Heat driven compressor and method of operating the same, and refrigeration and heating apparatus and method of operating the same

Abstract

A heat-driven compressor includes a compression assembly and a heat-powered device. The heat-powered device includes a high-temperature chamber, a high-temperature heat exchanger, a regenerator, a low-temperature heat exchanger, a low-temperature chamber, a discharge device, a piston, a transmission mechanism, a first elastic device sealing the chamber, a first elastic device for isolating the first elastic device sealing chamber from the working chamber, and an elastic device pressure differential regulating device. The high-temperature chamber, high-temperature heat exchanger, regenerator, low-temperature heat exchanger, and low-temperature chamber constitute the working chamber, which contains a first fluid. The compression assembly contains a second fluid. One end of the first elastic device is fixed, and the other end is connected to the piston. The piston, discharge device, and / or compression assembly are connected to the transmission mechanism. Its operation involves detecting the pressure differential across the elastic device. When the pressure differential exceeds a set value, a shutdown-protection device is first activated to reduce the pressure differential across the elastic device to the set value before restarting the heat-powered device. A refrigeration / heating device includes an evaporator, a condenser, an expansion device, and a heat-driven compressor.

Description

[0001] Cross-references to related applications

[0002] This application is based on and claims priority to Chinese Patent Application No. 202210927596.4, filed on August 3, 2022, entitled "Heat-Driven Compressor and Operating Method Thereof, Refrigeration and Heating Device and Operating Method Thereof", the full text of which is incorporated herein by reference as a part of this application. Technical Field

[0003] This invention relates to the fields of refrigeration and heat pump technology, and in particular to a heat-driven compressor and its operating method, and a refrigeration and heating device and its operating method. Background Technology

[0004] Vapor compression refrigeration is a widely used refrigeration technology in the refrigeration and heating fields. Its core component is the compressor, and currently, compressors in refrigeration and heating systems on the market almost entirely rely on electric motors. Because electricity undergoes multiple conversions and transmissions from production to use, this not only results in high operating costs for electrically driven compressors but also leads to energy waste and losses. Against this backdrop, the industry has proposed engine-driven refrigeration and heating systems. Since the mechanical work generated by an engine does not require the mechanical work-electricity-mechanical work conversion, and the waste heat generated by the engine can be used for applications such as home heating or hot water production, engine-driven refrigeration and heating systems have high energy efficiency, thus significantly reducing users' refrigeration and heating costs. Currently, internal combustion engine-driven refrigeration and heating systems have been widely used in large commercial and industrial systems. However, because domestic engine-driven compressor refrigeration and heating systems must meet requirements such as a lifespan of over 10 years, low noise, and maintenance-free operation for over 10 years, unlike commercial systems which require dedicated maintenance, internal combustion engines require maintenance every few tens of hours. This makes it difficult to meet these requirements, preventing the commercial application of engine-driven domestic refrigeration and heating systems.

[0005] Stirling engines possess the potential for low noise, maintenance-free operation, high efficiency, and long lifespan. Therefore, home refrigeration and heating systems driven by Stirling engines have excellent market prospects and significant economic benefits. Currently, there are various technical solutions for Stirling engine-driven home refrigeration and heating systems. On the one hand, Stirling engine-driven Stirling refrigerator solutions, such as the Vuilleumier machine and duplex Stirling machine, fall into this category. However, this solution suffers from high cost, low efficiency, and short lifespan. On the other hand, patent document (US3858802A) discloses a refrigeration and heating solution based on a Stirling engine-driven compressor. However, this patent is mainly based on a crank-connecting rod mechanism, which suffers from lifespan issues due to wear caused by lateral forces and the mixing of the engine working fluid and the refrigerant working fluid. Patent document (US4361008) discloses a solution based on a diaphragm and free-piston Stirling engine. However, hydraulic power transmission suffers from low efficiency, the diaphragm is difficult to meet lifespan requirements, and there are problems with the free-piston Stirling engine. The difficulty in frequency control is a significant concern. Patent document (US5383334) discloses a solution based on a bellows and a free-piston Stirling engine, but this suffers from problems such as a large compressor dead volume, difficulty in meeting bellows lifespan requirements, and low efficiency under varying operating conditions. Patent document (CN100376779C) discloses a solution with a fluid interconnection channel, but this suffers from problems such as mixing of the Stirling engine's working fluid (helium) with the compressor's working fluid (CO2), and difficulty in frequency control. Furthermore, published documents also report a refrigeration and heating scheme based on a magnetically coupled Stirling engine driving a compressor, but this suffers from low power transfer efficiency and high cost. Therefore, Stirling engine-driven refrigeration and heating systems have received relatively little attention and have not yet been practically applied. Summary of the Invention

[0006] The technical problem this invention aims to solve is to overcome the shortcomings of existing technologies and provide a low-noise, low-vibration, maintenance-free, easily frequency-adjustable heat-driven compressor that helps avoid cross-contamination of working fluids and achieves long lifespan and high efficiency. This invention further provides a method for operating the aforementioned heat-driven compressor. This invention further provides a refrigeration and heating device including the aforementioned heat-driven compressor.

[0007] To solve the above-mentioned technical problems, the present invention adopts the following technical solution:

[0008] A heat-driven compressor includes a compression assembly and a thermodynamic device. The thermodynamic device includes a high-temperature chamber, a high-temperature heat exchanger, a regenerator, a low-temperature heat exchanger, a low-temperature chamber, a discharge device, a piston, and a cylinder. The high-temperature chamber, the high-temperature heat exchanger, the regenerator, the low-temperature heat exchanger, and the low-temperature chamber constitute a working chamber containing a first fluid. The compression assembly contains a second fluid. The heat-driven compressor further includes a transmission mechanism, a first elastic device enclosed chamber containing a third fluid, a first elastic device for isolating the first elastic device enclosed chamber from the working chamber, and an elastic device differential pressure regulating device for adjusting the differential pressure of the first elastic device. One end of the first elastic device is fixed, and the other end is connected to the piston. The piston, the discharge device, and / or the compression assembly are connected to the transmission mechanism.

[0009] As a further improvement to the above technical solution: it also includes a second elastic device sealed cavity containing a third fluid, and a second elastic device for isolating the second elastic device sealed cavity from the working cavity. One end of the second elastic device is fixed, and the other end is connected to the discharge device. The first elastic device sealed cavity is in communication with the second elastic device sealed cavity. The elastic device differential pressure regulating device is connected to the second elastic device sealed cavity. And / or, it also includes a third elastic device sealed cavity containing a third fluid, and a third elastic device for isolating the third elastic device sealed cavity from the working cavity. One end of the third elastic device is fixed, and the other end is in a free state. The first elastic device sealed cavity is in communication with the third elastic device sealed cavity. The elastic device differential pressure regulating device is connected to the third elastic device sealed cavity.

[0010] The first, second, and third elastic devices are bellows or diaphragms, wherein the bellows are welded bellows or hydroformed bellows; when the bellows are hydroformed bellows, the ratio of the stroke of the piston or the discharger to the free length of the connected hydroformed bellows is 0.01 to 0.35; when the bellows are welded bellows, the ratio of the stroke of the piston or the discharger to the free length of the connected welded bellows is 0.1 to 0.6.

[0011] The first fluid is helium and / or hydrogen, the second fluid is carbon dioxide, ammonia, alkanes or Freon, and the third fluid is lubricating fluid or grease.

[0012] It also includes an electromagnetic device for driving the piston or discharger; or, the electromagnetic device for outputting electrical energy.

[0013] The compression assembly is a piston-type compression assembly, a rolling rotor-type compression assembly, or a scroll compression assembly; the compression assembly adopts a multi-stage compression structure or has an intermediate air inlet.

[0014] When the first elastic device is a bellows, the bellows has a guide rod inside, and the difference between the diameter of the guide rod and the inner diameter of the bellows is 0mm to 15mm.

[0015] The differential pressure regulating device for the elastic device includes a pump assembly and a control valve.

[0016] A heat-driven compressor includes a compression assembly and a thermal power device. The thermal power device includes a high-temperature chamber, a high-temperature heat exchanger, a regenerator, a low-temperature heat exchanger, a low-temperature chamber, a discharge device, a piston, and a cylinder. The high-temperature chamber, high-temperature heat exchanger, regenerator, low-temperature heat exchanger, and low-temperature chamber constitute a working chamber containing a first fluid. The compression assembly contains a second fluid. The heat-driven compressor includes a first elastic device enclosing a third fluid, a first elastic device for isolating the first elastic device enclosing the working chamber, and a spring for adjusting the pressure difference of the first elastic device. A pressure differential regulating device for a first elastic device, wherein one end of the first elastic device is fixed and the other end is connected to the piston; the second fluid is carbon dioxide and, at an ambient temperature of 305K and in a shutdown state, the pressure in the working chamber is ≥1 MPa, and the pressure in the compression assembly chamber where the compression component is located is ≥2 MPa; the second fluid is ammonia, alkanes, or Freon and, at an ambient temperature of 305K and in a shutdown state, the pressure in the working chamber is ≤2.5 MPa, and / or the pressure in the compression assembly chamber where the compression component is located is less than the saturation pressure of the second fluid at 305K.

[0017] A heat-driven compressor includes a compression assembly and a thermal power device. The thermal power device includes a high-temperature chamber, a high-temperature heat exchanger, a regenerator, a low-temperature heat exchanger, a low-temperature chamber, a discharge device, a piston, and a cylinder. The high-temperature chamber, high-temperature heat exchanger, regenerator, low-temperature heat exchanger, and low-temperature chamber constitute a working chamber containing a first fluid. The compression assembly contains a second fluid. The heat-driven compressor includes a first elastic device enclosed chamber containing a third fluid, a first elastic device for isolating the first elastic device enclosed chamber from the working chamber, and an elastic device differential pressure regulating device for regulating the pressure difference of the first elastic device. One end of the elastic device is fixed, and the other end is connected to the piston; the compression assembly has an intake pressure p1 and an exhaust pressure p2, the working chamber has an average pressure p3, and the pressure p inside the compression assembly chamber where the compression assembly is located is the pressure closest to p3 between p1 and p2; and / or, the compression assembly chamber where the compression assembly is located has a first buffer chamber, the piston passes through the first buffer chamber, the segment diameter of the piston located in the first buffer chamber is larger than the segment diameter of the piston located in the compression assembly chamber, and the pressure in the first buffer chamber is the intake pressure p1 or the exhaust pressure p2 of the compression assembly.

[0018] A heat-driven compressor includes a compression assembly and a thermodynamic device. The thermodynamic device includes a high-temperature chamber, a high-temperature heat exchanger, a regenerator, a low-temperature heat exchanger, a low-temperature chamber, a discharge device, a piston, and a cylinder. The high-temperature chamber, high-temperature heat exchanger, regenerator, low-temperature heat exchanger, and low-temperature chamber constitute a working chamber containing a first fluid. The compression assembly contains a second fluid. The heat-driven compressor includes a first elastic device enclosed by a third fluid, a first elastic device for isolating the first elastic device enclosed by the first elastic device from the working chamber, and an elastic device differential pressure regulating device for regulating the pressure difference of the first elastic device. One end of the first elastic device is fixed, and the other end is connected to the piston. The compression assembly has an unloading device for unloading the pressurization function of the compression assembly. The unloading device is a solenoid valve or an electromagnetic clutch.

[0019] A heat-driven compressor includes a compression assembly and a thermodynamic device. The thermodynamic device includes a high-temperature chamber, a high-temperature heat exchanger, a regenerator, a low-temperature heat exchanger, a low-temperature chamber, a discharge device, a piston, and a cylinder. The high-temperature chamber, high-temperature heat exchanger, regenerator, low-temperature heat exchanger, and low-temperature chamber constitute a working chamber containing a first fluid. The compression assembly contains a second fluid. The heat-driven compressor further includes a stop-start protection device, a first elastic device enclosed chamber containing a third fluid, a first elastic device for isolating the first elastic device enclosed chamber from the working chamber, and an elastic device differential pressure regulating device for regulating the pressure difference of the first elastic device. One end of the first elastic device is fixed, and the other end is connected to the piston. The stop-start protection device is used to maintain or balance the pressure difference of the elastic device in the stop state and to balance the pressure difference of the elastic device during the start-up process.

[0020] As a further improvement to the above technical solution: the shutdown-start protection device includes an active shutdown-start protection device and / or a passive shutdown-start protection device. The active shutdown-start protection device is used to adjust the pressure difference of the elastic device multiple times in a short period of time, and the passive shutdown-start protection device is used to maintain or balance the pressure difference of the elastic device for a long period of time. The compression assembly is located inside the compression assembly cavity, and the compression assembly cavity contains a second fluid and a third fluid. Wherein:

[0021] The active shutdown-start protection device has an electrically driven booster pump; and / or, the passive shutdown-start protection device has a fourth elastic device for isolating the working chamber and the compression assembly chamber, one end of the fourth elastic device being fixed and the other end being in a free state, the volume of the fourth elastic device in the free state being 0.5 to 100 times the scavenging volume of the exhaust device; and / or, the passive shutdown-start protection device has a fifth elastic device, the fifth elastic device isolating the compression assembly chamber and the working chamber, or the fifth elastic device isolating the compression assembly chamber and the compression chamber of the compression assembly; and / or, the passive shutdown-start protection device has a second buffer chamber, the second buffer chamber being located between the working chamber and the compression assembly chamber; and / or, the passive shutdown- The start-up protection device includes a pressure boosting and depressurization device, which has a pressure boosting and depressurization volume chamber and a compression mechanism, and adjusts the pressure inside the working chamber or the compression assembly chamber through the pressure boosting and depressurization volume chamber; and / or, the passive shutdown-start protection device includes a first solenoid valve and a second solenoid valve, the first solenoid valve being located at the inlet of the compression assembly and the second solenoid valve being located at the outlet of the compression assembly; and / or, the passive shutdown-start protection device is a gas-liquid separator with a volume ≥10L, such that the pressure inside the compression assembly chamber is less than the saturation pressure of the second fluid at 305K temperature under shutdown conditions and ambient temperature of 305K; and / or, the passive shutdown-start protection device includes a diaphragm protection device for protecting a diaphragm-based elastic device.

[0022] When the pressure boosting and depressurizing device is used to adjust the pressure of the working chamber, the compression mechanism has an intake valve and an exhaust valve, and the piston, the cylinder, the intake valve and the exhaust valve constitute the compression mechanism; or, the discharger, the cylinder, the intake valve and the exhaust valve constitute the compression mechanism.

[0023] The pressure boosting and depressurization device also has a fourth solenoid valve, which is used to unload the pumping function of the compression mechanism.

[0024] A heat-driven compressor includes a compression assembly and a thermodynamic device. The thermodynamic device includes a high-temperature chamber, a high-temperature heat exchanger, a regenerator, a low-temperature heat exchanger, a low-temperature chamber, a discharge device, a piston, and a cylinder. The high-temperature chamber, high-temperature heat exchanger, regenerator, low-temperature heat exchanger, and low-temperature chamber constitute a working chamber containing a first fluid. The compression assembly contains a second fluid. The heat-driven compressor includes a first elastic device enclosed chamber containing a third fluid, a first elastic device for isolating the first elastic device enclosed chamber from the working chamber, and an elastic device differential pressure regulating device for regulating the differential pressure of the first elastic device. One end of the first elastic device is fixed, and the other end is connected to the piston. The piston passes through the first elastic device enclosed chamber and through the cylinder with a clearance fit with the piston, extending into the compression assembly chamber where the compression assembly is located. The third fluid in the first elastic device enclosed chamber can leak through the clearance fit between the piston and the cylinder, and the clearance fit is located above the first elastic device enclosed chamber.

[0025] An operating method for the above-mentioned heat-driven compressor includes operating mode 1 or operating mode 2, wherein:

[0026] Operating Mode 1: First, detect the pressure difference borne by the elastic device. When the detected pressure difference borne by the elastic device is greater than the set value, first activate the shutdown-start protection device to reduce the pressure difference borne by the elastic device to the set value, and then start the thermal power device. When the detected pressure difference borne by the elastic device is less than the set value, the shutdown-start protection device can be activated first to further reduce the pressure difference borne by the elastic device before starting the thermal power device, or the thermal power device can be started directly.

[0027] Operating mode 2: Directly start the shutdown-start protection device, and then start the thermal power device.

[0028] A refrigeration and heating device includes an evaporator, a condenser, and an expansion device, and also includes the aforementioned heat-driven compressor. The high-temperature and high-pressure refrigerant compressed by the compression assembly flows into the condenser, and after passing through the condenser heat exchanger, it flows into the evaporator via the expansion device. After flowing out of the evaporator, the refrigerant flows back to the compression assembly.

[0029] As a further improvement to the above technical solution: under heating conditions, the difference between the average heat release temperature of the low-temperature heat exchanger and the condensation temperature of the condenser is ≥2.5℃.

[0030] It also includes a burner, a first flue gas waste heat exchanger, and a second flue gas waste heat exchanger, wherein the first flue gas waste heat exchanger and the second flue gas waste heat exchanger are used to recover the waste heat of the flue gas generated by the burner.

[0031] An operating method for the above-mentioned refrigeration and heating device, wherein an unloading device or an expansion device is controlled to achieve hot-cold mode operation and thermoelectric mode operation.

[0032] Compared with the prior art, the advantages of the present invention are as follows: The heat-driven compressor disclosed in the present invention achieves low noise by driving the compressor with a Stirling engine; the use of a first elastic device to isolate the working chamber of the Stirling engine and the compression assembly chamber can avoid mutual contamination between the working fluid of the engine and the working fluid of the compression assembly chamber, thus achieving long service life and high efficiency; by using an elastic device pressure difference adjustment device, the internal and external or upper and lower pressure differences of the elastic device during piston movement can be eliminated, thus achieving long service life, high reliability and maintenance-free operation; by using a transmission mechanism, low piston weight, low system vibration, high efficiency of power transmission between the engine and the piston, and long service life of the elastic device are achieved.

[0033] Furthermore, the use of lubricant or grease as the third fluid can significantly reduce friction and wear problems; by adopting a shutdown-start protection device, damage to the elastic device due to excessive pressure difference during shutdown and startup can be avoided, further improving service life, reliability and maintenance-free advantages.

[0034] The operating method of the heat-driven compressor disclosed in this invention detects the pressure difference borne by the elastic device and controls the shutdown-start protection device based on the pressure difference borne by the elastic device. This ensures that the pressure difference borne by the elastic device is small during startup, resulting in long life, high reliability, and maintenance-free operation. The refrigeration and heating device disclosed in this invention includes the aforementioned heat-driven compressor and therefore also possesses the above advantages. The operating method of the refrigeration and heating device disclosed in this invention, by controlling the third solenoid valve or expansion device, can achieve both hot-cold mode operation and thermoelectric mode operation, offering good flexibility, diverse functions, and simple operation. Attached Figure Description

[0035] Figure 1 This is a schematic diagram of the composition of the heat-driven compressor of the present invention.

[0036] Figure 2 This is a schematic diagram of the compression component in this invention.

[0037] Figure 3 This is a schematic diagram of the structure of a heat-driven compressor according to a first embodiment of the present invention.

[0038] Figure 4 This is a schematic diagram of the elastic device in this invention.

[0039] Figure 5 This is a schematic diagram of the structure of a second embodiment of the heat-driven compressor of the present invention.

[0040] Figure 6 This is a schematic diagram of the structure of Embodiment 3 of the heat-driven compressor of the present invention.

[0041] Figure 7 This is a schematic diagram of the structure of the multi-stage compression component in this invention.

[0042] Figure 8 This is a schematic diagram of the operation method of the heat-driven compressor of the present invention.

[0043] Figure 9 This is a schematic diagram of the cooling and heating device of the present invention.

[0044] The labels in the diagram represent: 1. High-temperature chamber; 2. High-temperature heat exchanger; 3. Regenerator; 4. Low-temperature heat exchanger; 5. Low-temperature chamber; 6. Discharge device; 7. Piston; 8. Cylinder; 91. First elastic device; 92. Second elastic device; 93. Third elastic device; 94. Fourth elastic device; 95. Fifth elastic device; 10. Elastic device differential pressure regulating device; 101. Pump assembly; 102. Control valve; 103. Check valve; 131. First elastic device closed chamber; 132. Second elastic device closed chamber; 133. Third elastic device closed chamber; 14. Compression assembly chamber; 15. Compression assembly; 151. First compression assembly; 152. Second compression assembly; 16. Transmission mechanism; 17. Thermodynamic device; 18. Electromagnetic device; 20. Active shutdown-start protection device. 21. Electric booster pump; 22. Passive shutdown-start protection device; 24. Buffer chamber; 241. First buffer chamber; 242. Second buffer chamber; 25. Condenser; 26. Evaporator; 27. Expansion device; 29. ​​Pressure boosting and depressurization device; 2901. Pressure boosting and depressurization volume chamber; 2902. Compression mechanism; 2903. Pressure boosting and depressurization control valve; 30. Four-way valve; 311. First medium heat exchanger; 312. Second medium heat exchanger; 32. Heat transfer medium pump; 33. Discharger; 34. Air supply valve; 351. First solenoid valve; 352. Second solenoid valve; 353. Third solenoid valve; 354. Fourth solenoid valve; 36. Burner; 37. First flue gas waste heat exchanger; 38. Second flue gas waste heat exchanger; 39. Diaphragm protection device; 40. Unloading device. Detailed Implementation

[0045] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0046] Example 1

[0047] like Figure 1As shown, a heat-driven compressor includes a compression assembly 15 and a thermodynamic device 17. The Stirling engine, as an external combustion engine, has the potential for low noise and long-term maintenance-free operation. Therefore, the thermodynamic device 17 in this invention is based on a Stirling engine. Specifically, the thermodynamic device 17 includes a high-temperature chamber 1, a high-temperature heat exchanger 2, a regenerator 3, a low-temperature heat exchanger 4, a low-temperature chamber 5, an exhaust device 6, a piston 7, and a cylinder 8. The high-temperature chamber 1, high-temperature heat exchanger 2, regenerator 3, low-temperature heat exchanger 4, and low-temperature chamber 5 constitute a working chamber. Under the reciprocating motion of the exhaust device 6, the working fluid in the working chamber is driven to flow alternately between the high-temperature chamber 1 and the low-temperature chamber 5, thereby generating alternating pressure within the working chamber, which drives the piston 7 to output mechanical work. The inventors of this application have discovered that the output mechanical work is transmitted to the compression assembly 15 through the piston 7 or a crankshaft, which has the advantage of the highest work transfer efficiency between the thermodynamic device 17 and the compression assembly 15. Therefore, the work coupling between the thermodynamic device 17 and the compression assembly 15 based on a piston or crankshaft has the advantage of high work transfer efficiency.

[0048] Stirling engines have two structures: free piston and crank-connecting rod. Free pistons are generally considered to offer low noise, long lifespan, high reliability, high efficiency, and maintenance-free operation. Theoretically, free piston Stirling engines are ideal thermal power sources for heat-driven compressors. However, the inventors of this application have discovered that: on the one hand, there is a work mismatch between the output work of the Stirling engine piston and the work demanded by the vapor compression system compressor during the cycle. This is mainly because the Stirling engine only performs work for half a cycle, while the compressor's intake process does very little work. Free piston Stirling engines require very heavy pistons to balance this work mismatch, resulting in large vibrations and noise, which can damage related system components. On the other hand, the frequency of free piston Stirling engines is almost non-adjustable, while refrigeration and heating devices typically require frequency conversion. Therefore, the thermal power device 17 in this invention is a Stirling engine based on a transmission mechanism 16. The transmission mechanism 16 can be a crank-connecting rod, Scottish yoke, or diamond drive, etc. By configuring a flywheel or balance weight on the transmission mechanism 16, the piston weight can be reduced to as low as 1-2 kg, and it has advantages such as low noise, low vibration, and adjustable frequency.

[0049] Furthermore, the inventors of this application have discovered that: on the one hand, for a Stirling engine based on a transmission mechanism, due to its rotational motion, there will inevitably be lateral forces, resulting in multiple frictions inside. Since there cannot be lubricating oil in a Stirling engine, the wear caused by dry friction between related components limits the lifespan of a Stirling engine based on a transmission mechanism to several hundred hours, making it unsuitable as a power unit for household refrigeration and heating systems that require an operating life of more than 10 years; on the other hand, the working fluid in the Stirling engine is different from the working fluid in the compression assembly 15 (different working fluids include different types of working fluids or different compositions of working fluids). The mixing of the working fluid in the Stirling engine and the working fluid in the compression assembly cavity 14 will not only reduce the performance of the Stirling engine, but also reduce the performance of the compression assembly 15, thereby reducing the energy-saving benefits of the heat-driven compressor. Therefore, this invention employs a combination of a third fluid and an elastic device. Preferably, the third fluid is a lubricating fluid or grease. Using the third fluid to lubricate relevant parts can significantly reduce friction and wear. The elastic device isolates the working fluid between the working chamber and the compression component chamber, preventing the third fluid from flowing into the working chamber and contaminating the heat exchanger and regenerator. It also prevents the mixing of the second and first fluids, improving system efficiency. Furthermore, the use of an elastic device for sealing further enhances system efficiency and ensures a long lifespan for the Stirling engine, guaranteeing over 10 years of maintenance-free and long-life operation for the sealing and friction components. Preferably, the elastic device can be a bellows or a diaphragm. Because diaphragms have a short stroke, they require a large diameter, resulting in a very heavy machine. Moreover, the inventors of this application have found that balancing the pressure difference across the diaphragm is difficult during shutdown and operation. Therefore, preferably, the elastic device is a bellows.

[0050] Furthermore, the thermal power unit 17 can be an alpha, beta, or gamma type Stirling engine.

[0051] Since this solution employs a transmission mechanism 16, the compression assembly 15 can be a piston-type compression assembly, a rolling rotor-type compression assembly, or a scroll-type compression assembly, etc. Figure 2 As shown in Figure a, the piston compression assembly 15 includes a piston compression assembly cylinder 1502, a piston compression assembly piston 1501, an intake valve 1503, and an exhaust valve 1504; as Figure 2 As shown in b, the rolling rotor compression assembly 15 includes an upper flange 1502a, a rolling rotor compression assembly cylinder 1502b, a lower flange 1502c, a crankshaft 1501a, rollers 1501b, a vane 1501c, a spring 1501d, and an exhaust valve 1503; Figure 2 As shown in Figure c, the scroll compressor assembly 15 includes a stationary scroll plate 1501e, a moving scroll plate 1501f, and a crankshaft 1501a. In addition, the scroll compressor assembly 15 may be equipped with an exhaust valve as needed.

[0052] Figure 3 a illustrates a heat-driven compressor based on a rotary compression assembly. For example... Figure 3 As shown in b, the compression assembly 15 and the transmission mechanism 16 share a crankshaft. The transmission mechanism 16 is connected to the piston 7, and the mechanical work output by the piston 7 is transmitted to the compression assembly 15 through the crankshaft. Figure 3 c illustrates a heat-driven compressor based on a linear piston compression assembly, wherein compression assembly 15 is a piston compression assembly.

[0053] Furthermore, the first elastic device 91 and the cylinder form the first elastic device closed cavity 131.

[0054] like Figure 4 As shown, the elastic device can be a diaphragm or a bellows, and the material can be rubber or metal. Since rubber is subject to aging, the elastic device material is preferably metal. When the elastic device is a metal bellows, the metal bellows can be a welded bellows, a hydroformed bellows, or an electrodeposited bellows. The metal bellows structure can be S-shaped, V-shaped, Ω-shaped, or U-shaped, etc. Preferably, the metal bellows is a welded bellows or a hydroformed bellows. Figure 4 a and Figure 4 b shows two types of bellows structures. Figure 4 'a' is V-shaped. Figure 4 b is S-shaped. Figure 4 b is a welded corrugated pipe with welds on both the inside and outside. Figure 4 c and Figure 4 Figure d illustrates two structures of metal diaphragms. Further, to meet the requirement of a lifespan of over 10 years for heat-driven compressors, the inventors of this application have discovered that: when the bellows is a hydroformed bellows, the optimal range for the ratio of the piston or discharger stroke to the free length of the connected hydroformed bellows is 0.01 to 0.35; when the bellows is a welded bellows, the optimal range for the ratio of the piston or discharger stroke to the free length of the connected welded bellows is 0.1 to 0.6. Here, the piston stroke refers to the distance the piston travels from top dead center to bottom dead center, and the discharger stroke is similarly defined. Further, the bellows thickness is between 0.05 mm and 1 mm, preferably between 0.1 mm and 0.3 mm.

[0055] Furthermore, the working fluid in the working chamber is a first fluid, which can be helium, hydrogen, air, etc. Preferably, the first fluid is helium, hydrogen, or a mixture of helium and hydrogen. The compression assembly chamber 14 has a second fluid and a third fluid. The second fluid can be CO2, ammonia, Freon (such as R32, R1234yf, R410A), or alkanes (such as propane, butane), etc., serving as the working fluid of the compression assembly 15. The third fluid is a lubricating fluid or grease, etc. The first fluid, the second fluid, and the third fluid are isolated from each other by a first elastic device 91.

[0056] Furthermore, such as Figure 3 As shown, the compression assembly 15 or the transmission mechanism 16 is also connected to the electromagnetic device 18 to output or input electrical power. Preferably, the electromagnetic device 18 is an integrated motor-generator unit.

[0057] Furthermore, such as Figure 3 As shown, the heat-driven compressor also includes a gas-liquid separator 28 for gas-liquid separation at the working fluid inlet of the compression assembly 15.

[0058] Furthermore, the inventors of this application discovered that the average pressure of the working fluid in a Stirling engine is less affected by operating conditions and has a smaller range of variation. Therefore, the range of operating pressure variation of the working fluid in a Stirling engine depends on the design and can be designed to be very small or even zero. However, the pressure of the working fluid in the compressor chamber is affected by operating conditions and will fluctuate significantly. For example, the condensing pressure of an R32 heat pump system varies between 1.5 and 5 MPa, and the evaporating pressure of a CO2 refrigeration system varies between 1 and 5 MPa. Therefore, although the operating pressure variation of the working fluid in a Stirling engine can be designed to be very small, such a large pressure variation on the compressor side can easily cause a pressure difference of several MPa in the elastic device, resulting in a force of several thousand or even tens of thousands of Newtons. For example, when the elastic device is a bellows, the pressure difference inside and outside the bellows will generate stress inside the bellows; when the elastic device is a diaphragm, the pressure difference above and below or left and right of the diaphragm will generate stress inside the diaphragm. These stresses will significantly reduce the life of the elastic device, resulting in a life of only tens of hours. Therefore, this invention further employs an elastic device differential pressure regulating device 10 to ensure that the internal and external or vertical differential pressure of the elastic device is close to zero under any refrigeration or heating conditions during the operation of the heat-driven compressor, thereby supporting the heat-driven compressor's service life of more than 10 years. Furthermore, the elastic device differential pressure regulating device 10 includes a pump assembly 101 for pressurizing a second or third fluid and a control valve 102. The power source for the pump assembly 101 can be a piston 7 or an electric motor. Figure 5 The power source for the pump assembly 101 in section a is driven by an electric motor. Figure 5The power source for pump assembly 101 in step b is piston 7. Preferably, the power source for pump assembly 101 is piston 7, which pressurizes the second or third fluid to a high pressure and injects it into the closed cavity 131 of the first elastic device, thereby ensuring that the first elastic device 91 withstands a small pressure difference. Preferably, the fluid pumped into the closed cavity 131 of the first elastic device is the third fluid. Control valve 102 can be an electrically controlled valve or an adaptive valve; preferably, control valve 102 is an adaptive valve.

[0059] Furthermore, the inventors of this application discovered that for the heat-driven compressor based on elastic devices of the present invention, the pressure difference borne by the elastic device in the shutdown state is crucial for the long-term operation of the elastic device. However, the pressure fluctuation of the compression assembly cavity 14 is large due to the influence of operating conditions. In order to meet the long-term requirements of the elastic device, thicker and / or longer elastic devices are needed, thereby increasing cost and dead volume and reducing the target life value. When the second fluid is not carbon dioxide, but ammonia, alkanes, or Freon, the pressure in the working cavity under the 305K ambient temperature and shutdown state is ≤2.5MPa, preferably 0.5MPa to 2MPa. The pressure in the compression assembly cavity 14 depends on the fluid. For example, if the second fluid is R32, the saturation pressure at 305K ambient temperature is 2.02MPa. Therefore, the pressure in the compression assembly cavity 14 needs to be less than the saturation pressure of the second fluid at 305K. If the second fluid is propane, the saturation pressure at 305K ambient temperature is only 1.129MPa. In this case, the pressure in the compression assembly cavity 14 can be equal to the saturation pressure of the second fluid at 305K.

[0060] When the second fluid is carbon dioxide, the pressure inside the working chamber is ≥1 MPa at an ambient temperature of 305 K and under shutdown conditions, and the pressure inside the compression assembly chamber 14 is ≥2 MPa. These constraints ensure that the pressure difference experienced by the elastic device under shutdown conditions remains within acceptable limits. It should be noted that when the second fluid is a mixed refrigerant containing carbon dioxide, if the carbon dioxide content is less than 50%, it should not be considered as carbon dioxide. Furthermore, it should be emphasized that the pressure range inside the compression assembly chamber 14 is not limited to independent heat-driven compressors, but also includes heat-driven compressors in refrigeration and heating devices that combine condensers and evaporators.

[0061] Furthermore, to protect the bellows from pressure damage, when the second fluid is not carbon dioxide and the first elastic device 91 is a bellows, the outer surface of the bellows of the first elastic device 91 contacts the first fluid, and the inner surface of the bellows contacts the third fluid, such as... Figure 3 As shown in d;

[0062] When the second fluid is carbon dioxide and the first elastic device 91 is a bellows, the outer surface of the bellows of the first elastic device 91 contacts the third fluid, and the inner surface of the bellows contacts the first fluid, such as... Figure 3 As shown in c.

[0063] Furthermore, when the first elastic device 91 is a bellows, the bellows has a guide rod inside. The difference between the diameter of the guide rod and the inner diameter of the bellows is 0mm to 15mm, preferably 0.5mm to 2mm. By setting the guide rod, it is beneficial to make the bellows extend and retract in a set direction and to ensure the shape of the bellows. The difference between the diameter of the guide rod and the inner diameter of the bellows is 0mm to 15mm to prevent the bellows from becoming unstable.

[0064] Similarly, when the second elastic device 92 and the third elastic device 93 are made of bellows, the bellows also have guide rods inside.

[0065] For bellows connected to a piston, the piston can serve as a guide rod; for bellows connected to a discharger, the discharger's connecting rod can serve as a guide rod. Furthermore, the valve stem of an adaptive valve can also serve as a guide rod.

[0066] Furthermore, as described above, the inventors of this application discovered that a work mismatch exists during the cycle between the output power of the Stirling engine piston and the required power of the vapor compression system compressor. Therefore, to reduce vibration, noise, and the mass of the balance block or flywheel, in this invention: the compression assembly 15 has an intake pressure p1 and an exhaust pressure p2, the working chamber has an average pressure p3, and the pressure p within the compression assembly cavity 14 where the compression assembly 15 is located is the pressure closest to p3 between p1 and p2. For example, when p1 is close to p3, the compression assembly cavity 14 can be connected to the compressor intake port, thereby achieving a pressure p within the compression assembly cavity 14 that is p1; when p2 is close to p3, the compression assembly cavity 14 can be connected to the compressor exhaust port, thereby achieving a pressure p within the compression assembly cavity 14 that is p2. When the second fluid is not carbon dioxide (such as ammonia, alkanes, or Freon), the intake pressure p1 is the saturation pressure of the second fluid at 0°C, and the exhaust pressure p2 is the saturation pressure of the second fluid at 35°C. Preferably, when the second fluid is not carbon dioxide, the compression assembly chamber 14 is connected to the exhaust port of the compression assembly 15, such as... Figure 3 As shown in Figure c, when the second fluid is carbon dioxide, the pressure needs to be determined based on the exhaust pressure. Preferably, the compression assembly chamber 14 is connected to the intake port of the compression assembly 15. Figure 3 d illustrates a structure in which the compression assembly cavity 14 is connected to the intake port of the compression assembly 15, and the connection is controlled by an electronically controlled valve; and / or, the compression assembly cavity 14 has a first buffer cavity 241, such as Figure 3 As shown in Figure e, piston 7 passes through the first buffer chamber 241 and is connected to the compression assembly 15. The pressure inside the first buffer chamber 241 is either the intake pressure p1 or the exhaust pressure p2 of the compression assembly 15. Preferably, the pressure p inside the first buffer chamber 241 is the pressure closest to p3 between p1 and p2. Figure 3e illustrates a structural design in which the first buffer chamber 241 is connected to the exhaust port of the compression assembly 15, therefore... Figure 3 In equation e, the pressure p inside the first buffer chamber 241 is the exhaust pressure p2 of the compression assembly 15. In this case, the pressure inside the compression assembly chamber 14 can be the intake pressure, reducing the pressure inside the compression assembly chamber 14. Moreover, the segment diameter of the piston 7 located in the first buffer chamber 241 is larger than the segment diameter of the piston 7 located in the compression assembly chamber 14. Figure 3 As shown in Figure e, the first buffer chamber 241 is located between the first elastic device closed chamber 131 and the compression component chamber 14, and the segment diameter of the piston 7 in the first buffer chamber 241 is larger than the segment diameter of the piston 7 located in the compression component chamber 14.

[0067] Furthermore, as described above, the piston 7 passes through the closed cavity 131 of the first elastic device and through the cylinder 8 which is clearance-fitted with the piston 7, extending into the compression assembly cavity 14 where the compression assembly 15 is located. Due to the clearance fit between the piston 7 and the cylinder 8, the third fluid in the closed cavity 131 of the first elastic device will leak through the clearance fit between the piston 7 and the cylinder 8. During operation, the third fluid leaking through the clearance fit can be replenished by the elastic device differential pressure regulating device 10. The inventors of this application have discovered that: because the heat-driven compressor is a refrigeration and heating device, its application requirements lead to frequent start-up and shutdown. If the clearance fit is located downwards, the third fluid will leak from the clearance fit under the action of gravity when the machine is stopped, making it difficult for the lifespan of the first elastic device 91 to meet the long lifespan requirements. Furthermore, when the second fluid is a refrigerant, it partially dissolves in the third fluid, causing gaseous second fluid to be released within the sealed cavity 131 of the first elastic device. If the clearance fit is positioned downwards, this gaseous second fluid easily accumulates at the top of the sealed cavity 131 and cannot be released from the clearance fit, thus making it difficult for the first elastic device 91 to meet long-life requirements. Therefore, in this invention, to protect the first elastic device 91 for long-life operation, Figure 3 The arrow pointing to the semi-solid part extending into the closed cavity 131 of the first elastic device indicates the location of the clearance fit between the piston 7 and the cylinder 8. Therefore, the clearance fit is located above the position of the closed cavity 131 of the first elastic device, and is not required to be perfectly perpendicular. The largest arrow in the figure indicates the direction of gravitational acceleration. Therefore, gravity will not drive the third fluid in the closed cavity 131 of the first elastic device to flow out from the clearance fit. If a gaseous second fluid forms in the closed cavity 131 of the first elastic device, the gaseous second fluid will accumulate near the end of the clearance fit due to its density and escape from the clearance fit. Furthermore, Figure 5 The position of the gap between the discharge device 6 and the cylinder 8 in c is also above the position of the second elastic device closed cavity 132.

[0068] Example 2

[0069] Furthermore, the heat-driven compressor also includes a second elastic device 92, which is a metal bellows, with one end connected to the discharge device 6 and the other end fixed, or alternatively connected to the piston 7. For example... Figure 5 As shown in Figure c, one end of the second elastic device 92 is connected to the discharge device 6, and the other end is fixed. Preferably, the second elastic device closed cavity 132 formed by the second elastic device 92 can communicate with the third elastic device closed cavity 133 to reduce the pressure difference caused by the volume change during the movement of the discharge device 6.

[0070] Furthermore, the heat-driven compressor also has a third elastic device 93 and a third elastic device enclosed cavity 133, such as Figure 5 As shown, the third elastic device 93 is fixed at one end and free at the other. To prevent the second fluid from entering the working chamber, the free end is closed. The closed end can be a flat plate or a diaphragm, preferably, as shown in the figure. Figure 4 As shown in Figure e, the closed end is a diaphragm. The closed cavity 133 of the third elastic device is connected to the closed cavity 131 of the first elastic device. The third elastic device 93 can be used to compensate for the volume change of the closed cavity 131 of the first elastic device caused by the movement of the first elastic device 91 with the piston 7, and to balance the pressure difference borne by the first elastic device 91. Figure 5 A further illustration shows an adaptive control valve 102 with a valve stem, one end of which is connected to a third elastic device 93, while the other end is free. When the pressure in the working chamber is higher than the pressure inside the closed cavity 133 of the third elastic device, the third elastic device 93 is compressed, and the valve stem moves downward under the action of the third elastic device 93. This connects the closed cavity 133 of the third elastic device to the pump assembly 101, allowing a third fluid to be pumped into the closed cavity 133. The third elastic device 93 then gradually elongates, and the valve stem of the adaptive control valve 102 moves upward under the action of the third elastic device 93. When the volume of the third elastic device 93 increases to a certain value, the connection between the closed cavity 133 of the third elastic device and the pump assembly 101 is broken. To prevent backflow of the third fluid, a check valve 103 is installed on the pipeline between the control valve 102 and the pump assembly 101.

[0071] Furthermore, the compression assembly 15 is a multi-stage compression structure or has an intermediate air inlet. For piston-type or rolling rotor-type compression assemblies, such as Figure 7 As shown, the compression assembly 15 includes a first compression assembly 151 and a second compression assembly 152. The first compression assembly 151 has an inlet a and an exhaust port b, and the second compression assembly 152 has an inlet c and an exhaust port d. It also has a make-up air port e, which is located on the pipeline between the exhaust port b of the first compression assembly 151 and the inlet c of the second compression assembly 152. For a scroll compressor assembly, there is an intermediate make-up air port on the scroll plate.

[0072] Furthermore, the inventors of this application have discovered that a home energy system has multiple energy input or output requirements. Although the present invention uses a thermodynamic device piston to directly drive the compression assembly piston or a thermodynamic device to drive a transmission mechanism to drive the compression assembly, it still possesses multi-functional potential. Therefore, the compression assembly 15 described in this invention has an unloading device 40 with unloading compression or pressurization functions. The unloading device 40 can be a solenoid valve or an electromagnetic clutch, etc. Figure 6 As shown in diagram i, the unloading device is the third solenoid valve 353. When the third solenoid valve 353 is open, the compression chamber of the compression assembly 15 is connected to the outside. Although the compression assembly 15 draws in and exhausts air, it does not generate a pressurization function. When the third solenoid valve 353 is closed, the compression chamber of the compression assembly 15 is disconnected from the outside. The compression assembly 15 draws in and exhausts air, but generates a pressurization function. When the unloading device 40 is an electromagnetic clutch, one end of the unloading device 40 is connected to the output shaft of the thermodynamic device 17, and the other end is connected to the input shaft of the compression assembly 15. By energizing or de-energizing, the connection and disconnection between the thermodynamic device 17 and the compression assembly 15 can be controlled.

[0073] Example 3

[0074] On the one hand, the inventors of this application have discovered that the working fluid pressure in the compression assembly chamber fluctuates significantly due to the influence of ambient temperature or operating conditions; for example, the pressure variation range of a CO2 system in a non-operating state is between 1 and 7 MPa. On the other hand, the working fluid pressure in the thermodynamic device 17 exhibits very small fluctuations in a non-operating state, even approaching zero. Therefore, when the thermodynamic compressor is not operating, a very large pressure difference may exist between the working chamber and the compression assembly chamber, leading to enormous stress within the elastic device during shutdown or startup, damaging the elastic device and preventing it from meeting the requirements for a long service life. Therefore, the thermodynamic Stirling device of this invention also includes a shutdown-start protection device, which can balance the pressure difference within the elastic device during the shutdown state and / or startup process of the thermodynamic compressor.

[0075] The shutdown-start protection device is divided into active and passive shutdown-start protection devices. Preferably, the active shutdown-start protection device 20 can adjust the pressure difference of the elastic device multiple times in a short period of time based on electronic control. Preferably, the active shutdown-start protection device 20 can adjust the pressure difference of the elastic device multiple times within 1 day to 1 week. The passive shutdown-start protection device 22 can maintain or balance the pressure difference of the elastic device for a long time. Preferably, the passive shutdown-start protection device 22 can maintain the pressure difference of the elastic device for more than 1 week under constant ambient temperature, or can maintain the pressure difference of the elastic device for more than 1 week after balancing.

[0076] Furthermore, such as Figure 5 As shown in Figure a, the active shutdown-start protection device includes an electric booster pump, i.e., pump assembly 101 in the figure is an electric booster pump. In the shutdown state, when a large pressure difference is detected on the elastic device, the electric booster pump is activated to inject a third fluid into the closed cavity of the elastic device until the pressure difference reaches a set value, at which point the injection of the third fluid stops. Because the working fluid inside the closed cavity of the elastic device may leak through relevant seals, the pressure difference on the elastic device will gradually increase again in the shutdown state. At this time, the electric booster pump needs to replenish the third fluid in the closed cavity of the elastic device to maintain or balance the pressure difference. The frequency of replenishment depends on the leakage at the seals. Therefore, the active shutdown-start protection device has the following characteristics: when the pressure difference increases, the electric booster pump of the active shutdown-start protection device starts to balance the pressure difference; then the pressure difference increases again, and the electric booster pump of the active shutdown-start protection device starts again to balance the pressure difference, and the above process is repeated cyclically. In addition, starting the electric booster pump can also pressurize the second fluid until the pressure difference of the elastic device reaches a certain value and then the injection of the second fluid stops. Similarly, in the shutdown state, the electric booster pump needs to pressurize the compression assembly cavity multiple times depending on the length of the shutdown time. The frequency of replenishment depends on the leakage at the seal.

[0077] Furthermore, the electric booster pump can be a booster pump for the third fluid or a compressor for boosting the second fluid. For example, by compressing the second fluid, the pressure of the second fluid working medium in the compression component cavity can be kept at a high pressure, which can also balance the pressure difference of the elastic device and protect the operation of the elastic device during the start-up process.

[0078] Furthermore, the active shutdown-start protection device also includes a battery, enabling active protection even in the event of a power outage.

[0079] Furthermore, such as Figure 6 As shown in Figure a, the passive stop-start protection device can employ a fourth elastic device 94. One end of the fourth elastic device is fixed, and the other end is in a free state. To prevent the second fluid from entering the working chamber, the free end is closed. The closed end can be a metal diaphragm or a flat plate. Preferably, the fourth elastic device 94 is an elastic device composed of a metal bellows and a metal diaphragm, such as... Figure 4 As shown in diagram e. In the shutdown state, when the pressure in the working chamber is higher than that in the compression component chamber, the volume of the fourth elastic device automatically increases, resulting in an increase in the volume of the working chamber. This reduces the pressure inside the working chamber and decreases the pressure difference between the working chamber and the compression component chamber, thereby reducing the pressure difference that the elastic device can withstand. Therefore, when the ambient temperature is constant, and without considering leakage of the first and second fluids, the pressure difference that the elastic device can withstand can be maintained for a long time. During operation, the pressure in the compression component chamber 14 rises, pushing the fourth elastic device 94 to reduce the volume of the working chamber, thereby increasing the pressure inside the working chamber.

[0080] Furthermore, such as Figure 6 As shown in Figure b, the differential pressure regulating device 10 is connected to the fourth elastic device 94. During operation, under the action of the differential pressure regulating device 10, the volume of the fourth elastic device 94 can be adjusted, allowing the working chamber pressure to reach the target value. To allow for a wider range of adjustment of the working chamber volume, the volume of the fourth elastic device in its free state is 0.5 to 100 times the scavenging volume of the discharger. The volume of the fourth elastic device determines the range of change in the working chamber volume. Preferably, the volume of the fourth elastic device in its free state is 1 to 20 times the scavenging volume of the discharger. The scavenging volume of the discharger is the product of the discharger area and the discharger stroke, approximately equal to the volume of the high-temperature chamber, where the discharger area is calculated based on the discharger's outer diameter. The free state refers to the state without applied force. When the elastic device is a jointed device at both ends, the joints need to be removed to eliminate the influence of gravity on the volume of the elastic device caused by the weight of the joints.

[0081] It should be noted that the third elastic device 93 and the fourth elastic device 94 are structurally similar and can both be connected to the first elastic device 91 and the second elastic device 92. Their difference lies in their function, resulting in significant differences in their dimensional parameters: the function of the third elastic device 93 is to compensate for volume changes in the first elastic device 91 or the second elastic device 92, typically with small changes, especially for applications such as... Figure 6 As shown in Figure a, the first elastic device 91 and piston 7 form a closed cavity 131. The volume change caused by the compression of the first elastic device 91 is largely offset by the dumbbell-shaped structure of piston 7. Therefore, the third elastic device typically has a small diameter and length, resulting in a small volume. The fourth elastic device, mainly used to regulate the working volume of the working chamber, has a larger diameter or length and a larger volume. In this invention, the volume of the fourth elastic device in its free state is 0.5 to 100 times the scavenging volume of the discharger. Preferably, the volume of the fourth elastic device in its free state is 1 to 20 times the scavenging volume of the discharger, or the volume of the fourth elastic device in its free state is 0.2 to 5 times the total volume of the working chamber. The larger volume of the fourth elastic device 94 provides protection for its wide-range adjustment of the average pressure of the working chamber and its adaptation to various operating conditions of the heat-driven compressor. Furthermore, the fourth elastic device 94 can also have a guide rod inside. One end of the guide rod is connected to the fourth elastic device 94, and the other end is located in a cylinder that cooperates with the guide rod and can reciprocate.

[0082] Preferably, the fourth elastic device is a welded bellows. Furthermore, for elastic devices based on metal bellows, the volume is as follows: Figure 4 As shown in f, this refers to the volume occupied by the second fluid in the internal free state. Furthermore, for the volume calculation of elastic devices based on metal diaphragms, as shown... Figure 4As shown in g.

[0083] Furthermore, such as Figure 6 As shown in Figure c, the passive shutdown-start protection device can also be a pressure boosting / depressurization device 29. The pressure boosting / depressurization device 29 has a pressure boosting / depressurization volumetric chamber 2901, a compression mechanism 2902, and a pressure boosting / depressurization control valve 2903. During startup, the pressure boosting / depressurization control valve 2903 is opened, and the compression mechanism 2902 pumps the working fluid from the pressure boosting / depressurization volumetric chamber 2901 into the working chamber, increasing the pressure in the working chamber. Once the target value is reached, the pressure boosting / depressurization control valve 2903 is closed. During shutdown, by controlling the opening of the pressure boosting / depressurization control valve 2903, the mass of the working fluid flowing into the pressure boosting / depressurization volumetric chamber 2901 from the working chamber can be adjusted, thereby regulating the pressure in the working chamber and ultimately balancing the pressure difference borne by the elastic device.

[0084] Furthermore, such as Figure 6As shown in f, the pressure boosting and depressurization device 29 can also be located on the second fluid side. During shutdown, the pressure boosting and depressurization control valve 2903 is opened, or leakage from the pressure boosting and depressurization control valve 2903 is utilized, allowing the working fluid in the compression assembly chamber 14 to flow into the pressure boosting and depressurization volume chamber 2901. This maintains the pressure within the compression assembly chamber 14 within a set range during shutdown, thereby improving the pressure differential resistance of the balance elastic device. During startup or operation, the pressure boosting and depressurization control valve 2903 is opened, and the compression mechanism 2902 pumps the working fluid out of the pressure boosting and depressurization volume chamber 2901 and into the compression assembly 15 or the compression assembly chamber 14. The pressure within the compression assembly chamber increases, enabling the normal operation of the compression assembly 15. Preferably, the volume of the pressure boosting and depressurization volume chamber 2901 can be calculated based on the refrigerant mass and the saturated vapor density at 1 MPa, i.e., the volume is equal to more than 20% of the ratio of the refrigerant mass to the saturated vapor density at 1 MPa. Furthermore, the pressure boosting and depressurization chamber 2901 can be a gas-liquid separator 28. Preferably, the volume of the gas-liquid separator 28 is equal to more than 20% of the ratio of the refrigerant mass to the saturated vapor density at 1 MPa, or the volume of the gas-liquid separator 28 is ≥10L, such that the pressure inside the compression assembly chamber 14 is less than the saturation pressure of the second fluid at 305K when the unit is shut down at 305K. In this case, the pressure boosting and depressurization device 29 may not include the pressure boosting and depressurization control valve 2903. It should be noted that when the pressure control function of the gas-liquid separator 28 is replaced by a gas cylinder connected to the gas-liquid separator 28, the volume of the gas cylinder should be considered as the volume of the gas-liquid separator 28. Alternatively, when the volume inside the compression assembly chamber 14 is ≥2L, the volume inside the compression assembly chamber 14 should also be considered as the volume of the gas-liquid separator 28. Furthermore, when the pressure boosting and depressurization device 29 is located on the second fluid side, it can also be used during the shutdown phase. The pressure boosting and depressurization control valve 2903 is opened, or leakage from the valve 2903 is utilized, allowing the working fluid in the pressure boosting and depressurization volume chamber 2901 to flow into the working fluid in the compression assembly chamber 14. During startup or operation, the pressure boosting and depressurization control valve 2903 is opened, and the compression mechanism 2902 pumps the working fluid from the compression assembly chamber 14 into the pressure boosting and depressurization volume chamber 2901. Furthermore, the pressure boosting and depressurization volume chamber 2901 can contain a non-condensable gas at room temperature (25°C), such as nitrogen, argon, or air. During shutdown, the non-condensable gas flows into the compression assembly chamber 14, achieving a pressure in the compression assembly chamber 14 comparable to the working chamber. During startup or operation, the non-condensable gas in the compression assembly chamber 14 is pumped into the pressure boosting and depressurization volume chamber 2901. To reduce the impact of non-condensable gases on heat exchange, a non-condensable gas separator may also be included.

[0085] Furthermore, such as Figure 6As shown in Figure d, the passive shutdown-start protection device can also be a second buffer chamber 24. The second buffer chamber 24 is connected to the compression component chamber 14 via a crankshaft. Therefore, the second buffer chamber 24 can maintain a pressure state comparable to that of the working chamber, thereby ensuring that the pressure of the working chamber is not limited by the compression component chamber 14, achieving long-life operation of the first elastic device 91. Preferably, in order to maintain the pressure inside the second buffer chamber 24, the second buffer chamber 24 can also have a gas supply device, such as an external gas cylinder or a booster pump. The booster pump is used to pump air into the second buffer chamber 24. Since the air pressure changes little with the ambient temperature, it can balance the pressure difference borne by the elastic device. Furthermore, the working medium inside the second buffer chamber 24 is a non-condensable gas at room temperature (25°C), such as nitrogen, argon, or air. Preferably, it is nitrogen.

[0086] Furthermore, the passive shutdown-start protection device can also be a fifth elastic device 95. Preferably, the fifth elastic device 95 has an elastic device differential pressure regulating device, such as... Figure 6 As shown in j, the fifth elastic device 95 isolates the compression chamber of the compression component 14 and the compression chamber of the compression component 15. Therefore, the pressure of the compression component 14 is not affected by the working condition of the compression component 15, thus maintaining a pressure state comparable to that of the working chamber, and achieving long-life operation of the first elastic device 91.

[0087] Furthermore, the passive shutdown-start protection device can also be as follows: Figure 6 As shown in Figure e, this passive stop-start protection device has a second buffer chamber 24 and a fifth elastic device 95. The second buffer chamber 24 is located between the working chamber and the compression assembly chamber 14. The working chamber and the second buffer chamber 24 are isolated by the fifth elastic device. One end of the fifth elastic device is connected to the piston 7, and the other end is fixed. To compensate for the volume change during the movement of the piston 7, one end of the other fifth elastic device is fixed, and the other end is in a free state. Furthermore, the closed cavities of the two fifth elastic devices are connected and share the elastic device pressure difference adjustment device 10. Therefore, in the stop state, when there is a large pressure difference between the working chamber pressure and the compression assembly chamber 14, the pressure can be transitioned through the second buffer chamber 24 to avoid excessive pressure difference on the elastic device.

[0088] Furthermore, the passive shutdown-start protection device 22 can also be as follows: Figure 6As shown in Figure h, the passive shutdown-start protection device 22 has a first solenoid valve 351 and a second solenoid valve 352. The first solenoid valve 351 is located at the inlet of the compression assembly 15, and the second solenoid valve 352 is located at the outlet of the compression assembly 15. Preferably, the first solenoid valve 351 and the second solenoid valve 352 are normally closed when de-energized. Therefore, when the leakage of the first solenoid valve 351 and the second solenoid valve 352 is almost zero, the pressure inside the compression assembly cavity 14 is less affected by the ambient temperature in the shutdown state, thereby achieving a small pressure difference between the working chamber pressure and the compression assembly cavity 14 in the shutdown state. Furthermore, the compression assembly cavity 14 is filled with a third fluid in the shutdown state. Furthermore, the leakage of the first solenoid valve 351 and the second solenoid valve 352 can meet the requirement that the pressure fluctuation inside the compression assembly cavity 14 within 1 hour is ≤0.1MPa. In addition, during the operation of the heat-driven compressor, the first solenoid valve 351 and the second solenoid valve 352 are open.

[0089] Furthermore, when the elastic device is a metal diaphragm, the passive stop-start protection device 22 can also be as follows: Figure 4 As shown in h or 4i, the passive shutdown-start protection device 22 is a diaphragm protection device 39. The diaphragm protection device 39 has a structure that matches the diaphragm that deforms under the design pressure. Therefore, the stretching range of the diaphragm is limited. Moreover, since the diaphragm protection device 39 matches the deformed diaphragm, the diaphragm is prevented from being damaged by the protection device. Figure 4 i shows another diaphragm protection device, diaphragm protection device 39, which also has a structure that matches the diaphragm that deforms under the design differential pressure, thus preventing the diaphragm from being damaged by the protection device.

[0090] Furthermore, the shutdown-start protection device can be a combination of active and passive types. On the one hand, the passive shutdown-start protection device reduces the pressure difference between the working chamber and the compression component chamber; on the other hand, the active shutdown-start protection device can further balance the pressure difference borne by the elastic device, reducing the performance requirements of the fourth elastic device and improving reliability and lifespan. Alternatively, it can be a combination of several different passive shutdown-start protection devices. For example: Figure 6 Figure g illustrates a combined scheme based on two different passive shutdown-start protection devices. A fourth elastic device 94 is used on the working chamber side, and a pressure boosting and depressurization device 29 is used on the compression assembly chamber side. During shutdown, the first fluid pressure on the working chamber side is reduced to a certain pressure range by the fourth elastic device 94, and the second fluid pressure on the compression assembly chamber side is reduced to a range corresponding to the first fluid pressure by the pressure boosting and depressurization device 29, thus maintaining the pressure difference between the working chamber and the compression assembly chamber within an allowable range under different ambient temperatures. Preferably, the working chamber pressure is controlled below 1 MPa during shutdown.

[0091] Furthermore, when the pressure boosting and depressurization device 29 is used to boost the second fluid, the compression mechanism 2902 in the pressure boosting and depressurization device 29 can be the compression assembly 15, such as... Figure 6 As shown in g, during the startup phase, the working fluid in the pressurization / depressurization chamber 2901 is pumped into the pressurization / depressurization unit 15 using the compression assembly 15. The fluid is then pumped into the condenser 25 connected to the compression assembly 15 or into the compression assembly chamber 14, thus achieving normal operation of the refrigeration or heating system. Preferably, the pressurization / depressurization control valve 2903 in the pressurization / depressurization device 29 can be a three-way valve, such as... Figure 6 As shown in g, when the compression assembly 15 is connected to the pressure boosting and depressurization volume chamber 2901 through the first pressure boosting and depressurization control valve 2903a, the compression assembly 15 is disconnected from the gas-liquid separator 28 through the second pressure boosting and depressurization control valve 2903b, and vice versa.

[0092] Furthermore, when the pressure boosting and depressurization device 29 is used to adjust the pressure of the working chamber, the compression mechanism 2902 has an intake valve 2903 and an exhaust valve 2904. The power source of the compression mechanism 2902 can be a piston 7, an exhaust device 6, or an electromagnetic device, etc. When the electromagnetic device is used as the power source of the compression mechanism 2902, the compression mechanism 2902 is a linear compression mechanism, eliminating the lateral force during the movement. The electromagnetic device can be a simple magnet coil that provides electromagnetic force, or it can be a linear motor. Figure 6 Figure 1 illustrates a pressure boosting and depressurization device 29 with a piston 7 as the power source. The piston 7, cylinder 8, intake valve 2903, and exhaust valve 2904 constitute the compression mechanism 2902. When the piston 7 moves upward, the intake valve 2903 opens and the exhaust valve 2904 closes, allowing the working fluid in the pressure boosting and depressurization chamber 2901 to flow into the compression chamber. When the piston 7 moves downward, the intake valve 2903 closes, and the working fluid in the compression chamber of the compression mechanism 2902 is compressed. When the pressure reaches a certain value, the exhaust valve 2904 opens, and the working fluid is discharged into the working chamber, increasing the pressure in the working chamber. Furthermore, the pressure boosting and depressurization device 29 also has a fourth solenoid valve 354. The fourth solenoid valve 354 can unload the pumping function of the compression mechanism 2902; that is, when the fourth solenoid valve 354 is open, although the compression mechanism 2902 still draws in and exhausts air, it does not produce a pressure boosting function or the pressure boost is very small. When the pressure boosting and depressurization device 29 is an electromagnetic device, the unloading of the pressure boosting and depressurization device 29 can be achieved by unloading the electromagnetic force. In addition, when the pressure boosting and depressurization device 29 is used to adjust the pressure of the working chamber, the pressure boosting and depressurization device 29 can also have the function of adjusting the output power of the thermodynamic device 17.

[0093] Example 4

[0094] The inventors of this application have discovered that even with the passive shutdown-start protection device 22, the pressure difference across the elastic device in the compression assembly cavity 14 can become excessive under certain operating conditions due to the influence of operating conditions, potentially damaging the elastic device during the start-up phase. Therefore, this invention also relates to an operating method for the aforementioned heat-driven compressor, which can be either operating mode 1 or operating mode 2, wherein operating mode 1:

[0095] (1) Detect the pressure difference that the elastic device can withstand;

[0096] (2) When the detected pressure difference of the elastic device is greater than the set value, the shutdown-start protection device is activated first to reduce the pressure difference of the elastic device to the set value, and then the thermodynamic device 17 is activated, that is, the piston 7 or the discharger 6 starts to reciprocate; when the detected pressure difference of the elastic device is less than the set value, the shutdown-start protection device 19 can be activated first to further reduce the pressure difference of the elastic device before the thermodynamic device 17 is activated. Of course, the thermodynamic device 17 can also be activated directly at this time.

[0097] Operating mode 2: Directly start the shutdown-start protection device, and then start the thermal power device 17.

[0098] Furthermore, operating mode 1 is as follows: Figure 8 As shown in Figure a, the thermally driven compressor starts and detects the pressure difference borne by the elastic device. Based on the pressure difference, it determines whether the electric booster pump needs to be started. The pressure difference setting range is 0.05 MPa to +∞, preferably 0.2 MPa to +∞. When the detected pressure difference borne by the elastic device is less than the set value, the electric booster pump does not need to be started; the thermal power device is started directly, or the electric booster pump is started to further reduce the pressure difference borne by the elastic device before starting the thermal power device. When the detected pressure difference borne by the elastic device is greater than the set value, the electric booster pump needs to be started. First, the electric booster pump is started to balance the pressure difference of the elastic device. When the pressure difference of the elastic device drops to a certain value, such as 0.2 MPa, the thermal power device 17 is started.

[0099] Operating mode 2: such as Figure 8 As shown in Figure b, the thermally driven compressor starts, directly starting the electric booster pump, and then the thermal power unit 17 starts. The time interval between starting the electric booster pump and starting the thermal power unit 17 depends on the pressure difference of the elastic device. For example, if the device stops operating for a long time at certain temperatures, the pressure difference of the elastic device is large, and more third fluid needs to be replenished in the closed cavity of the elastic device, which requires a long time; when the pressure difference of the elastic device is small, and less third fluid needs to be replenished in the closed cavity of the elastic device, which requires a short time.

[0100] It should be noted that starting the thermal power device 17 refers to the reciprocating motion of the piston within the thermal power device 17. However, the process of starting the thermal power device 17, such as heating while the piston remains stationary, is not considered as starting the thermal power device 17. Furthermore, the reciprocating motion of the piston refers to a piston movement frequency of 5 Hz or higher.

[0101] Furthermore, the pressure difference that the elastic device can withstand can be detected by measuring the length of the elastic device, or by measuring the pressure difference between the working chamber and the closed chamber of the elastic device, or by measuring the pressure difference between the working chamber and the compression component chamber, etc.

[0102] Furthermore, after starting the thermal power unit 17, the pressure in the working chamber and / or compression assembly 15 is increased to a set value through the shutdown-start protection device. For example, after starting the thermal power unit 17, the fourth solenoid valve 354 closes, the pressure boosting and depressurization device 29 operates, and the working fluid in the pressure boosting and depressurization volume chamber 2901 is pumped into the working chamber by the compression mechanism 2902. After the pressure reaches the set target value, the fourth solenoid valve 354 opens, the compression mechanism 2902 unloads the pumped air, and disconnects the pipeline connection between the working chamber and the pressure boosting and depressurization volume chamber 2901, thereby realizing the operation of the thermal power unit 17 in the vehicle. The electric-driven booster pump also maintains the pressure difference of the elastic device within the tolerable pressure difference range.

[0103] Example 5

[0104] Figure 9 A refrigeration and heating device based on a heat-driven compressor is shown, including the aforementioned heat-driven compressor, evaporator 26, condenser 25, and expansion device 27. The high-temperature and high-pressure refrigerant compressed by the compression assembly 15 flows into the condenser 25, and after the heat exchanger in the condenser 25, it flows into the evaporator 26 via the expansion device 27. After the refrigerant flows out of the evaporator 26, it flows back into the compression assembly 15.

[0105] Furthermore, Figure 9 The refrigeration and heating device based on a heat-driven compressor shown in Figure a also includes a gas-liquid separator 28 and a four-way valve 30. Figure 9 The refrigeration and heating device based on the heat-driven compressor shown in Figure a also includes a medium heat exchanger 312 that exchanges heat with the condenser 25, a medium heat exchanger 311 that exchanges heat with the evaporator, and a related heat transfer medium pump 32. The heat transfer medium can be an ethylene glycol solution or other heat transfer medium.

[0106] Furthermore, Figure 9Figure b illustrates a refrigeration and heating device based on a heat-driven compressor with intermediate gas injection, including the aforementioned heat-driven compressor, evaporator 26, condenser 25, expansion device 27, flash evaporator 33, first expansion device 271, second expansion device 272, and gas injection valve 34. The compression assembly 15 in the heat-driven compressor has two-stage compression or intermediate gas injection. The high-temperature, high-pressure refrigerant compressed by the compression assembly 15 flows into the condenser 25, and after the heat exchanger in the condenser 25, it flows into the flash evaporator 33 via the first expansion device 271. The liquid flows into the evaporator 26 via the second expansion device 272. After flowing out of the evaporator 26, the refrigerant flows into the suction port of the compression assembly 15. Vapor in the flash evaporator 33 flows into the gas injection port of the compression assembly 15 via the gas injection valve 34. Furthermore, Figure 9 The refrigeration and heating device shown in b also includes a gas-liquid separator 28, a four-way valve 30, a second medium heat exchanger 312 that exchanges heat with the condenser 25, a first medium heat exchanger 311 that exchanges heat with the evaporator, and a related heat transfer medium pump 32. Furthermore, the refrigeration and heating device with intermediate gas supply based on a heat-driven compressor can also be based on an economizer-based intermediate gas supply scheme.

[0107] Furthermore, Figure 9 c illustrates a refrigeration and heating device based on a heat-driven compressor. After heat exchange with the condenser 25, the heat exchange medium flows to the low-temperature heat exchanger 4 to absorb waste heat from the thermal power unit 17. After heat exchange in the low-temperature heat exchanger 4, it flows to the medium heat exchanger 312. Further, under heating conditions, the average heat release temperature in the low-temperature heat exchanger 4 is at least 2.5°C higher than the average heat release temperature or condensation temperature in the condenser 25. Preferably, under heating conditions, the average heat release temperature in the low-temperature heat exchanger 4 is at least 5°C higher than the average heat release temperature or condensation temperature in the condenser 25.

[0108] Furthermore, Figure 9 The refrigeration and heating device based on a heat-driven compressor shown in Figure c also includes a burner 36, a first flue gas waste heat exchanger 37, and a second flue gas waste heat exchanger 38. After the flue gas generated by the combustion of fuel and air in the burner 36 exchanges heat with the high-temperature heat exchanger 2, in order to recover the waste heat of the flue gas, the flue gas first passes through the first flue gas waste heat exchanger 37 to exchange heat with the heat exchange medium from the low-temperature heat exchanger 4, and then flows to the medium heat exchanger 312. Further, after the flue gas generated by the combustion of the burner 36 passes through the first flue gas waste heat exchanger 37, it flows through the second flue gas waste heat exchanger 38 to continue to recover the waste heat of the flue gas. In the second flue gas waste heat exchanger 38, it exchanges heat with the low-temperature refrigerant from the evaporator 26, and uses the low-temperature refrigerant to further recover the waste heat of the flue gas.

[0109] Example 6

[0110] The inventors of this application have discovered that the refrigeration and heating device based on the thermodynamic device 17 and the compression assembly 15 can also achieve efficient independent power generation. Therefore, this invention also relates to the operation method of the above-mentioned refrigeration and heating device: controlling the third solenoid valve 353 to unload the compression function of the heat-driven compressor compression assembly 15, the output power of the thermodynamic device 17 is used for power generation by the electromagnetic device 18, outputting electrical energy and waste heat, realizing a thermo-electric mode. When the expansion device 27 is an electrically controlled expansion valve, the electrically controlled expansion valve can be opened to the maximum, or the compression function of the heat-driven compressor compression assembly 15 can be almost unloaded. At this time, the evaporator fan stops running or the heat transfer medium pump that exchanges heat with the evaporator stops running, the output power of the thermodynamic device 17 is used for power generation by the electromagnetic device 18, outputting electrical energy and waste heat, also realizing a thermo-electric mode.

[0111] Furthermore, the unloading device 40, such as the third solenoid valve 353, activates the compression function of the thermally driven compressor compression assembly 15. When the output power of the thermal power device 17 is entirely used for the compression function of the refrigerant in the refrigeration and heating device, cold energy and waste heat are output, realizing a heat-cold mode. Additionally, when part of the output power of the thermal power device 17 is used for the compression function of the refrigerant in the refrigeration and heating device, and the remaining part is used for the power generation of the electromagnetic device 18, cold energy and electrical energy are output, realizing a heat-cold and electric mode. Similarly, when the electricity price is low, electrical energy can be input using the electromagnetic device 18 to drive the compression of the compression assembly 15. If the thermal power device 17 absorbs high-temperature heat to do work, cold energy is output, realizing a heat-electric-cold mode; if the thermal power device 17 does not absorb high-temperature heat to do work, an electric-cold mode is realized. Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make many possible variations and modifications to the technical solutions of this invention, or modify them into equivalent embodiments, without departing from the scope of the technical solutions of this invention. Therefore, any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of this invention without departing from the content of the technical solutions of this invention should fall within the protection scope of the technical solutions of this invention.

Claims

1. A heat-driven compressor, comprising a compression assembly (15) and a thermal power unit (17), the thermal power unit (17) being based on a Stirling engine, the thermal power unit (17) comprising a high-temperature chamber (1), a high-temperature heat exchanger (2), a regenerator (3), a low-temperature heat exchanger (4), a low-temperature chamber (5), an exhaust device (6), a piston (7), and a cylinder (8), the high-temperature chamber (1), the high-temperature heat exchanger (2), the regenerator (3), the low-temperature heat exchanger (4), and the low-temperature chamber (5) constituting a working chamber, the working chamber containing a first fluid, and the compression assembly (15) containing a second fluid, characterized in that: The heat-driven compressor also includes a transmission mechanism (16), a first elastic device closed cavity (131) containing a third fluid, a first elastic device (91) for isolating the first elastic device closed cavity (131) from the working cavity, and an elastic device differential pressure regulating device (10) for regulating the differential pressure of the first elastic device (91). One end of the first elastic device (91) is fixed and the other end is connected to the piston (7). The piston (7) and the compression assembly (15) are connected to the transmission mechanism (16), or the piston (7), the discharger (6) and the compression assembly (15) are connected to the transmission mechanism (16). It also includes a second elastic device closed cavity (132) containing a third fluid, and a second elastic device (92) for isolating the second elastic device closed cavity (132) from the working cavity. One end of the second elastic device (92) is fixed and the other end is connected to the discharge device (6). The first elastic device closed cavity (131) is connected to the second elastic device closed cavity (132). The elastic device differential pressure regulating device (10) is connected to the second elastic device closed cavity (132). And / or, it also includes a third elastic device enclosure (133) containing a third fluid, and a third elastic device (93) for isolating the third elastic device enclosure (133) from the working chamber, wherein one end of the third elastic device (93) is fixed and the other end is free, the first elastic device enclosure (131) is connected to the third elastic device enclosure (133), and the elastic device differential pressure regulating device (10) is connected to the third elastic device enclosure (133).

2. The heat-driven compressor according to claim 1, characterized in that: The first elastic device (91), the second elastic device (92) and the third elastic device (93) are bellows or diaphragms, and the bellows are welded bellows or hydroformed bellows; When the bellows is a hydraulically formed bellows, the ratio of the stroke of the piston (7) or the discharger (6) to the free length of the connected hydraulically formed bellows is 0.01 to 0.

35. When the bellows is a welded bellows, the ratio of the stroke of the piston (7) or the discharger (6) to the free length of the connected welded bellows is 0.1 to 0.

6.

3. The heat-driven compressor according to any one of claims 1 to 2, characterized in that: It also includes an electromagnetic device (18) for driving the piston (7) or the discharger (6) to move; and / or, the electromagnetic device (18) for outputting electrical energy.

4. The heat-driven compressor according to any one of claims 1 to 2, characterized in that: The compression assembly (15) is a piston-type compression assembly, a rolling rotor-type compression assembly, or a scroll-type compression assembly; the compression assembly (15) adopts a multi-stage compression structure or has an intermediate air inlet.

5. The heat-driven compressor according to any one of claims 1 to 2, characterized in that: When the first elastic device (91) is a bellows, the bellows has a guide rod inside, and the difference between the diameter of the guide rod and the inner diameter of the bellows is 0 mm to 15 mm.

6. The heat-driven compressor according to any one of claims 1 to 2, characterized in that: The elastic device differential pressure regulating device (10) includes a pump assembly (101) and a control valve (102).

7. A heat-driven compressor, comprising a compression assembly (15) and a thermal power unit (17), the thermal power unit (17) being based on a Stirling engine, the thermal power unit (17) comprising a high-temperature chamber (1), a high-temperature heat exchanger (2), a regenerator (3), a low-temperature heat exchanger (4), a low-temperature chamber (5), an exhaust device (6), a piston (7), and a cylinder (8), the high-temperature chamber (1), the high-temperature heat exchanger (2), the regenerator (3), the low-temperature heat exchanger (4), and the low-temperature chamber (5) constituting a working chamber, the working chamber containing a first fluid, and the compression assembly (15) containing a second fluid, characterized in that: The heat-driven compressor includes a first elastic device closed chamber (131) containing a third fluid, a first elastic device (91) for isolating the first elastic device closed chamber (131) from the working chamber, and an elastic device pressure difference regulating device (10) for regulating the pressure difference of the first elastic device (91). One end of the first elastic device (91) is fixed, and the other end is connected to the piston (7). The second fluid is carbon dioxide, and at an ambient temperature of 305K and in a shutdown state, the pressure in the working chamber is ≥1 MPa, and the pressure in the compression assembly chamber (14) where the compression assembly (15) is located is ≥2 MPa. The second fluid is ammonia, alkanes or Freon and the pressure in the working chamber is ≤2.5 MPa at an ambient temperature of 305 K and under shutdown conditions, and / or the pressure in the compression assembly chamber (14) where the compression assembly (15) is located is less than the saturation pressure of the second fluid at a temperature of 305 K; It also includes a second elastic device closed cavity (132) containing a third fluid, and a second elastic device (92) for isolating the second elastic device closed cavity (132) from the working cavity. One end of the second elastic device (92) is fixed and the other end is connected to the discharge device (6). The first elastic device closed cavity (131) is connected to the second elastic device closed cavity (132). The elastic device differential pressure regulating device (10) is connected to the second elastic device closed cavity (132). And / or, it also includes a third elastic device enclosure (133) containing a third fluid, and a third elastic device (93) for isolating the third elastic device enclosure (133) from the working chamber, wherein one end of the third elastic device (93) is fixed and the other end is free, the first elastic device enclosure (131) is connected to the third elastic device enclosure (133), and the elastic device differential pressure regulating device (10) is connected to the third elastic device enclosure (133).

8. A heat-driven compressor, comprising a compression assembly (15) and a thermal power unit (17), the thermal power unit (17) being based on a Stirling engine, the thermal power unit (17) comprising a high-temperature chamber (1), a high-temperature heat exchanger (2), a regenerator (3), a low-temperature heat exchanger (4), a low-temperature chamber (5), an exhaust device (6), a piston (7), and a cylinder (8), the high-temperature chamber (1), the high-temperature heat exchanger (2), the regenerator (3), the low-temperature heat exchanger (4), and the low-temperature chamber (5) constituting a working chamber, the working chamber containing a first fluid, and the compression assembly (15) containing a second fluid, characterized in that: The heat-driven compressor includes a first elastic device closed chamber (131) containing a third fluid, a first elastic device (91) for isolating the first elastic device closed chamber (131) from the working chamber, and an elastic device differential pressure regulating device (10) for adjusting the pressure difference of the first elastic device (91). One end of the first elastic device (91) is fixed, and the other end is connected to the piston (7). The compression assembly (15) has an intake pressure p1 and an exhaust pressure p2, and the working chamber has an average pressure p3. The compression assembly (15) is located in the compression assembly. The pressure p inside the cavity (14) is the pressure closest to p3 among p1 and p2; and / or, the compression assembly (15) has a first buffer cavity (241) inside the compression assembly cavity (14), the piston (7) passes through the first buffer cavity (241), the segment diameter of the piston (7) located in the first buffer cavity (241) is greater than the segment diameter of the piston (7) located in the compression assembly cavity (14), and the pressure in the first buffer cavity (241) is the intake pressure p1 or exhaust pressure p2 of the compression assembly (15); It also includes a second elastic device closed cavity (132) containing a third fluid, and a second elastic device (92) for isolating the second elastic device closed cavity (132) from the working cavity. One end of the second elastic device (92) is fixed and the other end is connected to the discharge device (6). The first elastic device closed cavity (131) is connected to the second elastic device closed cavity (132). The elastic device differential pressure regulating device (10) is connected to the second elastic device closed cavity (132). And / or, it also includes a third elastic device enclosure (133) containing a third fluid, and a third elastic device (93) for isolating the third elastic device enclosure (133) from the working chamber, wherein one end of the third elastic device (93) is fixed and the other end is free, the first elastic device enclosure (131) is connected to the third elastic device enclosure (133), and the elastic device differential pressure regulating device (10) is connected to the third elastic device enclosure (133).

9. A heat-driven compressor, comprising a compression assembly (15) and a thermal power unit (17), the thermal power unit (17) being based on a Stirling engine, the thermal power unit (17) comprising a high-temperature chamber (1), a high-temperature heat exchanger (2), a regenerator (3), a low-temperature heat exchanger (4), a low-temperature chamber (5), an exhaust device (6), a piston (7), and a cylinder (8), the high-temperature chamber (1), the high-temperature heat exchanger (2), the regenerator (3), the low-temperature heat exchanger (4), and the low-temperature chamber (5) constituting a working chamber, the working chamber containing a first fluid, and the compression assembly (15) containing a second fluid, characterized in that: The heat-driven compressor includes a first elastic device closed chamber (131) containing a third fluid, a first elastic device (91) for isolating the first elastic device closed chamber (131) from the working chamber, and an elastic device differential pressure regulating device (10) for regulating the differential pressure of the first elastic device (91). One end of the first elastic device (91) is fixed, and the other end is connected to the piston (7). The compression assembly (15) has an unloading device (40) for unloading the pressurization function of the compression assembly (15). The unloading device (40) is a solenoid valve or an electromagnetic clutch. It also includes a second elastic device closed cavity (132) containing a third fluid, and a second elastic device (92) for isolating the second elastic device closed cavity (132) from the working cavity. One end of the second elastic device (92) is fixed and the other end is connected to the discharge device (6). The first elastic device closed cavity (131) is connected to the second elastic device closed cavity (132). The elastic device differential pressure regulating device (10) is connected to the second elastic device closed cavity (132). And / or, it also includes a third elastic device enclosure (133) containing a third fluid, and a third elastic device (93) for isolating the third elastic device enclosure (133) from the working chamber, wherein one end of the third elastic device (93) is fixed and the other end is free, the first elastic device enclosure (131) is connected to the third elastic device enclosure (133), and the elastic device differential pressure regulating device (10) is connected to the third elastic device enclosure (133).

10. A heat-driven compressor, comprising a compression assembly (15) and a thermal power unit (17), the thermal power unit (17) being based on a Stirling engine, the thermal power unit (17) comprising a high-temperature chamber (1), a high-temperature heat exchanger (2), a regenerator (3), a low-temperature heat exchanger (4), a low-temperature chamber (5), an exhaust device (6), a piston (7), and a cylinder (8), the high-temperature chamber (1), the high-temperature heat exchanger (2), the regenerator (3), the low-temperature heat exchanger (4), and the low-temperature chamber (5) constituting a working chamber, the working chamber containing a first fluid, and the compression assembly (15) containing a second fluid, characterized in that: The heat-driven compressor also includes a shutdown-start protection device, a first elastic device enclosed cavity (131) containing a third fluid, a first elastic device (91) for isolating the first elastic device enclosed cavity (131) from the working cavity, and an elastic device differential pressure regulating device (10) for regulating the differential pressure of the first elastic device (91). One end of the first elastic device (91) is fixed and the other end is connected to the piston (7). The shutdown-start protection device is used to maintain or balance the differential pressure of the elastic device in the shutdown state and to balance the differential pressure of the elastic device during the start-up process. It also includes a second elastic device closed cavity (132) containing a third fluid, and a second elastic device (92) for isolating the second elastic device closed cavity (132) from the working cavity. One end of the second elastic device (92) is fixed and the other end is connected to the discharge device (6). The first elastic device closed cavity (131) is connected to the second elastic device closed cavity (132). The elastic device differential pressure regulating device (10) is connected to the second elastic device closed cavity (132). And / or, it also includes a third elastic device enclosure (133) containing a third fluid, and a third elastic device (93) for isolating the third elastic device enclosure (133) from the working chamber, wherein one end of the third elastic device (93) is fixed and the other end is free, the first elastic device enclosure (131) is connected to the third elastic device enclosure (133), and the elastic device differential pressure regulating device (10) is connected to the third elastic device enclosure (133).

11. The heat-driven compressor according to claim 10, characterized in that: The shutdown-start protection device includes an active shutdown-start protection device (20) and / or a passive shutdown-start protection device (22). The active shutdown-start protection device (20) is used to adjust the pressure difference of the elastic device multiple times in a short period of time, and the passive shutdown-start protection device (22) is used to maintain or balance the pressure difference of the elastic device for a long period of time. The compression assembly (15) is located in the compression assembly cavity (14), and the compression assembly cavity (14) contains a second fluid and a third fluid. Wherein: The active stop-start protection device (20) has an electric booster pump (21); And / or, the passive stop-start protection device (22) has a fourth elastic device (94) for isolating the working chamber and the compression assembly chamber (14), one end of the fourth elastic device (94) being fixed and the other end being free, and the volume of the fourth elastic device (94) in the free state being 0.5 to 100 times the scavenging volume of the discharger (6); And / or, the passive stop-start protection device (22) has a fifth elastic element (95) that isolates the compression assembly cavity (14) from the working cavity, or the fifth elastic element (95) isolates the compression assembly cavity (14) from the compression cavity of the compression assembly (15); And / or, the passive stop-start protection device (22) has a second buffer chamber (242) located between the working chamber and the compression assembly chamber (14); And / or, the passive shutdown-start protection device (22) has a pressure boosting and depressurization device (29), which has a pressure boosting and depressurization volume chamber (2901) and a compression mechanism (2902), through which the pressure boosting and depressurization volume chamber (2901) is used to adjust the pressure in the working chamber or the compression assembly chamber (14); And / or, the passive stop-start protection device (22) has a first solenoid valve (351) and a second solenoid valve (352), the first solenoid valve (351) being located at the inlet of the compression assembly (15) and the second solenoid valve (352) being located at the outlet of the compression assembly (15); And / or, the passive shutdown-start protection device (22) is a gas-liquid separator (28) with a volume ≥10L, such that the pressure in the compression assembly chamber (14) is less than the saturation pressure of the second fluid at 305K temperature under ambient temperature and shutdown conditions; And / or, the passive shutdown-start protection device (22) has a diaphragm protection device (39) for protecting the diaphragm-based elastic device.

12. The heat-driven compressor according to claim 11, characterized in that: When the pressure boosting and depressurizing device (29) is used to adjust the working chamber pressure, the compression mechanism (2902) has an intake valve (2903) and an exhaust valve (2904), and the piston (7), the cylinder (8), the intake valve (2903) and the exhaust valve (2904) constitute the compression mechanism (2902); or, the discharger (6), the cylinder (8), the intake valve (2903) and the exhaust valve (2904) constitute the compression mechanism (2902).

13. The heat-driven compressor according to claim 12, characterized in that: The pressure boosting and depressurization device (29) also has a fourth solenoid valve (354), which is used to unload the pumping function of the compression mechanism (2902).

14. A heat-driven compressor, comprising a compression assembly (15) and a thermal power unit (17), the thermal power unit (17) being based on a Stirling engine, the thermal power unit (17) comprising a high-temperature chamber (1), a high-temperature heat exchanger (2), a regenerator (3), a low-temperature heat exchanger (4), a low-temperature chamber (5), an exhaust device (6), a piston (7), and a cylinder (8), the high-temperature chamber (1), the high-temperature heat exchanger (2), the regenerator (3), the low-temperature heat exchanger (4), and the low-temperature chamber (5) constituting a working chamber, the working chamber containing a first fluid, and the compression assembly (15) containing a second fluid, characterized in that: The heat-driven compressor contains a first elastic device closed cavity (131) containing a third fluid, a first elastic device (91) for isolating the first elastic device closed cavity (131) from the working cavity, and an elastic device differential pressure regulating device (10) for regulating the differential pressure of the first elastic device (91). One end of the first elastic device (91) is fixed, and the other end is connected to the piston (7). The piston (7) passes through the first elastic device closed cavity (131) and through the cylinder (8) which is in clearance fit with the piston (7), and extends into the compression assembly cavity (14) where the compression assembly (15) is located. The third fluid in the first elastic device closed cavity (131) can leak through the clearance fit between the piston (7) and the cylinder (8). The clearance fit is located above the first elastic device closed cavity (131). It also includes a second elastic device closed cavity (132) containing a third fluid, and a second elastic device (92) for isolating the second elastic device closed cavity (132) from the working cavity. One end of the second elastic device (92) is fixed and the other end is connected to the discharge device (6). The first elastic device closed cavity (131) is connected to the second elastic device closed cavity (132). The elastic device differential pressure regulating device (10) is connected to the second elastic device closed cavity (132). And / or, it also includes a third elastic device enclosure (133) containing a third fluid, and a third elastic device (93) for isolating the third elastic device enclosure (133) from the working chamber, wherein one end of the third elastic device (93) is fixed and the other end is free, the first elastic device enclosure (131) is connected to the third elastic device enclosure (133), and the elastic device differential pressure regulating device (10) is connected to the third elastic device enclosure (133).

15. A method of operating a heat-driven compressor according to any one of claims 10 to 14, characterized in that: It has either operating mode 1 or operating mode 2, wherein: Operating mode 1: First, detect the pressure difference borne by the elastic device. When the detected pressure difference borne by the elastic device is greater than the set value, first activate the shutdown-start protection device to reduce the pressure difference borne by the elastic device to the set value, and then start the thermal power device (17). When the detected pressure difference borne by the elastic device is less than the set value, first activate the shutdown-start protection device to further reduce the pressure difference borne by the elastic device, and then start the thermal power device (17), or directly start the thermal power device (17). Operating mode 2: Directly start the shutdown-start protection device, and then start the thermal power device (17).

16. A refrigeration and heating device, comprising an evaporator (26), a condenser (25), and an expansion device (27), characterized in that: It also includes a heat-driven compressor according to any one of claims 1 to 14, wherein the high-temperature and high-pressure refrigerant compressed by the compression assembly (15) flows into the condenser (25), flows into the evaporator (26) after the heat exchanger of the condenser (25) via the expansion device (27), and flows back to the compression assembly (15) after the refrigerant flows out of the evaporator (26).

17. The refrigeration and heating apparatus according to claim 16, characterized in that: Under heating conditions, the difference between the average heat release temperature of the low-temperature heat exchanger (4) and the condensation temperature of the condenser (25) is ≥2.5℃.

18. A method of operating the refrigeration and heating apparatus according to any one of claims 16 to 17, characterized in that: Control the unloading device (40) or the expansion device (27) to achieve hot-cold mode operation and thermoelectric mode operation.

Images