomrefrigeration can be'producedfrom thermal energy supplemented by work input. The process can be applied over a broad temperature range, including air conditioning and-cryogenic applications, with high performance and low cost over the entire range. While only the presentlypreferred embodiments of the process and apparatus have been described hereinbefore, as will be apparent to those familiar with theart, certain changes andmodifications can be made without departing from the scope of the invention as defined by the following claims.

l claims i I l. in a process for producing refrigeration from thermal energy, the steps of confining a gas working fluid in free and open communication throughout a closed system comprising a high temperature hot expander chamber of variable volume, a low temperature refrigerator expander chamber of variable volume, a compressor chamber of-variable volume, said compressor chamber operating'at a temperature intermediate that of saidhot expander and refrigerator expander chambers, a first heat exchanger assembly connected intermediate said hot expander chamber and said compressor chamber, and a second heat exchanger assembly connected intermediate said refrigerator expander chamber and said compressor chamber, said first and second said heat exchanger assemblies each including means for adding thermal energy to the working fluid,

storing and releasing thermal energy, and removing thermal energy from the working fluid; varying the volumes of said hot and refrigerator expander chambers substantially harmonically' and substantially in phase with each other from their minimum values to their maximum values andback to their minimum values in an expansion cycle of 360; varying the volume of said heat exchangers to said compressor chamber, and a compression phase; adding high temperature thermal energy to the working fluid in said first heat exchanger assembly and removing thermal energy from the working fluid in said second heat exchanger assembly during said first substantially constant volume phase, thereby maintaining the pressure of said workingfluid substantially constant during said first substantially constant volume phase; adding low temperature thermal energy to the working fluid in said second heat exchanger assembly and removing thermal energy from the working fluid in said first heat exchanger assembly during said second substantially constant volume phase, thereby maintaining the pressure of said working fluid substantially constant during said second substantially constant volume phase. v

2. A thermal refrigeration process as in claim 1 wherein the relative workingvolumes of the expander chambers and the quantities of thermal energy added to and subtracted from the working fluid during the substantially constant volume phases are such that the work done in the expander chambers is substantially equal to the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the system; whereby said process is adapted for producing refrigeration alone.

3. A thermal refrigeration process as in claim 1 wherein the relative working volumes of the expander chambers and the quantities of thermal energy added to and subtracted from the working fluid during the substantially constant volume phases are such that the work done in the, expander chambers is greater than-the sum of the work done in. the compressor chamber and the work required to overcome friction and leakage in the system, whereby said process is adaptedfor producing both refrigeration and work output, the work output cycle being out of phase with the refrigeration cycle.

4. A thermal refrigeration process as .in claim 1 together with the additional step of adding work input to said system to-suppl'ement the thermal energy added in said heat exchangers in producing refrigeration.

5. A thermal refrigeration process as in claim 4 wherein said work input is provided by mechanically varying the volume of said expander and compressor chambers.

6; In a process for producing refrigeration from thermal energy, the steps of compressing a working fluid in at least one hot expander chamber, at least one refrigerator expander chamber and at least one compressor chamber, said compressor chamber operating at a temperature intermediate the temperatures of the expancompressor chamber substantially harmonically from its minimum value to its'maximumvalue and back to its minimum value in a compression cycle of 360, with bers to said compressor chamber in a second substan-' tially constant volume and pressure stroke; adding high temperature thermal energy to the working fluid passing from said compressor chamber to said hot expander chamber and removing low temperature thermal energy from the working fluid passing from said compressor chamber to said refrigerator expander chamber during the first constant volume stroke; and adding low temperature thermal energy to the working fluid passing from said refrigerator expander chamber to said compressor chamber and removing high temperature thermal energy from the working fluid passing from said hot expander chamber to said compressor chamber during the second constant volume stroke.

7. In thermal refrigeration process as in claim 6 therein the relative volumes of the expander chambers and the quantities of thermal energy added and subtracted are such that the work done in the expander chambers is substantially equal to the sum of the work done in the compressor chamber and the work required to overcome friction and leakage, whereby said process is adapted for producing refrigeration along with no work output.

8. A thermal refrigeration process as in claim 6 wherein the relative volumes of the expander chambers and the quantities of thermal energy added and subtracted are such that the work done in the expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction'and leakage whereby said process is adapted for producing refrigeration plus work output, the work output cycle being out of phase with therefrigeration cycle.

9. A thermal refrigeration process'as in claim 6 together with the additional step of adding work input to supplement the thermal energy in producing refrigera- I tron.

10. In apparatus for producing refrigeration from thermal energy, first means defining a hot expander chamber; second means defining a refrigerator expander chamber; third meansdefininga compressor chamber; the temperature of said compressor chamber being intermediate the temperatures of the expander chambers; first heat exchanger means connected to said first and third means in such manner that said hot expander chamber is in communication with said compressor chamber through said first heat exchangermeans; second heat exchanger means connected to said second and third means in suchvmanner that said refrigerator expander chamber is in communication with said compressor chamber through said second heat exchanger means; said chambers and heat exchanger means forming a closed system adapted for containing a gas working fluid; movable means carried by each'of said first, second and third means for varying the volumes of said expander and compressor chambers substantially harmonically between maximum and minimum values; linking means connecting said movable means in such manner thatsaid expander volumes vary substantially in phase with each other and lead said compressor volume by an angle suchthat the net volume of said chambers passes through acycle comprising a first substantially constant volume phase in which the working fluid is transferred from said'compressor chamber through said first and second heat exchanger means to said expander chambers. an expansionphase in which the working fluid is expanded in saidexpander and compressor chambers, a secondsubstantially constant volume phase in which the working fluid is transferred from said expander chambers through said first and second heat exchanger means to said compressor chamber, and a compression phase in which the working fluid is compressed in said expander and compressor chambers; and means forming a part of said heat exchanger means for adding thermal energy to and extracting thermal energy from the working fluid during said first and second constant volume phases.

11. Thermal refrigeration apparatus as in claim 10 wherein said first heat exchanger means includes means for adding high temperature thermal energy to the working fluid during said first constant volume phase and means for extracting thermal energy from the working fluid during said second constant volume phase; and wherein said second heat exchanger means.

includes means for extracting thermal energy from the working fluid during said first constant'volume phase and means for adding low temperature energy to the working fluid during said second constant volume phase.

12. A thermal refrigeration apparatus as in claim 10 wherein the relative working .volumes of the expander chambers and the quantities of thermal energy added and extracted during the substantially constant volume phases are such that the work done in the expander chambers is substantially equal to the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing refrigeration alone. 13. Thermal refrigeration apparatus as in claim 10 wherein the relative working volumes of the expander chambers and the quantities of thermal energy added and extracted during the substantially constant volume phases are such that the work done in the expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing both refrigeration and work output, the work output cycle being out of phase with the refrigeration cycle.

14. Thermal refrigeration apparatus as in claim 10 together with driving means connected to said movable means for supplementing the-thermal energy input to said apparatus with work energy input in producing refrigeration.

15. In thermal refrigeration apparatus, first means forming an arcuate hot expander chamber; second means forming an arcuate refrigerator expander chamber; third means forming an arcuate compressor chamber; oscillating vane means in each of said chambers movable between advanced and retracted positions to form in each chamber a pair of alternately enlarging and diminishing volumes each adapted to receive and discharge a working fluid; linking means connected to said oscillating vane means in such manner that the-volumes of saidexpander chamber vary substantially in phasewith each other and lead the volume of said compressor chamber, said linking means including an oscillating shaft connected to said oscillating vane means, a crankshaft, and connecting rod means connecting said oscillating shaft to said crankshaft; first flow passage means interconnecting one of the volumes in said hot expander chamber with one of the volumes in said compressor chamber; second flow passage means interconnecting one of the volumes in said refrigerator expander chamber with said one volume in said compressor chamber; and first and second heat exchanger ond heat exchanger means includes a refrigerator heat exchanger adjoining said refrigerator expander chamher, a cooler adjoining said compressor chamber, and a regerierator intermediate said refrigerator and cooler.

17. Thermal refrigeration apparatus as in claim wherein the sum of the working volumes in said expander chambers is substantially equal to the working volume of said compressor chamber whereby during each 360 of crankshaft rotation the net volume of the interconnected expander and compressor volumes undergoes a first substantially constant volume phase, an expansion phase, a second substantially constant volume phsae, and a compression phase.

18. Thermal refrigeration apparatus as in claim 17 wherein said first and second heat exchanger means are adapted for both adding thermal energy to and extracting thermal energy from the working fluid during each of the constant volume phases to maintain the'pressure of the'working fluid substantially constant during said phases. l i I 19. Thermal refrigeration apparatus as in claim 18 wherein the relative volumes of the interconnected expander chambers and the quantities of thermal energy added and extracted in the heat exchanger means are such'that the work done in the expander chambers is substantially equal to the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus. is adapted for producing refrigeration alone. I I f 20. Thermal refrigeration apparatus as in claim 18 wherein the relative volumes of the interconnected expander chambers and the quantities of thermal energy added and extracted in the heat exchanger means are such that the work done in the, expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparams is adapted for producing'refrigeration and work output, the work output cycle being out of phase with the refrigeration cycle.

21. Thermal refrigeration apparatus as in claim 18 together with driving means connected to said crankshaft for supplying .work input to supplement the thermal energy in producing refrigeration.

. 22. Thermal refrigeration apparatus as in claim 15 together with means forming second arcuate expander and compressor chambers diametrically opposite the first named expander and compressor chambers in said first, seconds-and third means; said oscillating vane means being adapted forforming in each of said second chambers an additional pair of altematelyenlarging and diminishing volumes adapted to receive and discharge the working fluid, and means connecting one of the volumes of each additional pair of fluid communication with the first named volume which is diametrically opposite andenlarging and diminishing in phase with the additional volume.

23. In apparatus for producing'refrigeration from thermal energy, means forming a hot expander chamber, means forming a refrigerator expander chamber; means forming a compressor chamber; said compressor chamber operating at a temperature intermediate the temperature of the expander chambers; piston means in each of said chambers movable between advanced and retracted positions for enlarging and diminishing the volumes of said chambers, thereby adapting said chambers for receiving and discharging a working fluid;

linking means including a crankshaft and connectin rods interconnecting said piston means in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volume of said compressor chamber; first flow passage means interconnecting said hot expander chamber and said compressor chamber; second flow passage means interconnecting said refrigerator expander chamber and said compressor chamber; and first and second heat exchanger means disposed in said first and second flow passage means, respectively.

24. Thermal refrigeration apparatus as in claim 23 wherein said first heat exchanger means includes a heater adjoining said hot expander chamber, a cooler adjoining said compressor chamber, and a regenerator intermediate said heater and cooler and said second heat exchanger means includes a refrigerator heat exchanger adjoining said refrigerator expander chamber, a cooler adjoining said compressor chamber, and a regenerator intermediate said refrigerator and cooler.

25. Thermal refrigeration apparatus as in claim 23 wherein thesum of the working-volumes in said expander chambers is substantially equal to the working volume of said compressor chamber, whereby during each 360 of crankshaft rotation the net volume of the interconnected expander and compressor chambers undergoes aifirst substantially constant volume phase, an expansion phase, a second substantially constant volume phase, and a compression phase.

26.'Thermal refrigeration apparatus as in claim 25 wherein said first and second heat exchanger means are adapted for both adding thermal energy to and extracing thermal energy from the working fluid during each of the constant volume phase to maintain the pressure of the working fluid substantially constant during said phases.

27. Thermal refrigeration apparatus as in claim 26 wherein the relative volumes of the expander chambers and the quantities of thermal energy added and extracted in the heat exchanger means are such that the work done in the expander chambers is substantially equal to the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing refrigeration alone.

28. Thermal refrigeration apparatus as in claim 26 wherein the relative volume of the expander chambers and the quantities of. thermal energy added and. extracted in the heat exchanger means are such that the work done in the expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing refrigeration and work output, the work outputcycle being out of phase with the refrigeration cycle.

29. Thermal refrigeration apparatus as in claim 26 together with driving means connected to said crankshaft for supplying work input to supplement the thermal energy in producing refrigeration.

30. Thermal refrigeration apparatus as in claim 23 wherein said'compressor chamber is formed in two sections, each of said first and second flow passageways being connected to a different one of said sections, each of said sections having piston means movable between advanced and retracted positions for enlarging and diminishing the volumes of said sections, said linking means connecting the pistons in said sections in such mannerthat the volumes of said sections vary substantially in phase with each other, together with flow passage means connecting the compressor chamber sections in free and open communication with each other.

31. Thermal refrigeration apparatus as in claim 30 wherein the total working volume of said compressor chamber is substantially equal to the total working volume of said expander chambers.

32. Thermal refrigeration apparatus as in claim 23 together with means forming a balancing chamber; pis ton means in said balancing chamber movable between advanced and retracted positions for enlarging and diminishing the volume of the chamber; the piston means in the balancing chamber and the refrigerator expander chamber being arranged in such manner that the volume of said balancing chamber varies substantially 180 out of phase with the volume of said'refrigerator expander chamber; and flow passage means connecting said balancing chamber in free and open communication with said second flow passage means intermediate said compressor chamber and said second heat exchanger means.

33. Thermal refrigerator apparatus as in claim 32 together with means forming a second balancing chamber; piston means movably disposed in said chamber for varying the volume of said balancing chamber substantially 180 out of phase with the volume of said hot expander chamber; and flow passage means connecting said second balancing chamber in free and open communication with said first flow passage means intermediate said compressor chamber and said first heat exchanger means.

34. In apparatus for producing refrigeration from thermal energy, refrigerationand work from thermal energy, or refrigeration from thermal energy supplemented by input work energy, means forming first, second and third cylinders, piston means in said first and second cylinders movable between advanced and retracted positions to form, respectively, a hot expander chamber and a compressor chamber having substantially equal working volumes adapted for receiving and discharging a working fluid; displacer piston means in said third cylinder movable between advanced and retracted positions to form in said cylinder a refrigerator expander chamber and a balancing chamber of alternately expander chamber and a balancing chamber of alternately expanding and diminishing volumes adapted for receiving and discharging a working fluid; said compressor chamber and balancing chamber operating at a temperature intermediate the temperatures of said expander chambers; linking means connecting said piston means and displacer piston means in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volume of said compressor chambenfirst flow passage means interconnecting said hot expander chamber and said compressor chamber; second flow passage means interconnecting said refrigerator expander chamber, said balancing chamber and said compressor chamber, first heat exchanger means disposed in said first flow passage means; and second heat exchanger means disposed in said second flow passage means, one end of said heat exchanger means being connected to said refrigerator expander chamber and the other end being connected to said balancing chamber and to said compressor chamber.

35. ln apparatus for producing refrigeration from thermal energy, refrigeration and work thermal energy, or refrigeration from thermal energy supplemented by work energy, means'forming first, second, and third cylinders; displacer piston means in said first cylinder movable between said advanced and retracted positions to form in said cylinder a hot expander chamber and a first balancing compressor chamber of alternately expanding and diminishing volumes adapted for receiving and discharging a working fluid at high and intermediate temperatures, respectively; piston means in said second cylinder movable between advanced and retracted positions to form a power chamber of expanding and diminishing volume adapted for receiving and discharging a working fluid; displacer piston means in said third cylinder movable between advanced and retracted positions to form in said cylinder a refrigerator expander chamber and a second balancing compressor chamber of alternately expanding and diminishing volumes adapted for receiving and discharging a working fluid at a low temperature and at said intermediate temperature, respectively; linking means connecting said piston means and displacer piston means in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volume of said power chamber by an angle on the order of 90 degrees; first flow passage means interconnecting said hot expander chamber, said first balancing compressor chamber, and said power chamber; second flow passage means interconnecting said refrigerator'expander chamber, said second balancing compressor chamber, and said power chamber; heat exchanger means disposed in eachof said first and second flow passage means, one end of each heat exchanger means being connected to the expander chamber and the other end being connected to thebalancing compressor chamber.

36. In apparatus for producing refrigeration from thermal energy, refrigeration and work from thermal energy or refrigeration from thermal energy supplemented by work energy, means forming first and second cylinders; displacer and power piston means in said first cylinder movable between advanced and retracted positions to form a hot expander chamber and a compressor chamber of expanding and diminishing volumes adapted to receive and discharge a working fluid at high and intermediate temperatures; displacer piston means in said second cylinder movable between advanced and retracted positions to form a refrigerator expander chamber and a balancing chamber of alternately expanding and contracting volumes adapted to receive and discharge a working fluid at a low temperature and at said intermediate temperature, respectively; linking means connecting said displacer and power pis ton means in such manner that the volumes of said ex-

Claims

1. In a process for producing refrigeration from thermal energy, the steps of confining a gas working fluid in free and open communication throughout a closed system comprising a high temperature hot expander chamber of variable volume, a low temperature refrigerator expander chamber of variable volume, a compressor chamber of variable volume, said compressor chamber operating at a temperature intermediate that of said hot expander and refrigerator expander chambers, a first heat exchanger assembly connected intermediate said hot expander chamber and said compressor chamber, and a second heat exchanger assembly connected intermediate said refrigerator expander chamber and said compressor chamber, said first and second said heat exchanger assemblies each including means for adding thermal energy to the working fluid, storing and releasing thermal energy, and removing thermal energy from the working fluid; varying the volumes of said hot and refrigerator expander chambers substantially harmonically and substantially in phase with each other from their minimum values to their maximum values and back to their minimum values in an expansion cycle of 360*; varying the volume of said compressor chamber substantially harmonically from its minimum value to its maximum value and back to its minimum value in a compression cycle of 360*, with said compression cycle lagging said expansion cycle by an angle such that the net volume of said expander and compressor chambers undergoes a cycle comprising a first substantially constant volume phase in which the working fluid is transferred from said compressor chamber through the heat exchangers to said expander chambers, an expansion phase, a second substantially constant volume phase in which the working fluid is transferred from said expander chambers through the heat exchangers to said compressor chamber, and a compression phase; adding high temperature thermal energy to the working fluid in said first heat exchanger assembly and removing thermal energy from the working fluid in said second heat exchanger assembly during said first substantially constant volume phase, thereby maintaining the pressure of said working fluid substantially constant during said first substantially constant volume phase; adding low temperature thermal energy to the working fluid in said second heat exchanger assembly and removing thermal energy from the working fluid in said first heat exchanger assembly during said second substantially constant volume phase, thereby maintaining the pressure of said working fluid substantially constant during said second substantially constant volume phase.

2. A thermal refrigeration process as in claim 1 wherein the relative working volumes of the expander chambers and the quantities of thermal energy added to and subtracted from the working fluid during the substantially constant volume phases are such that the work done in the expander chambers is substantially equal to the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the system, whereby said process is adapted for producing refrigeration alone.

3. A thermal refrigeration process as in claim 1 wherein the relative working volumes of the expander chambers and the quantities of thermal energy added to and subtracted from the working fluid during the substantially constant volume phases are such that the work done in the expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the system, whereby said process is adapted for producing both refrigeration and work output, the work output cycle being out of phase with the refrigeration cycle.

4. A thermal refrigeration process as in claim 1 together with the additional step of adding work input to said system to supplement the thermal energy added in said heat exchangers in producing refrigeration.

6. In a process for producing refrigeration from thermal energy, the steps of compressing a working fluid in at least one hot expander chamber, at least one refrigerator expander chamber and at least one compressor chamber, said compressor chamber operating at a temperature intermediate the temperatures of the expander chambers, transferring the working fluid from said compressor chamber to said expander chambers simultaneously in a first substantially constant volume and pressure stroke; expanding the working fluid in said expander and compressor chambers; transferring the working fluid simultaneously from said expander chambers to said compressor chamber in a second substantially constant volume and pressure stroke; adding high temperature thermal energy to the working fluid passing from said compressor chamber to said hot expander chamber and removing low temperature thermal energy from the working fluid passing from said compressor chamber to said refrigerator expander chamber during the first constant volume stroke; and adding low temperature thermal energy to the working fluid passing from said refrigerator expander chamber to said compressor chamber and removing high temperature thermal energy from the working fluid passing from said hot expander chamber to said compressor chamber during the second constant volume stroke.

8. A thermal refrigeration process as in claim 6 wherein the relative volumes of the expander chambers and the quantities of thermal energy added and subtracted are such that the work done in the expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction and leakage whereby said process is adapted for producing refrigeration plus work output, the work output cycle being out of phase with the refrigeration cycle.

9. A thermal refrigeration process as in claim 6 together with the additional step of adding work input to supplement the thermal energy in producing refrigeration.

10. In apparatus for producing refrigeration from thermal energy, first means defining a hot expander chamber; second means defining a refrigerator expander chamber; third means defining a compressor chamber; the temperature of said compressor chamber being intermediate the temperatures of the expander chambers; first heat exchanger means connected to said first and third means in such manner that said hot expander chamber is in communication with said compressor chamber through said first heat exchanger means; second heat exchanger means connected to said second and third means in such manner that said refrigerator expander chamber is in communication with said compressor chamber through said second heat exchanger means; said chambers and heat exchanger means forming a closed system adapted for containing a gas working fluid; movable means carried by each of said first, second and third means for varying the volumes of said expander and compressor chambers substantially harmonically between maximum and minimum values; linking means connecting said movable means in such manner that saiD expander volumes vary substantially in phase with each other and lead said compressor volume by an angle such that the net volume of said chambers passes through a cycle comprising a first substantially constant volume phase in which the working fluid is transferred from said compressor chamber through said first and second heat exchanger means to said expander chambers, an expansion phase in which the working fluid is expanded in said expander and compressor chambers, a second substantially constant volume phase in which the working fluid is transferred from said expander chambers through said first and second heat exchanger means to said compressor chamber, and a compression phase in which the working fluid is compressed in said expander and compressor chambers; and means forming a part of said heat exchanger means for adding thermal energy to and extracting thermal energy from the working fluid during said first and second constant volume phases.

11. Thermal refrigeration apparatus as in claim 10 wherein said first heat exchanger means includes means for adding high temperature thermal energy to the working fluid during said first constant volume phase and means for extracting thermal energy from the working fluid during said second constant volume phase; and wherein said second heat exchanger means includes means for extracting thermal energy from the working fluid during said first constant volume phase and means for adding low temperature energy to the working fluid during said second constant volume phase.

12. A thermal refrigeration apparatus as in claim 10 wherein the relative working volumes of the expander chambers and the quantities of thermal energy added and extracted during the substantially constant volume phases are such that the work done in the expander chambers is substantially equal to the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing refrigeration alone.

13. Thermal refrigeration apparatus as in claim 10 wherein the relative working volumes of the expander chambers and the quantities of thermal energy added and extracted during the substantially constant volume phases are such that the work done in the expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing both refrigeration and work output, the work output cycle being out of phase with the refrigeration cycle.

14. Thermal refrigeration apparatus as in claim 10 together with driving means connected to said movable means for supplementing the thermal energy input to said apparatus with work energy input in producing refrigeration.

15. In thermal refrigeration apparatus, first means forming an arcuate hot expander chamber; second means forming an arcuate refrigerator expander chamber; third means forming an arcuate compressor chamber; oscillating vane means in each of said chambers movable between advanced and retracted positions to form in each chamber a pair of alternately enlarging and diminishing volumes each adapted to receive and discharge a working fluid; linking means connected to said oscillating vane means in such manner that the volumes of said expander chamber vary substantially in phase with each other and lead the volume of said compressor chamber, said linking means including an oscillating shaft connected to said oscillating vane means, a crankshaft, and connecting rod means connecting said oscillating shaft to said crankshaft; first flow passage means interconnecting one of the volumes in said hot expander chamber with one of the volumes in said compressor chamber; second flow passage means interconnecting one of the volumes in said refrigerator expander chamber with said one volume in said compressor chamber; and first and second heat exchanger means disposed in said first and second flow passage means, respectively.

16. Thermal refrigeration apparatus as in claim 15 wherein said first heat exchanger means includes a heater adjoining said hot expander chamber, a cooler adjoining said compressor chamber, and a regenerator intermediate said heater and refrigerator; and said second heat exchanger means includes a refrigerator heat exchanger adjoining said refrigerator expander chamber, a cooler adjoining said compressor chamber, and a regenerator intermediate said refrigerator and cooler.

17. Thermal refrigeration apparatus as in claim 15 wherein the sum of the working volumes in said expander chambers is substantially equal to the working volume of said compressor chamber whereby during each 360* of crankshaft rotation the net volume of the interconnected expander and compressor volumes undergoes a first substantially constant volume phase, an expansion phase, a second substantially constant volume phsae, and a compression phase.

18. Thermal refrigeration apparatus as in claim 17 wherein said first and second heat exchanger means are adapted for both adding thermal energy to and extracting thermal energy from the working fluid during each of the constant volume phases to maintain the pressure of the working fluid substantially constant during said phases.

19. Thermal refrigeration apparatus as in claim 18 wherein the relative volumes of the interconnected expander chambers and the quantities of thermal energy added and extracted in the heat exchanger means are such that the work done in the expander chambers is substantially equal to the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing refrigeration alone.

20. Thermal refrigeration apparatus as in claim 18 wherein the relative volumes of the interconnected expander chambers and the quantities of thermal energy added and extracted in the heat exchanger means are such that the work done in the expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing refrigeration and work output, the work output cycle being out of phase with the refrigeration cycle.

21. Thermal refrigeration apparatus as in claim 18 together with driving means connected to said crankshaft for supplying work input to supplement the thermal energy in producing refrigeration.

22. Thermal refrigeration apparatus as in claim 15 together with means forming second arcuate expander and compressor chambers diametrically opposite the first named expander and compressor chambers in said first, second, and third means; said oscillating vane means being adapted for forming in each of said second chambers an additional pair of alternately enlarging and diminishing volumes adapted to receive and discharge the working fluid, and means connecting one of the volumes of each additional pair of fluid communication with the first named volume which is diametrically opposite and enlarging and diminishing in phase with the additional volume.

23. In apparatus for producing refrigeration from thermal energy, means forming a hot expander chamber, means forming a refrigerator expander chamber; means forming a compressor chamber; said compressor chamber operating at a temperature intermediate the temperature of the expander chambers; piston means in each of said chambers movable between advanced and retracted positions for enlarging and diminishing the volumes of said chambers, thereby adapting said chambers for receiving and discharging a working fluid; linking means including a crankshaft and connectin rods interconnecting said piston means in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volume of said compressor chamber; first flow passage means interconnecting said hot expander chamber and said compressor chamber; second flow passage means interconnecting said refrigerator expander chamber and said compressor chamber; and first and second heat exchanger means disposed in said first and second flow passage means, respectively.

25. Thermal refrigeration apparatus as in claim 23 wherein the sum of the working volumes in said expander chambers is substantially equal to the working volume of said compressor chamber, whereby during each 360* of crankshaft rotation the net volume of the interconnected expander and compressor chambers undergoes a first substantially constant volume phase, an expansion phase, a second substantially constant volume phase, and a compression phase.

26. Thermal refrigeration apparatus as in claim 25 wherein said first and second heat exchanger means are adapted for both adding thermal energy to and extracing thermal energy from the working fluid during each of the constant volume phase to maintain the pressure of the working fluid substantially constant during said phases.

28. Thermal refrigeration apparatus as in claim 26 wherein the relative volume of the expander chambers and the quantities of thermal energy added and extracted in the heat exchanger means are such that the work done in the expander chambers is greater than the sum of the work done in the compressor chamber and the work required to overcome friction and leakage in the apparatus, whereby said apparatus is adapted for producing refrigeration and work output, the work output cycle being out of phase with the refrigeration cycle.

30. Thermal refrigeration apparatus as in claim 23 wherein said compressor chamber is formed in two sections, each of said first and second flow passageways being connected to a different one of said sections, each of said sections having piston means movable between advanced and retracted positions for enlarging and diminishing the volumes of said sections, said linking means connecting the pistons in said sections in such manner that the volumes of said sections vary substantially in phase with each other, together with flow passage means connecting the compressor chamber sections in free and open communication with each other.

32. Thermal refrigeration apparatus as in claim 23 together with means forming a balancing chamber; piston means in said balancing chamber movable between advanced and retracted positions for enlarging and diminishing the volume of the chamber; the piston means in the balancing chamber and the refrigerator expander chamber being arranged in such manner that the volume of said balancing chamber varies substantially 180* out of phase with the volume of said refrigerator expander chamber; and flow passage means connectIng said balancing chamber in free and open communication with said second flow passage means intermediate said compressor chamber and said second heat exchanger means.

33. Thermal refrigerator apparatus as in claim 32 together with means forming a second balancing chamber; piston means movably disposed in said chamber for varying the volume of said balancing chamber substantially 180* out of phase with the volume of said hot expander chamber; and flow passage means connecting said second balancing chamber in free and open communication with said first flow passage means intermediate said compressor chamber and said first heat exchanger means.

34. In apparatus for producing refrigeration from thermal energy, refrigeration and work from thermal energy, or refrigeration from thermal energy supplemented by input work energy, means forming first, second and third cylinders, piston means in said first and second cylinders movable between advanced and retracted positions to form, respectively, a hot expander chamber and a compressor chamber having substantially equal working volumes adapted for receiving and discharging a working fluid; displacer piston means in said third cylinder movable between advanced and retracted positions to form in said cylinder a refrigerator expander chamber and a balancing chamber of alternately expander chamber and a balancing chamber of alternately expanding and diminishing volumes adapted for receiving and discharging a working fluid; said compressor chamber and balancing chamber operating at a temperature intermediate the temperatures of said expander chambers; linking means connecting said piston means and displacer piston means in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volume of said compressor chamber; first flow passage means interconnecting said hot expander chamber and said compressor chamber; second flow passage means interconnecting said refrigerator expander chamber, said balancing chamber and said compressor chamber, first heat exchanger means disposed in said first flow passage means; and second heat exchanger means disposed in said second flow passage means, one end of said heat exchanger means being connected to said refrigerator expander chamber and the other end being connected to said balancing chamber and to said compressor chamber.

35. In apparatus for producing refrigeration from thermal energy, refrigeration and work thermal energy, or refrigeration from thermal energy supplemented by work energy, means forming first, second, and third cylinders; displacer piston means in said first cylinder movable between said advanced and retracted positions to form in said cylinder a hot expander chamber and a first balancing compressor chamber of alternately expanding and diminishing volumes adapted for receiving and discharging a working fluid at high and intermediate temperatures, respectively; piston means in said second cylinder movable between advanced and retracted positions to form a power chamber of expanding and diminishing volume adapted for receiving and discharging a working fluid; displacer piston means in said third cylinder movable between advanced and retracted positions to form in said cylinder a refrigerator expander chamber and a second balancing compressor chamber of alternately expanding and diminishing volumes adapted for receiving and discharging a working fluid at a low temperature and at said intermediate temperature, respectively; linking means connecting said piston means and displacer piston means in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volume of said power chamber by an angle on the order of 90 degrees; first flow passage means interconnecting said hot expander chamber, said first balancing compressor chamber, and said power chamber; second flow passage means interconnecting said refrigerator expander chamber, said second balancing compressor chamber, anD said power chamber; heat exchanger means disposed in each of said first and second flow passage means, one end of each heat exchanger means being connected to the expander chamber and the other end being connected to the balancing compressor chamber.

36. In apparatus for producing refrigeration from thermal energy, refrigeration and work from thermal energy or refrigeration from thermal energy supplemented by work energy, means forming first and second cylinders; displacer and power piston means in said first cylinder movable between advanced and retracted positions to form a hot expander chamber and a compressor chamber of expanding and diminishing volumes adapted to receive and discharge a working fluid at high and intermediate temperatures; displacer piston means in said second cylinder movable between advanced and retracted positions to form a refrigerator expander chamber and a balancing chamber of alternately expanding and contracting volumes adapted to receive and discharge a working fluid at a low temperature and at said intermediate temperature, respectively; linking means connecting said displacer and power piston means in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volume of said compressor chamber first flow passage means interconnecting said hot expander chamber and said compressor chamber; first heat exchanger means disposed in said first heat flow passage means; second flow passage means interconnecting said refrigerator expander chamber, said balancing volume, and said compressor chamber; and second heat exchanger means disposed in said second flow passage means, one end of said heat exchanger means being connected to said refrigerator expander chamber and the other end being connected to said balancing chamber and to said compressor chamber.

37. In apparatus for producing refrigeration from thermal energy, refrigeration and work from thermal energy, or refrigeration from thermal energy supplemented by work energy, means forming first and second cylinders; displacer and power piston means in each of said cylinders movable between advanced and retracted positions to form in said first cylinder a hot expander chamber and a first compressor chamber and in said second cylinder a refrigerator expander chamber and a second compressor chamber of expanding and diminishing volumes adapted to receive and discharge a working fluid at three temperature levels; linking means connecting said displacer and power piston means in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volumes of said compressor chambers by an angle on the order of 90* to 120*, the volumes of said compressor chambers varying substantially in phase with each other; first flow passage means interconnecting said hot expander chamber and said first compressor chamber; second flow passage means interconnecting said refrigerator expander chamber and said second compressor chamber; heat exchanger means disposed in each of said first and second flow passage means; and additional flow passage means interconnecting said first and second compressor chambers.

38. In apparatus for producing refrigeration from thermal energy, refrigeration and work from thermal energy, means forming first and second cylinders; displacer and power piston means in each of said cylinders movable between advanced and retracted positions to form in said first cylinder a hot expander chamber and a first compressor chamber and in said second cylinder a refrigerator expander chamber and a second compressor chamber of expanding and diminishing volumes adapted to receive and discharge a working fluid at three temperature levels; said displacer and power piston means being arranged in such manner that the volumes of said expander chambers vary substantially in phase with each other and lead the volumes of said compressor chambers, the volumes of said compressor chambers varying subsTantially in phase with each other; first flow passage means interconnecting said hot expander chamber and said first compressor chamber; second flow passage means interconnecting said refrigerator expander chamber and said second compressor chamber; heat exchanger means disposed in each of said first and second flow passage means; and additinal flow passage means interconnecting said first and second compressor chambers.