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EP0162868B1 - Moteur a cycle stirling et pompe thermique - Google Patents

Moteur a cycle stirling et pompe thermique Download PDF

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Publication number
EP0162868B1
EP0162868B1 EP19840904048 EP84904048A EP0162868B1 EP 0162868 B1 EP0162868 B1 EP 0162868B1 EP 19840904048 EP19840904048 EP 19840904048 EP 84904048 A EP84904048 A EP 84904048A EP 0162868 B1 EP0162868 B1 EP 0162868B1
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EP
European Patent Office
Prior art keywords
heat exchanger
externally
heated
space
gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19840904048
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German (de)
English (en)
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EP0162868A4 (fr
EP0162868A1 (fr
Inventor
Matthew P. Mitchell
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Individual
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Individual
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Priority to AT84904048T priority Critical patent/ATE43680T1/de
Publication of EP0162868A1 publication Critical patent/EP0162868A1/fr
Publication of EP0162868A4 publication Critical patent/EP0162868A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2244/00—Machines having two pistons
    • F02G2244/50—Double acting piston machines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2254/00—Heat inputs
    • F02G2254/30—Heat inputs using solar radiation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2270/00—Constructional features
    • F02G2270/50—Crosshead guiding pistons

Definitions

  • the present invention is directed to novel forms of a hot gas engine and heat pump in which heat to be converted to work or to be pumped is applied external to cylinders containing the working gas.
  • the present invention is directed to improved forms of a Stirling cycle engine and heat pump.
  • the term "heat pump” is used in its generic sense designating a device which may be used either for heating or refrigeration.
  • the present invention is directed to a novel machine utilizing a modified "Stirling cycle".
  • the first Stirling cycle machine was invented in 1816 by Robert Stirling. It ran as an engine, turning heat into mechanical energy. Subsequent development has shown that Stirling cycle machines can also be run in reverse, being driven by mechanical energy to act as heat pumps in refrigeration applications. Practical problems, discussed below, have prevented Stirling cycle machines from coming into widespread use in any of their potential applications.
  • the expansion of the working gas in the hot space of the Stirling cycle machine during the power stroke of the cycle produces work when the machine is run as an engine.
  • the compression phase of the cycle absorbs work when the Stirling machine is run as an engine, but it absorbs less work than is generated in the expansion phase of the cycle.
  • the excess work is absorbed in part by mechanical and gas friction (including that involved in the transfer/regeneration phase). The remainder of the work is useful work.
  • a Stirling cycle machine When run as a heat pump, a Stirling cycle machine requires more energy to compress the working gas during the compression phase of the cycle than is returned during the expansion phase of the cycle because the part of the machine that is absorbing heat from the surroundings (i.e., the expansion space) is colder than the part of the machine where the working gas is compressed (i.e., the compression space).
  • the present invention is described below as an engine, with reference to the compression space as the "cold space” and the expansion space as the “hot space”. If the machine were operated as a refrigerator (heat pump) rather than as an engine, temperatures of the compression and expansion space would be reversed. Both when the invention is used as an engine and as a heat pump, gas entering the expansion space is subjected to external heating, and gas entering the compression space is subjected to external cooling.
  • Stirling cycle engines are considerable. They are, in theory, highly efficient. Also, since their heat sources are external to the working gas, some of the air pollution problems associated with internal combustion engines can be avoided. Since fuel for a Stirling cycle engine can be burned steadily at atmospheric pressure rather than exploded at high temperature and pressure, Stirling cycle engines are comparatively quiet. They may be powered by any available source of heat and can thus operate with any type of fuel, including solar heat, geothermal heat or heat from nuclear fission or fusion.
  • the present invention accomplishes improvements in all of these areas, producing an efficient thermodynamic cycle with mechanical apparatus employing simple harmonic motion with reduced gas friction.
  • improvements in Stirling engine type devices are obtained by employing two separate volumes of gas which are expanded and compressed through Stirling type cycles, sequentially sharing expansion and compression chambers with one volume undergoing expansion while the other undergoes compression.
  • gas enters and exits the expansion space of the engine through different ports and a regenerator at the entrance port retains heat of compression and may permit superheating of the working gas in the regenerator.
  • the invention provides a method of the Stirling Cycle type for converting energy between work and heat employing a first heat exchanger means with an externally-heated part and an externally-cooled part, compression and expansion chambers connected to the first heat exchanger means, piston means for decreasing the volume of one of the chambers while increasing the volume of the other chamber, and a first quantity of gas confined to the compression and expansion chambers and the heat exchanger means, comprising the steps of (a) confining a second quantity of gas in a second heat exchanger means having an externally heated part and an externally-cooled part, (b) connecting the externally-heated part of the second heat exchanger means to the expansion chamber while connecting the externally-cooled part of the first heat exchanger means to the compression chamber during a first working stroke of the piston means, (c) connecting the externally-heated and cooled parts of the second heat exchanger means to the expansion and compression chambers, respectively, during a return stroke of the piston means, (d) connecting the heated part of the first heat exchanger means to
  • a machine of the Stirling Cycle type, adapted to carry out this method is also object of the present invention.
  • a machine operating according to the method of the invention can achieve a high compression ratio and can thus function as a refrigerator/heat pump, in contrast to the prior art method disclosed in US-A-3,667,215.
  • regenerator means are serially interposed between the externally-heated heat exchanger means and the externally-cooled heat exchanger means in each of said heat exchanger assemblies; in addition, or in place thereof, regenerator means may be serially interposed between said externally-heated heat exchanger means and said valve means at the externally-heated end of each of said heat exchanger assemblies.
  • regenerator means may be serially interposed between said externally-heated heat exchanger means and said valve means at the externally-heated end of each of said heat exchanger assemblies.
  • a bypass technique may be employed, wherein the flow of gas in step (c) is routed through a separate conduit bypassing the externally-heated heat exchanger means of said second heat exchanger assembly and the flow of gas in step (e) is routed through a separate conduit bypassing the externally-heated heat exchanger means of said first heat exchanger assembly.
  • a plurality of second quantities of gas are confined in a corresponding plurality of second heat exchanger means.
  • a hot gas engine comprising compression and expansion chambers, piston means for decreasing the space in one of the chambers and simultaneously increasing the space in the other chamber, heat exchanger means including an externally-heated space connected to an externally-cooled space, with the externally-heated space also connected to both the expansion chamber and the compression chamber and the externally-cooled space connected both to the expansion chamber and the compression chamber, and a quantity of compressible gas substantially confined for circulation through the chambers and heat exchanger means.
  • this prior art machine there is a heater in one conduit and a cooler in the other, and it employs only a single quantity of gas, moving always in the same direction through the conduits.
  • a machine of the Stirling Cycle type as proposed by the invention has some superficial similarities with the hot gas engine disclosed in US-A-3,667,215 in that it also comprises compression and expansion chambers, piston means for decreasing the space of one of the chambers and simultaneously increasing the space of the other chamber, heat exchanger means including an externally-heated space connected to an externally-cooled space, with the externally-heated space connected to the expansion chamber and the externally-cooled space connected to the compression chamber, and a quantity of compressible gas substantially confined for circulation through the chambers and heat exchanger means, but differs therefrom in that there are provided a second heat exchanger assembly including an externally-heated space connected to an externally-cooled space, with the externally-heated space connected to the expansion chamber and an externally-cooled space connected to the compression chamber, a second quantity of compressible gas substantially confined for circulation through the chambers and said second heat exchanger assembly, and control means for communicating the externally-heated space of the first mentioned heat exchanger means to the expansion chamber while communicating the externally-cooled space
  • each heat exchanger assembly is a reversing flow, whereas in the prior art method disclosed in US-A-3,667,215, the gas flow through the heat exchangers is unidirectional in a continuous loop.
  • separate inlet and outlet valve means connect the expansion chamber to each of the heat exchanger assemblies with the outlet valve communicating with the heat exchanger assembly between the externally-heated and the externally-cooled spaces.
  • a regenerator is connected between the externally-heated space of each heat exchanger assembly and the inlet valve means; further, a regenerator is serially interposed between the externally-heated spaces and the externally-cooled spaces in each of said heat exchanger assemblies.
  • the present invention provides an engine employing at least one cylinder, sealed at both ends, fitted with a double-acting piston, and with two or more heat-exchanger assemblies connecting one end of the cylinder to the other end of the cylinder.
  • Each heat exchanger assembly contains at least a heater, a cooler, and a valve at each end where it opens into one or the other end of the cylinder.
  • Each heat exchanger may also contain one or more regenerators and/or one or more bypasses and bypass valves.
  • each heat exchanger assembly participates in a thermodynamic cycle, sharing, in its turn, the assistance of the piston for the movement of gas.
  • the cycles accomplished by all of the heat exchanger assemblies are identical, but interlocked in time sequence.
  • the theoretical operation of the cycle in each heat exchanger assembly may be as follows:
  • the working gas is expelled from the compression space of the cylinder into the heat exchanger assembly and thereby compressed from its lowest pressure level during the cycle to a higher level, being cooled as it passes through the cooler during this stroke to minimize the work required to compress it;
  • the working gas is confined in the heat exchanger assembly in its compressed state, with no change in volume, and no input or output of mechanical work.
  • the working gas is expanded out of the heat exchanger assembly into the expansion space of the cylinder, dropping from its highest pressure to an intermediate pressure, while being heated during this stroke to minimize the pressure drop and maximize the work done, and;
  • the working gas is moved, with no change in volume, out of the expansion space of the cylinder, through the heat exchanger assembly and into the compression space of the cylinder with no significant input or output of mechanical work, so that it can be compressed again, repeating stroke 1.
  • this "regeneration" stroke the working gas is cooled so that its pressure reaches the lowest point in the cycle at the beginning of the compression stroke, thereby reducing the amount of work required to compress the working gas during stroke I.
  • FIG. 1(a) This theoretical illustration of the local pressure of the gas is dependent upon heat transfer rates between gas and the surface of the heat exchangers. Gas trapped in the heat exchanger assembly during the isolation stroke would heat up or cool down depending upon the temperature of the adjacent surface. Gas in the cooler would cool. Gas in the heater would adjust its temperature in both directions; gas entering the heater during the preceding (compression) stroke would be cooler than the adjacent heat exchange surface but gas at the far, closed end of the heater would be compressed and would actually be hotter than the adjacent heater surface.
  • FIG. 1 look like two triangles, apex to apex, as shown in FIG. I(b).
  • the temperature rise and drop could cancel out perfectly. That would produce the triangle-shaped PN diagram of FIG. 1 (c) which also results theoretically from perfect, instantaneous heat transfer.
  • the PN diagram in Figure 1 could look like 1 (a), 1 (b), or 1 (c). It is conceivable that the same engine, running at different temperature differentials and/or different operating speeds might at times reflect each of these three PN diagrams.
  • the area under the compression curve (stroke 1) is less than the area under the expansion curve (stroke 3), and the difference is the mechanical work output of the engine.
  • FIG. 2 An elemental embodiment of the invention is shown schematically in FIG. 2.
  • a double acting piston 10 travels within an enclosed cylinder 9.
  • the piston is connected to a piston rod 11.
  • the piston rod 11 is in turn supported against lateral movement by a crosshead (not shown).
  • the piston rod 11 connects through a conventional connecting rod (not shown) to a crankshaft (not shown).
  • the piston rod passes through a seal 22.
  • One end of the cylinder 9 is connected to the other end of the cylinder through heat exchanger assemblies 12 and 13, consisting of, in each instance, a heater (12A, 13A) and a cooler (12B, 13B).
  • the heat exchanger assemblies communicate into the expansion space of the cylinder through ports 16, 17 and into the compression space of the cylinder through other ports 18, 19.
  • Between each port 16, 17 into the expansion space and its associated heater 12A, 13A is a valve (16A, 17A).
  • a valve 18A, 19A Between each port into the compression space and its associated cooler 12B, 13B is a valve 18A, 19A.
  • Regenerators 14 located between each heater and cooler are optional.
  • valves 16A, 17A, 18A, 19A open and close in this sequence:
  • FIG. 3 A preferred embodiment of an engine is shown in FIG. 3.
  • a double-acting piston 10 travels within an enclosed cylinder.
  • the piston is connected to a piston rod 11.
  • the piston rod 11 is in turn connected to a conventional connecting rod (not shown) which connects to a crankpin and crankshaft (not shown), and is preferably supported against lateral motion by a conventional cross-head (also not shown).
  • FIG. 3 there are two heat exchanger assemblies 12 and 13 consisting of a cooler 12B, 13B, a heater 12A, 13A and a regenerator 14A, 14B, connected in series.
  • the regenerator end of each heat exchanger assembly is connected to the hot end of the cylinder through valved ports 16 and 17, accommodating valve means 16A and 17A, respectively.
  • the other end of each heat exchanger assembly is connected to the compression valve cylinder ports 18 and 19 accommodating valve means 18A and 19A, respectively.
  • Bypass ports 20 and 21 accommodating valve means 20A and 21A, respectively, are provided, connecting the expansion space of the cylinder to each heater exchanger assembly 12, 13, between the cooler 12B, 13B and the heater 12A, 13A.
  • a second pair of regenerators 23A and 23B may be provided between the valves 20A and 21A and the cooling sections 12B and 13B.
  • working gas flows through the heat exchanger assemblies into the expansion space through valves 16A and 17A, but flows out of the expansion space into the heat exchanger assemblies through valves 20A and 21A.
  • the valving sequence is as follows:
  • the effect of this sequence is that, in the course of one cycle, the working gas flows through the cooler twice (once in each direction) but flows through the heater and regenerator only once, (in one direction).
  • the working gas passes through heater, cooler and the regenerator in both directions during each cycle.
  • the present invention thus eliminates some of the gas friction that occurs in the traditional Stirling cycle engine. Moreover, to the extent that there is gas friction resulting from passage of the gas through the regenerator, it is turned into heat, which is then transferred into expansion space rather than into the cooler.
  • the heaters 12A, 13A are heated by heating means (not shown), such as a combustor, solar energy, and the like.
  • the coolers 12B, 13B are cooled by water jackets, air, or other suitable heat sink.
  • the cycle of an engine according to the present invention differs from the traditional Stirling cycle in that much higher compression ratios are possible. Since an entire volume of working gas is swept into a heat exchanger assembly and locked there under compression by the valves at each end, the ratio of the swept volume of the cylinder to the volume of the heat exchanger assembly determines the compression ratio. By using a relatively small volume in the heat exchanger assembly high compression may be obtained.
  • the high compression attainable with the present engine is desirable in that it permits the engine to generate great power relative to its size.
  • the high compression ratio carries with it a penalty in the form of very high pressures in the machine at the conclusion of the compression stroke. This high pressure tends to raise the temperature of the working gas as the compression stroke progresses, increasing the amount of work consumed in compressing the working gas.
  • each heat exchanger assembly is arranged to limit the compression heating of the working gas.
  • each heat exchanger assembly is accomplished by arranging each heat exchanger assembly so that cold gas from the cold heat exchanger (orocenter regenerator, if any) is not immediately warmed as it enters the heater, such as, by using heater tubes substantially larger in diameter than those that would be used in a conventional Stirling cycle machine, or even a single heater tube. By thus reducing the heat exchange area of the heater, the heating process may be delayed.
  • regenerator and cooler tubes may be designed for rapid heat transfer so that gas entering either will assume the temperature of the regenerator or cooler tubes almost immediately.
  • the heater may have heat transfer characteristics such that the gas that is in the heater (12A, 13A) at the beginning of the compression stroke will have approached the temperature of the heater tube by the time that compression begins. Referring to FIG. 3, as the compression stroke progresses, that hot gas will be progressively forced towards the expansion valve (16A or 17A), and, through compression, further heated. To mitigate that effect, the expansion end regenerators (14A, 14B) are interposed between the heater and the ports into the expansion space so that heat from gas that is forced out of the heaters into the expansion end regenerators will be absorbed b the regenerators and the temperature rise will be mitigated. With sufficient thermal mass of the regenerators, minimal temperature rise will occur in the regenerator during any single cycle.
  • gas will be heated to expansion end regenerator temperature as it expands into the expansion space in the cylinder.
  • the temperature of that gas will, at least initially, exceed heater temperature. While the gas in the heater will drop in temperature as the expansion stroke progresses, it must pass through the expansion end regenerator on its way into the cylinder and will be heated in that process to a temperature close to or even above maximum heater tube temperature.
  • a bypass arrangement similar to that shown for the expansion end may be incorporated into the compression end. If that is done, working gas should enter the compression space through the coolers 12B, 13B, but leave the compression space through bypasses communicating directly with the center-mounted regenerators 23A, 23B.
  • valves in direct communication with the expansion space of a high pressure version of the engine will be pressure-sealing in both directions.
  • a simple gate valve (FIGS. 4A and 4B) may be used.
  • the gate 30 intersects the flow of working gas.
  • a hole 31 in the gate lines up with the path of flow, and the gas flows unimpeded.
  • a flat plate cuts off the gas flow.
  • both sides of the gate are suitably smooth and the ends of the opening through which the working gas passes can be ground to a smooth valve seat, then the gate will press first against one side and then the other side of its slot as gas pressure reverses. It thus forms a pressure seal 32 in either direction.
  • a suitable sealing means 33 further seals the gate 30 surfaces from leakage. Hermetically sealed, solenoid operated valves may also be used.
  • double poppet valves 35 may be used.
  • Other arrangements known in the valve pressure-sealing art will be obvious to those of ordinary skill.
  • timing of valve movements may be synchronized to piston movements by conventional mechanical, electrical or electronic means that sense crankshaft position.
  • tubes sets More than two heat exchanger assemblies
  • tubes may be used.
  • Another advantage of a single heater tube (or a small number of relatively large diameter heater tubes) is the substantial reduction of gas friction drag that can be accomplished.
  • machines according to the present invention should be balanced, i.e., the volumes of working gas associated with the heat exchanger assemblies should be essentially equal.
  • Most practical machines will be self-balancing, while running, due to the inability of the piston to completely scavenge the cylinder and valve ports. A small quantity of gas will remain in the compression space and in the compression space valve ports at the end of each power/compression stroke. If the heat exchanger assembly into which gas has just been compressed contains a disproportionately large quantity of gas, the residual quantity of gas in the compression space and compression space valve ports will also be disproportionately large.
  • Balancing the machine as an engine when the engine is to be started after it has been left in a condition such that working gas has leaked through valves or otherwise redistributed itself, may be achieved by a starting mechanism. Thus, it may be necessary to crank the engine until approximate balance is achieved. If the engine is already balanced when it is to be started, it may need only be cranked through one cycle to start.

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  • General Engineering & Computer Science (AREA)
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  • Physics & Mathematics (AREA)
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  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

Un moteur de type à cycle Stirling est doté d'une pluralité de montages d'échangeur thermique (12 et 13). Chaque montage se compose d'un refroidisseur (12B, 13B), d'un régénérateur (23A, 23B), d'un réchauffeur (12A, 13A) et d'un régénérateur monté en position terminale (14A, 14B) reliés en série. Grâce à l'utilisation de vannes (18A, 19A, 20A, 21A) synchronisées pour s'ouvrir et se fermer dans un ordre spécifique en fonction du mouvement d'un piston (10), deux volumes séparés de gaz sont comprimés, dilatés et transférés à travers des cycles de type Stirling, partageant séquentiellement des chambres de dilatation et de compression, un volume étant soumis à la dilatation pendant que l'autre est soumis à la compression, et un volume étant isolé dans un montage d'échangeur thermique alors que l'autre est transféré à travers l'autre montage d'échangeur thermique d'une extrémité du cylindre à l'autre.

Claims (10)

1. Procédé du type à cycle de Stirling pour une transformation d'énergie entre travail et chaleur utilisant un premier moyen échangeur de chaleur (12) comportant une partie (12A) chauffée extérieurement et une partie (12B) refroidie extérieurement, des chambres de compression et de détente raccordées au premier moyen échangeur de chaleur (12), des moyens à pistons (10, 11) destinés à diminuer le volume de l'une des chambres tout en augmentant le volume de l'autre chambre, et une première quantité de gaz confinée aux chambres de compression et de détente et au moyen échangeur de chaleur, comprenant les étapes qui consistent
a) à confiner une seconde quantité de gaz dans un second moyen échangeur de chaleur (13) comportant une partie chauffée extérieurement (13A) et une partie refroidie extérieurement (13B),
b) à raccorder la partie chauffée extérieurement (13A) du second moyen échangeur de chaleur (13) à la chambre de détente tout en raccordant la partie refroidie extérieurement (12B) du premier moyen échangeur de chaleur (12) à la chambre de compression durant un premier temps de travail des moyens à pistons,
c) à raccorder les parties chauffée et refroidie extérieurement (13A, 13B) du second moyen échangeur de chaleur (13) aux chambres de détente et de compression, respectivement, pendant un temps de retour des moyens à pistons,
d) à raccorder la partie chauffée extérieurement (12A) du premier moyen échangeur de chaleur (12) à la chambre de détente tout en raccordant la partie refroidie extérieurement (13B) du second moyen échangeur de chaleur (13) à la chambre de compression durant un second temps de travail des moyens à pistons, et
e) à raccorder les parties chauffée et refroidie (12A, 12B) du premier moyen échangeur de chaleur (12) aux chambres de détente et de compression, respectivement, durant un autre temps de retour des moyens à pistons avant de répéter de nouveau le premier temps de travail,
de manière que les deux quantités séparées de gaz occupent en alternance les chambres de compression et de détente sans mélange notable.
2. Procédé selon la revendication 1, dans lequel des moyens régénérateurs (14; 23A, 23B) sont intercalés en série entre les moyens échangeurs de chaleur chauffés extérieurement (12A, 13A) et les moyens échangeurs de chaleur refroidis extérieurement (12B, 13B) dans chacun desdits ensembles échangeurs de chaleur (12, 13).
3. Procédé selon la revendication 1 ou 2, dans lequel des moyens régénérateurs (14A, 14B) sont intercalés en série entre lesdits moyens échangeurs de chaleur chauffés extérieurement (12A, 13A) et des moyens à soupapes (16A, 17A) à l'extrémité chauffée extérieurement de chacun desdits ensembles échangeurs de chaleur (12, 13).
4. Procédé selon la revendication 1, 2 ou 3, dans lequel l'écoulement du gaz dans l'étape (c) est acheminé par un conduit séparé (21) en dérivation avec les moyens échangeurs de chaleur (13A), apportant de la chaleur, dudit second ensemble échangeur de chaleur (13), et l'écoulement du gaz dans l'étape (e) est acheminé par un conduit séparé (20) en dérivation avec le moyen échangeur de chaleur (12A), apportant de la chaleur, dudit premier ensemble échangeur de chaleur (12).
5. Procédé selon l'une quelconque des revendications 1 à 4, dans lequel plusieurs secondes quantités de gaz sont confinées dans un nombre correspondant de seconds moyens échangeurs de chaleur.
6. Machine du type à cycle de Stirling, conçue en particulier pour mettre en oeuvre le procédé selon l'une quelconque des revendications 1 à 5, comprenant des chambres de compression et de détente, des moyens à pistons (10, 11) destinés à diminuer l'espace de l'une des chambres et à augmenter simultanément l'espace de l'autre chambre, un moyen échangeur de chaleur (12) comprenant un espace chauffé extérieurement (12A) raccordé à un espace refroidi extérieurement (12B), l'espace chauffé extérieurement étant raccordé à la chambre de détente et l'espace refroidi extérieurement étant raccordé à la chambre de compression, et une quantité de gaz compressible sensiblement confinée de façon à circuler à travers les chambres et le moyen échangeur de chaleur (12), un second ensemble échangeur de chaleur (13) comprenant un espace chauffé extérieurement (13A) raccordé à un espace refroidi extérieurement (13B), l'espace chauffé extérieurement (13A) étant raccordé à la chambre de détente et l'espace refroidi extérieurement (13B) étant raccordé à la chambre de compression, une seconde quantité de gaz compressible sensiblement confinée de façon à circuler à travers les chambres et ledit second ensemble échangeur de chaleur (13), et des moyens de commande (16A, 17A, 18A, 19A) destinés à mettre en communication l'espace chauffé extérieurement (13A) du second moyen échangeur de chaleur cité (13) avec la chambre de détente tout en mettant en communication l'espace refroidi extérieurement (12B) dudit premier ensemble échangeur de chaleur (12) avec la chambre de compression et à mettre ensuite en communication l'espace chauffé extérieurement (12A) dudit premier ensemble échangeur de chaleur (12) avec la chambre de détente tout en mettant en communication l'espace refroidi extérieurement (13B) du second ensemble échangeur de chaleur (13) avec la chambre de compression, afin de constituer une machine capable de fonctionner en tant que moteur à gaz chaud et/ou en tant que pompe à chaleur pour un chauffage ou une réfrigération.
7. Machine selon la revendication 6, dans laquelle des moyens à soupapes séparés d'entrée et de sortie (16A, 20A; 17A, 21A) raccordent la chambre de détente à chacun des espaces chauffés extérieurement (12A, 13A) des ensembles échangeurs de chaleur (12,13), la soupape de sortie (20A, 21A) communiquant avec l'ensemble échangeur de chaleur (12, 13) entre les espaces chauffés extérieurement (12A, 13A) et refroidis extérieurement (12B, 13B).
8. Machine selon la revendication 7, dans laquelle un régénérateur (14A, 14B) est raccordé entre l'espace chauffé extérieurement (12A, 13A) de chaque ensemble échangeur de chaleur (12, 13) et les moyens à soupapes d'entrée (16A, 17A).
9. Machine selon la revendication 6, 7 ou 8, dans laquelle un régénérateur (14; 23A, 23B) est intercalé en série entre les espaces chauffés extérieurement (12A, 13A) et les espaces refroidis extérieurement (12B, 13B) dans chacun desdits ensembles échangeurs de chaleur (12, 13).
10. Machine selon l'une quelconque des revendications 6 à 9, dans laquelle sont prévus plusieurs seconds ensembles échangeurs de chaleur et un nombre correspondant de quantités de gaz compressible.
EP19840904048 1983-11-02 1984-10-29 Moteur a cycle stirling et pompe thermique Expired EP0162868B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84904048T ATE43680T1 (de) 1983-11-02 1984-10-29 Stirlingmotor und waermepumpe.

Applications Claiming Priority (2)

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US54819883A 1983-11-02 1983-11-02
US548198 1983-11-02

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EP0162868A1 EP0162868A1 (fr) 1985-12-04
EP0162868A4 EP0162868A4 (fr) 1986-08-21
EP0162868B1 true EP0162868B1 (fr) 1989-05-31

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EP (1) EP0162868B1 (fr)
JP (1) JPH071028B2 (fr)
DE (1) DE3478486D1 (fr)
WO (1) WO1985001988A1 (fr)

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JP4520527B2 (ja) * 2009-01-19 2010-08-04 横浜製機株式会社 外燃式クローズドサイクル熱機関
JP5317942B2 (ja) * 2009-12-07 2013-10-16 横浜製機株式会社 外燃式クローズドサイクル熱機関
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WO2011151888A1 (fr) * 2010-06-01 2011-12-08 横浜製機株式会社 Moteur thermique à combustion externe et à cycle fermé
JP5525371B2 (ja) * 2010-08-02 2014-06-18 横浜製機株式会社 外燃式クローズドサイクル熱機関
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WO2021104398A1 (fr) * 2019-11-29 2021-06-03 钟学斌 Appareil moteur, procédé de travail, et ensemble turbine hydraulique

Also Published As

Publication number Publication date
EP0162868A4 (fr) 1986-08-21
JPS61500272A (ja) 1986-02-20
JPH071028B2 (ja) 1995-01-11
DE3478486D1 (en) 1989-07-06
EP0162868A1 (fr) 1985-12-04
WO1985001988A1 (fr) 1985-05-09

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