CN114688755A - Heat-driven Stirling refrigerating system - Google Patents

Heat-driven Stirling refrigerating system Download PDF

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Publication number
CN114688755A
CN114688755A CN202011578281.0A CN202011578281A CN114688755A CN 114688755 A CN114688755 A CN 114688755A CN 202011578281 A CN202011578281 A CN 202011578281A CN 114688755 A CN114688755 A CN 114688755A
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China
Prior art keywords
piston
phasing
engine
refrigerator
cylinder
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CN202011578281.0A
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Chinese (zh)
Inventor
胡剑英
王日颖
张丽敏
孙岩雷
吴张华
陈燕燕
罗二仓
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Technical Institute of Physics and Chemistry of CAS
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Technical Institute of Physics and Chemistry of CAS
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Priority to CN202011578281.0A priority Critical patent/CN114688755A/en
Publication of CN114688755A publication Critical patent/CN114688755A/en
Pending legal-status Critical Current

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    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

The present invention provides a thermally driven stirling refrigeration system comprising: engine, refrigerator and coupling device, coupling device's both ends are connected with engine and refrigerator respectively, and coupling device includes: the two ends of the cylinder are respectively connected with the engine and the refrigerator; the first phase modulation piston assembly and the second phase modulation piston assembly are arranged in the cylinder and can reciprocate in the cylinder; wherein, form sealed cavity between first phase modulation piston assembly, the second phase modulation piston assembly and the cylinder, the gas in the sealed cavity can transmit the mechanical energy of first phase modulation piston assembly to the second phase modulation piston assembly. According to the heat-driven Stirling refrigeration system provided by the invention, the engine and the refrigerator are coupled by arranging the first phase modulation piston assembly and the second phase modulation piston assembly, so that the phase modulation range of the coupling device is enlarged, the performance of the Stirling refrigeration system is improved, the sensitivity of the Stirling refrigeration system to parameter change is reduced, and the Stirling refrigeration system can operate efficiently and relatively stably.

Description

Heat-driven Stirling refrigerating system
Technical Field
The invention relates to the technical field of refrigerators, in particular to a thermally driven Stirling refrigerating system.
Background
The Stirling heat engine is an energy conversion device with high efficiency, reliability and compact structure, and is widely applied to the fields of solar power generation, superconduction and the like. The stirling engine converts heat energy into mechanical energy, and the stirling cooler carries out heat transportation at the cost of mechanical energy consumption. Therefore, the Stirling engine can be used for driving the Stirling refrigerator, so that a heat-driven Stirling refrigerating system is formed.
In a conventional thermally driven stirling refrigeration system, a stirling engine is provided at one end, a stirling cooler is provided at the other end, and a resonant piston for coupling the engine and the cooler is provided in the middle. After a high-temperature end heat exchanger in the Stirling engine is heated, a certain temperature gradient exists in the heat regenerator, the system can generate self-oscillation, heat energy is converted into sound power, the sound power generated in the engine is transmitted to the Stirling refrigerator through the reciprocating motion of the resonant piston, and then most of the sound power is consumed in the heat regenerator of the refrigerator, so that heat is carried to a room-temperature end heat exchanger from the low-temperature end heat exchanger to achieve the refrigerating effect.
The existing heat-driven Stirling refrigeration system adopts a resonant piston for coupling, and pressure fluctuation and generated sound work on the engine side are transmitted to the refrigerator side through the reciprocating motion of the resonant piston. The area, the piston mass and the spring stiffness of the engine side and the refrigerator side of the resonant piston are adjusted to enable the engine and the refrigerator to obtain ideal sound field matching. Because the engine side end face and the refrigerator side end face of the resonant piston are fixedly connected together, the volume flows of the two end faces are in the same phase and fixed, and the size of the scavenging amount cannot be changed, so that the working condition of the system cannot be changed at will once the design is determined. When the heating temperature, the refrigerating temperature, the average pressure and the like slightly change, the displacement of the resonant piston can be greatly changed and is difficult to control, and even exceeds the allowable stroke, so that the whole system is difficult to stably operate.
Disclosure of Invention
The invention provides a thermally driven Stirling refrigeration system, which is used for solving the defect that the Stirling refrigeration system in the prior art is unstable in operation.
The present invention provides a thermally driven stirling refrigeration system comprising: the engine, refrigerator and coupling device, coupling device's both ends respectively with the engine with the refrigerator is connected, coupling device includes: the two ends of the cylinder are respectively connected with the engine and the refrigerator; a first phasing piston assembly and a second phasing piston assembly disposed within said cylinder and capable of reciprocating within said cylinder; and a sealed cavity is formed among the first phase modulation piston assembly, the second phase modulation piston assembly and the cylinder, and the gas in the sealed cavity can transfer the mechanical energy of the first phase modulation piston assembly to the second phase modulation piston assembly.
According to the present invention there is provided a thermally driven stirling refrigeration system, said first phasing piston assembly comprising: a first phasing piston and a first resilient member coupled to said first phasing piston; the second phasing piston assembly includes: a second phasing piston and a second resilient member connected to said second phasing piston; wherein the first phasing piston and the second phasing piston are reciprocable under pressure and the action of the first resilient member and the second resilient member.
According to the thermally driven stirling refrigeration system provided by the invention, the first phasing piston and the second phasing piston have different sectional areas, wherein the sectional area is the area of the section of the first phasing piston and the section of the second phasing piston which is perpendicular to the moving direction of the first phasing piston and the second phasing piston.
According to the heat-driven Stirling refrigeration system provided by the invention, the areas of the two opposite end surfaces of the first phase modulation piston are different, the areas of the two opposite end surfaces of the second phase modulation piston are different, and one of the two opposite end surfaces is connected with the first elastic piece or the second elastic piece.
According to the heat-driven Stirling refrigerating system provided by the invention, the heat-driven Stirling refrigerating system further comprises a third elastic element, and two ends of the third elastic element are respectively connected with the first phase modulation piston and the second phase modulation piston.
According to the thermally driven Stirling refrigeration system provided by the invention, the first elastic piece and the second elastic piece are mechanical springs.
According to the thermally driven Stirling refrigeration system provided by the invention, the first elastic piece and the second elastic piece are magnetic springs.
According to the heat-driven Stirling refrigeration system provided by the invention, the heat-driven Stirling refrigeration system further comprises an acoustoelectric conversion device, and the acoustoelectric conversion device is connected with the first phase modulation piston or the second phase modulation piston.
According to the present invention there is provided a thermally driven stirling refrigeration system, the engine comprising: an engine cylinder connected to the cylinder; the annular high-temperature end heat exchanger, the annular first heat regenerator and the annular first room-temperature end heat exchanger which are sequentially connected are arranged in the engine cylinder; the engine spring is arranged in the first room-temperature-end heat exchanger and is connected with the first room-temperature-end heat exchanger, and the engine spring is arranged close to the first phase modulation piston assembly; and the engine ejector is arranged in the engine cylinder, and one end of the engine ejector is connected with the engine spring.
According to the present invention there is provided a thermally driven stirling refrigeration system, the refrigerator comprising: the refrigerator cylinder is connected with the cylinder; the annular low-temperature end heat exchanger, the annular second heat regenerator and the annular second room-temperature end heat exchanger which are sequentially connected are arranged in the cylinder of the refrigerator; a refrigerator spring disposed within and connected to the second room-temperature-end heat exchanger, the refrigerator spring disposed adjacent to the second phasing piston assembly; and the refrigerator discharger is arranged in the refrigerator cylinder, and one end of the refrigerator discharger is connected with the refrigerator spring.
According to the heat-driven Stirling refrigeration system provided by the invention, the engine and the refrigerator are coupled by arranging the first phase modulation piston assembly and the second phase modulation piston assembly, so that the phase modulation range of the coupling device is enlarged, the performance of the Stirling refrigeration system is improved, the sensitivity of the Stirling refrigeration system to parameter change is reduced, and the Stirling refrigeration system can efficiently and relatively stably operate when the working condition is changed.
Drawings
In order to more clearly illustrate the technical solutions of the present invention or the prior art, the drawings needed for the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and those skilled in the art can also obtain other drawings according to the drawings without creative efforts.
FIG. 1 is a schematic diagram of a prior art thermally driven Stirling refrigeration system;
FIG. 2 is one of the schematic diagrams of the thermally driven Stirling refrigeration system provided by the present invention;
FIG. 3 is a second schematic diagram of a thermally driven Stirling refrigeration system according to the present invention;
reference numerals:
10: an engine; 11: a high temperature side heat exchanger; 12: a first heat regenerator;
13: a first room temperature end heat exchanger; 14: an engine spring; 15: an engine exhaust;
20: a refrigerator; 21: a low temperature side heat exchanger; 22: a second regenerator;
23: a second room temperature end heat exchanger; 24: a refrigerator spring; 25: a refrigerator ejector;
30: a resonant piston; 40: a coupling device; 41: a first phasing piston;
42: a first elastic member; 43: a second phasing piston; 44: a second elastic member;
45: an acoustoelectric conversion device.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The thermally driven stirling refrigeration system of the present invention is described below in conjunction with fig. 1 to 3.
As shown in fig. 1, a conventional thermally driven stirling cooler system includes an engine 10, a resonator device, and a cooler 20. The engine 10 includes: the engine comprises an engine cylinder, a high temperature end heat exchanger 11, a first regenerator 12, a first room temperature end heat exchanger 13, an engine spring 14 and an engine ejector 15. Specifically, the annular high-temperature-side heat exchanger 11, the annular first regenerator 12, and the annular first room-temperature-side heat exchanger 13 are connected in this order and disposed in the engine cylinder. The engine spring 14 is arranged in the first room temperature end heat exchanger 13 and connected with the first room temperature end heat exchanger 13, the engine ejector 15 is arranged in the engine cylinder, and one end of the engine ejector 15 is connected with the engine spring 14.
The refrigerator 20 includes: a refrigerator cylinder, a low temperature side heat exchanger 21, a second regenerator 22, a second room temperature side heat exchanger 23, a refrigerator spring 24, and a refrigerator ejector 25. Specifically, the annular low temperature side heat exchanger 21, the annular second regenerator 22, and the annular second room temperature side heat exchanger 23 are connected in this order and are disposed in the cylinder of the refrigerator. The refrigerator spring 24 is arranged on the second room temperature end heat exchanger 23 and connected with the second room temperature end heat exchanger 23, the refrigerator discharger 25 is arranged in the cylinder of the refrigerator, and one end of the refrigerator discharger 25 is connected with the refrigerator spring 24.
The resonance device comprises a cylinder and a resonance piston 30, the resonance piston 30 is arranged in the cylinder, and two ends of the cylinder are respectively connected with the engine cylinder and the refrigerator cylinder.
Specifically, the thermally driven stirling refrigerating system is coupled by the resonant piston 30, and pressure fluctuation on the engine side and generated acoustic power are transmitted to the refrigerator side by the reciprocating motion of the resonant piston 30. The engine 10 and the refrigerator 20 achieve ideal sound field matching by adjusting the area of the two sides of the resonant piston 30, the mass of the resonant piston 30, and the stiffness of the engine spring 14 and the refrigerator spring 24. Since the engine-side end face and the refrigerator-side end face of the resonant piston 30 are fixedly connected together, the volume flows of the two end faces are in phase and fixed, and the magnitude of the scavenging amount cannot be changed, so that the working condition of the system cannot be changed at will once the design is determined. When a heating temperature, a cooling temperature, an average pressure, etc. are slightly changed, the displacement of the resonant piston 30 is largely changed and is difficult to control, and even exceeds an allowable stroke, so that the entire system is difficult to stably operate.
According to thermoacoustic theory, a stirling refrigeration system is capable of achieving ideal energy conversion when the phase difference between the pressure and the volumetric flow rate in the first regenerator 12 of the stirling engine 10 is close to 0 °. Thus, to achieve the desired phase in the first recuperator 12 of the engine 10, the high-temperature side heat exchanger 11 and the first room-temperature side heat exchanger 13 in the engine 10 should be set such that one of the pressure phases leads the volume flow rate phase and the other lags the volume flow rate phase. The same is true for the refrigerator 20. The changes in pressure and volumetric flow rate in chiller 20 are primarily affected by coupling device 40 between engine 10 and chiller 20, so to optimize system performance, a high efficiency coupling between engine 10 and chiller 20 should be achieved.
As shown in fig. 2 and 3, an embodiment of the present invention provides a thermally driven stirling refrigeration system, comprising: engine 10, refrigerator 20, and coupling device 40. Both ends of coupling device 40 are connected to engine 10 and refrigerator 20, respectively. Wherein the coupling means 40 comprise: the cylinder, first phase modulation piston assembly and second phase modulation piston assembly, the both ends of cylinder are connected with engine cylinder and refrigerator cylinder respectively, first phase modulation piston assembly and second phase modulation piston assembly set up in the cylinder to can be at reciprocating motion in the cylinder, form seal chamber between first phase modulation piston assembly, the second phase modulation piston assembly and the cylinder, gas in the seal chamber can transmit first phase modulation piston assembly's mechanical energy for second phase modulation piston assembly.
Specifically, when the high-temperature-side heat exchanger 11 and the first room-temperature-side heat exchanger 13 of the engine 10 are heated, a temperature gradient exists in the first heat regenerator 12 of the engine 10, the stirling refrigeration system generates self-oscillation, so that heat is converted into sound work, certain pressure fluctuation is generated, and the first phase modulation piston assembly starts to reciprocate under the combined action of pressure and self acting force. Pressure fluctuations may also be generated in the cylinder due to the movement of the first phasing piston assembly. Similarly, the combined action of the pressure and the second phasing piston assembly causes the second phasing piston assembly to reciprocate, causing certain pressure fluctuations within the chiller cylinder, thereby transferring the acoustic work generated in the engine 10 to the chiller 20. The second regenerator 22 consumes most of the acoustic work to carry heat from the second room-temperature-side heat exchanger 23 to the low-temperature-side heat exchanger 21, thereby achieving a cooling effect.
In this embodiment, a two-piston phasing assembly design is used between the engine 10 and the refrigerator 20, and the two piston phasing assemblies are not fixedly connected together. The two phasing piston assemblies and the cylinder are sealed by gas, the gas is used as a gas spring and coacts with the two phasing piston assemblies to flexibly connect the two phasing piston assemblies together, so that the first phasing piston assembly can transmit sound work to the second phasing piston assembly through the gas spring. The displacements of the two phase modulation piston assemblies can be different, and certain phase difference can exist in the movement, so that the working volume change of the engine side and the working volume change of the refrigerator side are not limited to phase reversal only, but a reasonable phase difference can exist, the phase modulation range of the intermediate coupling device 40 is expanded, the engine 10 and the refrigerator 20 can obtain ideal sound field phases more easily, and the performance of the whole thermally driven Stirling refrigerating system is improved.
Most importantly: when the heating temperature, the refrigerating temperature and the average pressure change or the actual working condition deviates from the design values, the displacement and the phase difference of the two phase modulation piston assemblies can correspondingly change, so that a new energy balance state is achieved between the two phase modulation piston assemblies and the engine 10 and the refrigerating machine 20, the two phase modulation piston assemblies can stably work, the cylinder collision or shutdown condition is avoided, and the parameter sensitivity of the system can be greatly reduced compared with the traditional structure.
In particular, in one embodiment of the invention, the first phasing piston assembly and the second phasing piston assembly may alternatively be of the phasing piston and elastomeric member configuration.
According to the heat-driven Stirling refrigeration system provided by the embodiment of the invention, the engine and the refrigerator are coupled by arranging the first phase modulation piston assembly and the second phase modulation piston assembly, so that the phase modulation range of the coupling device is enlarged, the performance of the Stirling refrigeration system is improved, the sensitivity of the Stirling refrigeration system to parameter change is reduced, and the Stirling refrigeration system can efficiently and relatively stably operate when the working condition is changed.
As shown in fig. 2 and 3, in one embodiment of the present invention, a first phasing piston assembly comprises: a first phasing piston 41 and a first resilient member 42, wherein the first resilient member 42 is connected to the first phasing piston 41; the second phasing piston assembly includes: a second phasing piston 43 and a second resilient member 44, wherein the second resilient member 44 is connected to the second phasing piston 43.
In particular, the first phasing piston 41 and the second phasing piston 43 and the cylinder are sealed with gas therebetween, which acts as a gas spring to flexibly link the two phasing pistons together so that the first phasing piston 41 can transfer acoustic work to the second phasing piston 43 through the gas spring. Because the first phase modulation piston 41 and the second phase modulation piston 43 are flexibly connected through the gas spring, the displacements of the two phase modulation pistons can be different, and a certain phase difference can exist in the movement, so that the working volume change of the engine side and the working volume change of the refrigerator side are not limited to phase reversal only, but a reasonable phase difference can exist, the phase modulation range of the intermediate coupling device 40 is expanded, the engine 10 and the refrigerator 20 can obtain ideal sound field phases more easily, and the performance of the whole thermally driven Stirling refrigerating system is improved.
It should be noted that: the position, size and mass of the two phasing pistons and the rigidity of the elastic members connected with the phasing pistons can be changed according to design requirements.
Further, in an embodiment of the present invention, the cross sections of the first phase-modulating piston 41 and the second phase-modulating piston 43 perpendicular to the moving direction thereof may be equal or unequal, and when the cross sections are unequal, a more desirable sound field effect may be obtained. Further, the areas of the two end faces of the first phase-modulating piston 41 may be equal or unequal, and the areas of the two end faces of the second phase-modulating piston 43 may be equal or unequal, but when the areas of the two end faces are unequal, a more desirable sound field effect may be obtained. It should be noted that: a first elastic member 42 is attached to one of two end surfaces of the first phasing piston 41 which are opposed to each other, and a second elastic member 44 is attached to one of two end surfaces of the second phasing piston 43 which are opposed to each other.
Alternatively, as shown in fig. 2, in the present embodiment, the first phasing piston 41 and the second phasing piston 43 have different sectional areas in the cross section perpendicular to the direction of movement thereof, and the first phasing piston 41 and the second phasing piston 43 have different areas in the opposite end faces. Specifically, the opposing end surfaces of the first phasing piston 41 and the second phasing piston 43 are formed with grooves, respectively, in which the first elastic member 42 and the second elastic member 44 are disposed, respectively. The two elastic pieces are oppositely arranged, and each phase modulation piston can be independently positioned, so that the two phase modulation pistons are prevented from drifting, and the stability of the system is reduced. In one embodiment of the present invention, optionally, the first elastic member 42 and the second elastic member 44 are mechanical springs.
Alternatively, as shown in fig. 3, in the present embodiment, the first phasing piston 41 and the second phasing piston 43 have different sectional areas in a section perpendicular to the direction of movement thereof, the first elastic member 42 is connected to the first phasing piston 41, and the second elastic member 44 is connected to the second phasing piston 43.
Further, the first elastic member 42 and the second elastic member 44 are magnetic springs.
In particular, the first phasing piston 41 and the second phasing piston 43 can use the mutual attraction between the first elastic element 42 and the second elastic element 44 to control the movement of the two phasing pistons around the equilibrium position, so as to reduce the sensitivity of the system to parameter variations. Further, magnetic springs have a longer service life than mechanical springs.
It can be understood that: the first phasing piston 41 and the second phasing piston 43 may have other shapes, not limited to the shapes listed in the embodiments of the present invention, and the positions of the first elastic member 42 and the second elastic member 44 connected to the first phasing piston 41 and the second phasing piston 43, respectively, may be other positions, as long as the phasing pistons can be positioned.
In one embodiment of the present invention, the thermally driven stirling cooler system further comprises a third resilient member having opposite ends connected to the first phasing piston 41 and the second phasing piston 43, respectively, for transmitting acoustic work. Further, optionally, the third elastic member is a mechanical spring.
In one embodiment of the present invention, as shown in fig. 3, the thermally driven stirling refrigeration system further comprises an acousto-electric conversion device 45, the acousto-electric conversion device 45 being connectable to the first phasing piston 41 and to the second phasing piston 43. In one embodiment of the invention, optionally, an acousto-electric conversion device 45 is connected to the first phasing piston 41. Specifically, the sound-electricity conversion device 45 may convert a part of the sound power generated by the engine 10 into electric power, thereby implementing cooling power cogeneration or cooling power cogeneration.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.

Claims (10)

1. A thermally driven stirling refrigeration system comprising: the refrigerator comprises an engine, a refrigerator and a coupling device, wherein two ends of the coupling device are respectively connected with the engine and the refrigerator, and the coupling device comprises:
the two ends of the cylinder are respectively connected with the engine and the refrigerator;
a first phasing piston assembly and a second phasing piston assembly disposed within said cylinder and capable of reciprocating within said cylinder;
and a sealed cavity is formed among the first phase modulation piston assembly, the second phase modulation piston assembly and the cylinder, and the gas in the sealed cavity can transfer the mechanical energy of the first phase modulation piston assembly to the second phase modulation piston assembly.
2. A thermally driven Stirling refrigeration system according to claim 1,
the first phasing piston assembly includes: a first phasing piston and a first resilient member connected to said first phasing piston;
the second phasing piston assembly includes: a second phasing piston and a second resilient member connected to said second phasing piston;
wherein the first phasing piston and the second phasing piston are reciprocable under pressure and the action of the first resilient member and the second resilient member.
3. A thermally driven stirling refrigeration system according to claim 2 wherein the first phasing piston and the second phasing piston differ in cross-sectional area, wherein the cross-sectional area is the area of the cross-section of the first phasing piston and the second phasing piston perpendicular to the direction of movement of the first phasing piston and the second phasing piston.
4. A thermally driven stirling cooler system according to claim 3 wherein the first phasing piston has a different area of its opposite end faces and the second phasing piston has a different area of its opposite end faces, wherein one of the opposite end faces is connected to either the first or second resilient member.
5. A thermally driven stirling cooling system according to claim 2 further comprising a third resilient member, the third resilient member being connected at each end to the first phasing piston and the second phasing piston respectively.
6. A thermally driven stirling cooling system according to claim 5 wherein the first, second and third resilient members are mechanical springs.
7. A thermally driven stirling cooling system according to claim 2 wherein the first and second resilient members are magnetic springs.
8. A thermally driven stirling refrigeration system according to claim 7 further comprising an acousto-electric conversion device connected to either the first phasing piston or the second phasing piston.
9. A thermally driven stirling cooler in accordance with claim 1 wherein the engine comprises:
an engine cylinder connected with the cylinder;
the annular high-temperature end heat exchanger, the annular first heat regenerator and the annular first room-temperature end heat exchanger which are sequentially connected are arranged in the engine cylinder;
the engine spring is arranged in the first room-temperature-end heat exchanger and is connected with the first room-temperature-end heat exchanger, and the engine spring is arranged close to the first phase modulation piston assembly;
and the engine ejector is arranged in the engine cylinder, and one end of the engine ejector is connected with the engine spring.
10. A thermally driven stirling cooler according to claim 1, wherein the cooler comprises:
the refrigerator cylinder is connected with the cylinder;
the annular low-temperature end heat exchanger, the annular second heat regenerator and the annular second room-temperature end heat exchanger which are sequentially connected are arranged in the cylinder of the refrigerator;
the refrigerator spring is arranged in the second room-temperature-end heat exchanger and connected with the second room-temperature-end heat exchanger, and the refrigerator spring is arranged close to the second phase modulation piston assembly;
and the refrigerator discharger is arranged in the refrigerator cylinder, and one end of the refrigerator discharger is connected with the refrigerator spring.
CN202011578281.0A 2020-12-28 2020-12-28 Heat-driven Stirling refrigerating system Pending CN114688755A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202011578281.0A CN114688755A (en) 2020-12-28 2020-12-28 Heat-driven Stirling refrigerating system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202011578281.0A CN114688755A (en) 2020-12-28 2020-12-28 Heat-driven Stirling refrigerating system

Publications (1)

Publication Number Publication Date
CN114688755A true CN114688755A (en) 2022-07-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202011578281.0A Pending CN114688755A (en) 2020-12-28 2020-12-28 Heat-driven Stirling refrigerating system

Country Status (1)

Country Link
CN (1) CN114688755A (en)

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