Stirling engine and heat pump system

Abstract

The present application provides a Stirling engine and a heat pump system. The Stirling engine comprises: a housing, provided with an accommodating cavity, a first end of the accommodating cavity being provided with a first intake port and a first exhaust port, a second end of the accommodating cavity being provided with a second intake port and a second exhaust port, the first intake port and the second intake port being in communication with an exhaust port of a compressor, and the first exhaust port and the second exhaust port being in communication with a suction port of the compressor; a first heat exchanger, arranged in the first end; a second heat exchanger, arranged in the second end; a heat regenerator, arranged in the accommodating cavity and located between the first heat exchanger and the second heat exchanger; a first switch component, arranged in the first end and located on the side of the first heat exchanger away from the heat regenerator, and used for connecting the first intake port or the first exhaust port to a first pressure cavity located on the side of the first switch component facing the first heat exchanger; and a second switch component, arranged in the second end and located on the side of the second heat exchanger away from the heat regenerator, and used for connecting the second intake port or the second exhaust port to a second pressure cavity located on the side of the second switch component facing the second heat exchanger.

Description

Stirling engines and heat pump systems

[0001] This application claims priority to Chinese Patent Application No. 202510059269.5, filed on January 14, 2025, entitled “Stirling Heat Engine and Heat Pump System”, which is incorporated herein by reference in its entirety.

[0002] [Technical Field]

[0003] This application relates to the field of heat pump technology, and in particular to a Stirling engine and a heat pump system.

[0004] [Background Technology]

[0005] A traditional Stirling engine typically consists of a compression piston, an expansion piston, a hot-end heat exchanger, a cold-end heat exchanger, and a regenerator. The compression piston and the expansion piston reciprocate at a certain phase angle, and thermo-acoustic conversion occurs in the regenerator, forming a temperature gradient in the regenerator, pumping heat from the low-temperature end to the high-temperature end.

[0006] In related technologies, during the entire cycle of the working fluid in a Stirling engine, the compression piston and expansion piston rely on the crankshaft, connecting rod, and piston rod to convert the motor rotation into the reciprocating motion of the piston along the axial direction. However, the mechanical efficiency of the reciprocating motion of the compression piston and expansion piston along the axial direction is low, and the sealing between the compression piston and expansion piston and the piston cylinder is poor.

[0007] [Summary of the Invention]

[0008] This application provides a heat pump system to improve the mechanical efficiency and sealing performance of a Stirling engine.

[0009] To solve the above-mentioned technical problems, one technical solution adopted in this application is: providing a Stirling heat engine, comprising: a shell with a receiving cavity, wherein the cavity wall at a first end of the receiving cavity is provided with a first air inlet and a first air outlet, the cavity wall at a second end of the receiving cavity is provided with a second air inlet and a second air outlet, and the first air inlet and the second air inlet are configured to communicate with the exhaust port of a compressor, and the first exhaust port and the second exhaust port are configured to communicate with the suction port of the compressor; a first heat exchanger disposed in the first end; a second heat exchanger disposed in the second end; and a regenerator disposed in the receiving cavity and located between the first heat exchanger and the second heat exchanger. A first switching assembly is disposed within the first end and located on the side of the first heat exchanger away from the regenerator. The first switching assembly is configured to selectively connect the first air inlet or the first exhaust port to a first pressure chamber located on the side of the first switching assembly facing the first heat exchanger, so as to adjust the pressure of the first pressure chamber. A second switching assembly is disposed within the second end and located on the side of the second heat exchanger away from the regenerator. The second switching assembly is configured to selectively connect the second air inlet or the second exhaust port to a second pressure chamber located on the side of the second switching assembly facing the second heat exchanger, so as to adjust the pressure of the second pressure chamber.

[0010] In some embodiments, the first switching assembly includes a first rotating wheel, which is sealed to and rotatably disposed on the inner wall of the first end; the first rotating wheel has a first flow channel communicating with the first pressure chamber on the side near the first heat exchanger, and the first flow channel extends to the first outer peripheral wall of the first rotating wheel to form a first air port communicating with the first flow channel on the first outer peripheral wall; when the first rotating wheel rotates relative to the first pressure chamber, it selectively connects the first air port with the first air inlet or the first exhaust port; the second switching assembly includes a second rotating wheel, which is sealed to and rotatably disposed on the inner wall of the second end; the second rotating wheel has a second flow channel communicating with the second pressure chamber on the side near the second heat exchanger, and the second flow channel extends to the second outer peripheral wall of the second rotating wheel to form a second air port communicating with the second flow channel on the second outer peripheral wall; when the second rotating wheel rotates relative to the second pressure chamber, it selectively connects the second air port with the second air inlet or the second exhaust port.

[0011] In some embodiments, the first air inlet and the first exhaust outlet are arranged along the diameter direction of the first rotor; the second air inlet and the second exhaust outlet are arranged along the diameter direction of the second rotor.

[0012] In some embodiments, the dimension of the first flow channel along the circumference of the first impeller is half the circumference of the first impeller; the dimension of the second flow channel along the circumference of the second impeller is half the circumference of the second impeller.

[0013] In some embodiments, the first flow channel is semi-circular; the second flow channel is semi-circular.

[0014] In some embodiments, the first and second rotors are configured to rotate in the same direction and at the same speed; during rotation, the phase difference between the first flow channel and the second flow channel is 90°.

[0015] In some embodiments, during rotation, the first flow channel leads the second flow channel along the direction of rotation.

[0016] In some embodiments, the operating phases of the Stirling engine include: an isothermal compression phase, an isochoric cooling phase, an isothermal expansion phase, and an isochoric heating phase; the first pressure chamber and the second pressure chamber are respectively connected to the exhaust port of the compressor, and the Stirling engine is in the isothermal compression phase; the first pressure chamber is connected to the exhaust port of the compressor, and the second pressure chamber is connected to the intake port of the compressor, and the Stirling engine is in the isochoric cooling phase; the first pressure chamber and the second pressure chamber are respectively connected to the intake port of the compressor, and the Stirling engine is in the isothermal expansion phase; the first pressure chamber is connected to the intake port of the compressor, and the second pressure chamber is connected to the exhaust port of the compressor, and the Stirling engine is in the isochoric heating phase.

[0017] In some embodiments, the Stirling engine further includes: a first shaft connected to the first impeller and configured to drive the first impeller to rotate relative to the housing; and a second shaft connected to the second impeller and configured to drive the second impeller to rotate relative to the housing.

[0018] In some embodiments, the Stirling engine further includes: a first throttling element located between the first rotor and the first heat exchanger; and a second throttling element located between the second rotor and the second heat exchanger.

[0019] In some embodiments, a first buffer cavity is formed between the side of the first impeller away from the first heat exchanger and the end wall of the first end; a second buffer cavity is formed between the side of the second impeller away from the second heat exchanger and the end wall of the second end.

[0020] To solve the above-mentioned technical problems, one technical solution adopted in this application is: to propose a heat pump system, including: the above-mentioned Stirling heat engine; a compressor, wherein the exhaust port of the compressor is connected to the first air inlet and the second air inlet respectively, and the suction port of the compressor is connected to the first exhaust port and the second exhaust port respectively.

[0021] In some embodiments, the compressor includes a rotary compressor.

[0022] In some embodiments, the heat pump system further includes a first medium-temperature heat exchanger connected between the exhaust port of the compressor and the second intake port.

[0023] In some embodiments, the heat pump system further includes a second medium-temperature heat exchanger connected between the suction port and the first exhaust port of the compressor.

[0024] In some embodiments, the heat pump system further includes: a first throttling element and a first buffer tank, both disposed outside the housing and connected in series between the exhaust port of the compressor and the housing; a second throttling element and a second buffer tank, both disposed outside the housing and connected in series between the intake port of the compressor and the housing.

[0025] The beneficial effects of this application are as follows: The Stirling engine provided by this application includes a first heat exchanger, a second heat exchanger, a regenerator, a first switching assembly, and a second switching assembly disposed within a receiving cavity formed by the shell. The cavity wall at the first end of the receiving cavity is provided with a first air inlet and a first air outlet, and the cavity wall at the second end of the receiving cavity is provided with a second air inlet and a second air outlet. The first air inlet and the second air inlet are configured to communicate with the exhaust port of the compressor, and the first exhaust port and the second exhaust port are configured to communicate with the suction port of the compressor. The first heat exchanger is disposed within the first end, the second heat exchanger is disposed within the second end, and the regenerator is disposed within the receiving cavity. It is located between the first heat exchanger and the second heat exchanger; the first switch assembly is located in the first end and on the side of the first heat exchanger away from the regenerator, and the first switch assembly is configured to selectively connect the first air inlet or the first exhaust port to the first pressure chamber located on the side of the first switch assembly facing the first heat exchanger, so as to adjust the pressure of the first pressure chamber; the second switch assembly is located in the second end and on the side of the second heat exchanger away from the regenerator, and the second switch assembly is configured to selectively connect the second air inlet or the second exhaust port to the second pressure chamber located on the side of the second switch assembly facing the second heat exchanger, so as to adjust the pressure of the second pressure chamber. In this way, on the one hand, this application utilizes a first switching assembly to switch the compressor on and off to supply or discharge working fluid to the first pressure chamber, thereby regulating the pressure within the first pressure chamber. Similarly, it utilizes a second switching assembly to switch the compressor on and off to supply or discharge working fluid to the second pressure chamber, thus regulating the pressure within the second pressure chamber. Therefore, the combined use of the first and second switching assemblies enables alternating motion of the working fluid between the first and second ends of the chamber, thereby creating a temperature gradient in the regenerator and achieving heat pumping from the low-temperature end to the high-temperature end. On the other hand, compared to existing methods that achieve heat pumping through the axial reciprocating motion of a piston relative to a piston cylinder, this application achieves heat pumping through a switching assembly. The switching assembly has high operating efficiency, improving the mechanical efficiency of the Stirling engine and enhancing the sealing between the moving parts (switching assembly and housing). Therefore, this application can improve the heat pumping efficiency and reliability of the Stirling engine.

[0026] [Attached Image Description]

[0027] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort, wherein:

[0028] Figure 1 is a structural schematic diagram of an embodiment of the Stirling engine of this application;

[0029] Figure 2 is a structural schematic diagram of an embodiment of the first rotary wheel of this application;

[0030] Figure 3 is a structural schematic diagram of an embodiment of the second rotary wheel of this application;

[0031] Figure 4 is a schematic diagram of the relative position structure of the first rotor of this application with the compressor exhaust port and intake port in one state;

[0032] Figure 5 is a schematic diagram of the relative position structure of the second rotor of this application with the compressor exhaust port and intake port in one state;

[0033] Figure 6 is a schematic diagram of the relative position structure of the first impeller of this application with the compressor exhaust port and intake port in another state;

[0034] Figure 7 is a schematic diagram of the relative position structure of the second impeller of this application with the compressor exhaust port and intake port in another state;

[0035] Figure 8 is a schematic diagram of the relative position of the first impeller of this application with the compressor exhaust port and intake port in another state;

[0036] Figure 9 is a schematic diagram of the relative position of the first impeller of this application with the compressor exhaust port and intake port in another state;

[0037] Figure 10 is a schematic diagram of the relative position structure of the first impeller of this application with the compressor exhaust port and intake port in another state;

[0038] Figure 11 is a schematic diagram of the relative position of the first impeller of this application with the compressor exhaust port and intake port in another state;

[0039] Figure 12 is a schematic diagram of the ideal waveform of the pressure-volume change of the Stirling heat engine;

[0040] Figure 13 is a waveform diagram of the actual pressure-volume change of the Stirling engine in this application;

[0041] Figure 14 is a structural schematic diagram of another embodiment of the Stirling engine of this application;

[0042] Figure 15 is a structural schematic diagram of an embodiment of the heat pump system of this application;

[0043] Figure 16 is a schematic diagram of another embodiment of the heat pump system of this application;

[0044] Figure 17 is a structural schematic diagram of another embodiment of the heat pump system of this application.

[0045]

Detailed Implementation Methods

[0046] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0047] It should be noted that if the embodiments of this application involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicators will also change accordingly.

[0048] Furthermore, if the embodiments of this application involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, features defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the technical solutions of various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. If the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed in this application.

[0049] This application first proposes a Stirling engine, as shown in Figure 1, which is a structural schematic diagram of an embodiment of the Stirling engine of this application. The Stirling engine 10 of this embodiment includes: a casing 110, a first heat exchanger 120, a second heat exchanger 130, a regenerator 160, a first switching assembly 140, and a second switching assembly 150; wherein, the casing 110 has a receiving cavity (not shown), the cavity wall at the first end of the receiving cavity has a first air inlet (not shown) and a first exhaust port (not shown), the cavity wall at the second end of the receiving cavity has a second air inlet (not shown) and a second exhaust port (not shown), and the first air inlet and the second air inlet are configured to connect to the exhaust port (not shown) of a compressor (not shown), and the first exhaust port and the second exhaust port are configured to connect to the suction port (not shown) of the compressor; the first heat exchanger 120 is disposed in the first end; the second heat exchanger 130 is disposed in the second end; the regenerator 160... The first switch assembly 140 is disposed within the receiving cavity and located between the first heat exchanger 120 and the second heat exchanger 130. The first switch assembly 140 is disposed within the first end and located on the side of the first heat exchanger 120 away from the regenerator 160. The first switch assembly 140 is configured to selectively connect the first air inlet or the first exhaust port to the first pressure chamber A1 located on the side of the first switch assembly 140 facing the first heat exchanger 120, so as to adjust the pressure of the first pressure chamber A1. The second switch assembly 150 is disposed within the second end and located on the side of the second heat exchanger 130 away from the regenerator 160. The second switch assembly 150 is configured to selectively connect the second air inlet or the second exhaust port to the second pressure chamber A2 located on the side of the second switch assembly 150 facing the second heat exchanger 130, so as to adjust the pressure of the second pressure chamber A2.

[0050] On the one hand, this embodiment utilizes the first switching assembly 140 to switch the compressor on and off to supply or discharge working fluid to the first pressure chamber A1, thereby regulating the pressure within the first pressure chamber A1. Similarly, the second switching assembly 150 switches the compressor on and off to supply or discharge working fluid to the second pressure chamber A2, thereby regulating the pressure within the second pressure chamber A2. Therefore, the combined use of the first and second switching assemblies 140 and 150 enables alternating motion of the working fluid between the first and second ends of the chamber, thus creating a temperature gradient in the regenerator 160 and achieving heat pumping from the low-temperature end to the high-temperature end. On the other hand, compared to existing methods that achieve heat pumping through the axial reciprocating motion of a piston relative to a piston cylinder, this embodiment achieves heat pumping through the aforementioned switching assemblies. These switching assemblies have high operating efficiency, improving the mechanical efficiency of the Stirling engine 10 and enhancing the sealing between the moving parts (switching assembly) and the housing 110. Therefore, this embodiment improves the heat pumping efficiency and reliability of the Stirling engine 10.

[0051] In some embodiments, within the receiving cavity formed by the housing 110, the first heat exchanger 120, the regenerator 160, and the second heat exchanger 130 are sequentially arranged in contact to increase heat transfer efficiency; and the first heat exchanger 120, the regenerator 160, and the second heat exchanger 130 are arranged sequentially from the first end to the second end.

[0052] In other embodiments, the first heat exchanger, the regenerator, and the second heat exchanger may be arranged alternately.

[0053] In some embodiments, the first switching assembly 140 is spaced apart from the first heat exchanger 120 on the side near the first heat exchanger 120, so that the working fluid flows through multiple heat exchange channels within the first heat exchanger 120 to improve the flow efficiency of the working fluid and improve the pumping efficiency; and / or the second switching assembly 150 is spaced apart from the second heat exchanger 130 on the side near the second heat exchanger 130, so that the working fluid flows through multiple heat exchange channels within the second heat exchanger 130 to improve the flow efficiency of the working fluid and improve the pumping efficiency.

[0054] In some embodiments, as shown in Figures 1 and 2, Figure 2 is a structural schematic diagram of an embodiment of the first rotating wheel of this application; the first switching assembly 140 includes a first rotating wheel 141, the first rotating wheel 141 is sealed to the inner sidewall of the first end and is rotatably disposed; the first rotating wheel 141 is provided with a first flow channel 142 communicating with the first pressure chamber A1 on the side near the first heat exchanger 120, and the first flow channel 142 extends to the first outer peripheral wall of the first rotating wheel 141 to form a first air port (not shown in the figure) communicating with the first flow channel 142 on the first outer peripheral wall; when the first rotating wheel 141 rotates relative to the first pressure chamber A1, it selectively connects the first air port with the first air inlet or the first exhaust port.

[0055] The outer edge of the first rotating wheel 141 is sealed to the inner wall of the first end and is rotatably mounted.

[0056] In this embodiment, a first rotating wheel 141 with a first flow channel 142 serves as a first switching assembly 140. The relative rotation of the first rotating wheel 141 with the housing 110 allows for switching between the first pressure chamber A1 and either the first air inlet or the first exhaust port, or between the first air inlet and the first exhaust port, thereby adjusting the pressure of the first pressure chamber A1 via the compressor. Furthermore, the first rotating wheel 141 has a simple structure, requiring only rotation relative to the housing 110, thus improving mechanical efficiency and sealing performance.

[0057] In some embodiments, as shown in Figures 1 and 3, Figure 3 is a structural schematic diagram of an embodiment of the second rotating wheel of this application; the second switching assembly 150 includes a second rotating wheel 151, the second rotating wheel 151 is sealed to the inner sidewall of the second end and is rotatably disposed; the second rotating wheel 151 is provided with a second flow channel 152 communicating with the second pressure chamber A2 on the side near the second heat exchanger 130, and the second flow channel 152 extends to the second outer peripheral wall of the second rotating wheel 151 to form a second air port communicating with the second flow channel 152 on the second outer peripheral wall; when the second rotating wheel 151 rotates relative to the second pressure chamber A2, it selectively connects the second air port with the second air inlet or the second exhaust port.

[0058] The outer edge of the second rotating wheel 151 is sealed to the inner wall of the second end and is rotatably mounted.

[0059] In this embodiment, a second rotating wheel 151 with a second flow channel 152 serves as a second switching assembly 150. The relative rotation of the second rotating wheel 151 with the housing 110 allows for switching between the second pressure chamber A2 and either the second air inlet or the second exhaust port, or vice versa, thereby adjusting the pressure of the second pressure chamber A2 via the compressor. Furthermore, the second rotating wheel 151 has a simple structure, requiring only rotation relative to the housing 110, thus improving mechanical efficiency and sealing performance.

[0060] In some embodiments, other structures may be used to implement the above-described switching component.

[0061] In some embodiments, the first air inlet and the first exhaust outlet are arranged along the diameter direction of the first impeller 141. In this way, the structure of the first flow channel 142 of the first impeller 141 can be simplified, and the size of the first impeller 141 along the axial direction X of the receiving cavity can be reduced.

[0062] The arrangement of the first air inlet and the first exhaust outlet along the diameter of the first rotating wheel 141 means that the first air inlet and the first exhaust outlet are symmetrically arranged with the center of the first rotating wheel 141 as the center.

[0063] In some embodiments, the first air inlet and the first exhaust outlet may also be offset along the axial direction of the first rotor 141, so that the structure of the first flow channel 142 can be adjusted appropriately.

[0064] The first rotating wheel 141 has a certain thickness. The first air inlet and the first exhaust outlet are offset along the axial direction X of the first rotating wheel 141, which means that the first air inlet and the first exhaust outlet are offset in the thickness direction of the first rotating wheel 141.

[0065] In some embodiments, the second air inlet and the second exhaust outlet are arranged along the diameter direction of the second impeller 151. In this way, the structure of the second flow channel 152 of the second impeller 151 can be simplified, and the size of the second impeller 151 along the axial direction X of the receiving cavity can be reduced.

[0066] In some embodiments, the second air inlet and the second exhaust outlet may also be offset along the axial direction X of the second rotor 151, so that the structure of the second flow channel 152 can be adjusted appropriately.

[0067] In some embodiments, the circumferential dimension of the first flow channel 142 along the first rotor 141 is half the circumference of the first rotor 141. In this way, rotating the first rotor 141 90° relative to the housing 110 can switch the connection and disconnection between the first pressure chamber A1 and the compressor's intake port, and the connection and disconnection between the first pressure chamber A1 and the exhaust port. Furthermore, rotating the first rotor 141 360° can switch between the four states of the first pressure chamber A1: intake, shut-off, exhaust, and shut-off, thereby improving mechanical efficiency and pumping thermal efficiency.

[0068] In some embodiments, the circumferential dimension of the first flow channel 142 along the first rotor 141 can be appropriately adjusted and / or the position, number, etc. of the first air inlet and the first exhaust port on the housing 110 can be adjusted.

[0069] In some embodiments, the circumferential dimension of the second flow channel 152 along the second rotor 151 is half the circumference of the second rotor 151. In this way, rotating the second rotor 151 90° relative to the housing 110 can switch the connection and disconnection between the second pressure chamber A2 and the compressor's intake port, and the connection and disconnection between the second pressure chamber A2 and the compressor's exhaust port. Furthermore, rotating the second rotor 151 360° can switch between the four states of the second pressure chamber A2: intake, shut-off, exhaust, and shut-off, thereby improving mechanical efficiency and pumping thermal efficiency.

[0070] In some embodiments, the circumferential dimension of the second flow channel 152 along the second rotor 151 can be appropriately adjusted and / or the position, number, etc. of the second air inlet and the second exhaust outlet on the housing 110 can be adjusted.

[0071] In some embodiments, the first flow channel 142 is arranged in a semi-circular shape, which can increase the flow rate of the first flow channel 142, thereby improving the pumping efficiency.

[0072] In some embodiments, the first flow channel 142 may also be configured in other non-semi-circular ways, as long as the first pressure chamber A1 is connected to the first air port.

[0073] In some embodiments, the second flow channel 152 is arranged in a semi-circular shape, which can increase the flow rate of the second flow channel 152, thereby improving the pumping efficiency.

[0074] In some embodiments, the second flow channel 152 may also be configured in other non-semi-circular ways, as long as the second pressure chamber A2 is connected to the first air port.

[0075] In some embodiments, the first switching assembly 140 and the second switching assembly 150 may adopt the same structure, such as a high-frequency switching valve. In other embodiments, the two switching assemblies may adopt different structures.

[0076] In some embodiments, the first rotor 141 and the second rotor 151 are configured to rotate in the same direction and at the same speed; during rotation, the phase difference between the first flow channel 142 and the second flow channel 152 is 90°. In this way, the adjustment accuracy and matching degree of the gas pressure in the first pressure chamber A1 and the second pressure chamber A2 can be improved, thereby improving the heat pumping efficiency of the Stirling heat engine 10.

[0077] In some embodiments, during rotation, the first flow channel 142 leads the second flow channel 152 along the rotation direction. In this way, the phase angle of the working fluid in the first pressure chamber A1 is 90° earlier than the phase angle of the working fluid in the second pressure chamber A2. This not only makes the first end the hot end and the second end the cold end, but also allows the switching between the first pressure chamber A1, the second pressure chamber A2 and the compressor's exhaust or intake port to be achieved by rotating the first wheel 141 and the second wheel 151 by 90°. Therefore, this method also makes the alternating motion of the working fluid between the first and second ends more efficient, thereby improving cooking efficiency.

[0078] In other embodiments, the motion phase difference between the first rotating wheel 141 and the second rotating wheel 151 can be adjusted appropriately.

[0079] In some embodiments, the operating stages of the heat pump system include: isothermal compression, isochoric cooling, isothermal expansion, and isochoric heating. The first pressure chamber A1 and the second pressure chamber A2 are respectively connected to the exhaust port of the compressor 20, and the heat pump system is in the isothermal compression stage. The first pressure chamber A1 is connected to the suction port of the compressor 20, and the second pressure chamber A2 is connected to the exhaust port of the compressor 20, and the heat pump is in the isochoric cooling stage. The first pressure chamber A1 and the second pressure chamber A2 are respectively connected to the exhaust port of the compressor 20, and the heat pump system is in the isothermal expansion stage. The first pressure chamber A1 is connected to the exhaust port of the compressor 20, and the second pressure chamber A2 is connected to the suction port of the compressor 20, and the heat pump is in the isochoric heating stage. This embodiment, by controlling the first switching assembly 140 and the second switching assembly 150, can realize the switching and cycling of the isothermal compression mode, isochoric cooling mode, isothermal expansion mode, and isochoric heating mode of the Stirling heat engine 10, which can improve mechanical efficiency and pump thermal efficiency.

[0080] In some embodiments, as shown in FIG1, the first switching assembly 140 includes a first rotating wheel 141, and the second switching assembly 150 includes a second rotating wheel 151; the first flow channel 142 of the first rotating wheel 141 is semi-circular, and the second flow channel 152 of the second rotating wheel 151 is semi-circular; the first rotating wheel 141 and the second rotating wheel 151 are configured to rotate in the same direction and at the same speed; as shown in FIG4 and FIG5, during the rotation process, in the isothermal compression stage, the first rotating wheel 141 and the second rotating wheel 151 are rotated so that the first flow channel 142 of the first rotating wheel 141 and the second flow channel 152 of the second rotating wheel 151 are both connected to the exhaust port of the compressor 20, thereby pressurizing the working fluid in the accommodating cavity and releasing heat to the first pressure chamber A1 and the first heat exchanger 120; as shown in FIG6 and FIG7, the first rotating wheel 141 and the second rotating wheel 151 continue to rotate in the isochoric cooling stage, and the first flow channel 142 of the first rotating wheel 141 continues to be connected to the exhaust port of the compressor 20. The exhaust port is connected, while the second flow channel 152 of the second rotor 151 is connected to the suction port of the compressor 20. The working fluid stores heat in the regenerator 160, and the working fluid in the containment cavity is cooled at an isochoric rate. As the first rotor 141 and the second rotor 151 continue to rotate, as shown in Figures 8 and 9, during the isothermal expansion stage, the first flow channel 142 of the first rotor 141 is connected to the suction port of the compressor 20, while the second flow channel 152 of the second rotor 151 continues to be connected to the suction port of the compressor 20. The working fluid in the containment chamber is depressurized, cooled, and absorbs heat through the second heat exchanger 130. As shown in Figures 10 and 11, the first flow channel 142 of the first wheel 141 continues to connect with the suction port of the compressor 20 during the isochoric heating stage, while the second flow channel 152 of the second wheel 151 connects with the discharge port of the compressor 20. The working fluid absorbs heat from the regenerator 160, and the working fluid in the containment chamber undergoes isochoric heating. At this time, the first wheel 141 and the second wheel 151 have rotated 360°, rotating 90° in each working stage. The first wheel 141 and the second wheel 151 continue to rotate for the next revolution, thus continuing the four working stages of the next cycle.

[0081] Figure 12 shows the theoretical pressure and volume changes in the first pressure chamber A1 and the second pressure chamber A2 during the four working stages described above, forming two isothermal (temperatures Tc and Th) and two isochoric theoretical Stirling cycles. The theoretical cycle efficiency of this cycle is 100%, equivalent to the Carnot cycle efficiency. Since the heat exchange process in the heat exchanger is non-ideal isothermal, the actual pressure-volume changes during the above working stages are shown in Figure 13. The actual cycle efficiency can reach 70%, which is higher than that of traditional vapor compression cycles.

[0082] In some embodiments, the Stirling engine 10 further includes: a first rotating shaft 170 and a second rotating shaft 180; the first rotating shaft 170 is connected to the first rotating wheel 141 and configured to drive the first rotating wheel 141 to rotate relative to the housing 110; the second rotating shaft 180 is connected to the second rotating wheel 151 and configured to drive the second rotating wheel 151 to rotate relative to the housing 110.

[0083] The arrangement of the first rotating shaft 170 and the second rotating shaft 180 can not only improve the rotational stability of the first rotating wheel 141 and the second rotating wheel 151, but also improve the operability of their rotation.

[0084] In some embodiments, a first rotating shaft 170 is connected to the side of the first rotating wheel 141 away from the first heat exchanger 120, one end of the first rotating shaft 170 is connected to the first rotating wheel 141, and the other end can extend outside the receiving cavity to obtain driving force; a second rotating shaft 180 is connected to the side of the second rotating wheel 151 away from the second heat exchanger 130, one end of the second rotating shaft 180 is connected to the second rotating wheel 151, and the other end can extend outside the receiving cavity to obtain driving force.

[0085] In some embodiments, the first rotating shaft 170 and the second rotating shaft 180 can be driven by the same motor or other drive component, and their speeds and rotation directions can be consistent to simplify control and improve mechanical and pumping efficiency. However, in other embodiments, the control of the two rotating shafts and impellers can employ other control strategies based on the specific structure of the impellers and pumping requirements.

[0086] In some embodiments, the first rotating shaft 170 and the second rotating shaft 180 are coaxially arranged to simplify the structure and control.

[0087] In some embodiments, as shown in FIG14, the Stirling engine 10 further includes a first throttling element 190 located between the first impeller 141 and the first heat exchanger 120. This embodiment can reduce the pressure of the working fluid input to the first pressure chamber A1 by the first throttling element 190 located between the first impeller 141 and the first heat exchanger 120, thereby reducing damage to the first heat exchanger 120 and improving the reliability of the Stirling engine 10.

[0088] In some embodiments, the first throttling element 190 includes a first orifice plate, the outer edge of the first orifice plate being sealed to a wall inside the first end, and the first orifice plate having a first flow hole.

[0089] In some embodiments, as shown in FIG14, the Stirling engine 10 further includes a second throttling element 200 located between the second impeller 151 and the second heat exchanger 130. This embodiment can reduce the pressure of the working fluid input from the compressor to the second pressure chamber A2 by using the second throttling element 200 located between the second impeller 151 and the second heat exchanger 130, thereby reducing damage to the second heat exchanger 130 and improving the reliability of the Stirling engine 10.

[0090] In some embodiments, the second throttling element 200 includes a second orifice plate, the outer edge of which is sealed to the wall inside the second end, and the second orifice plate is provided with a second flow hole.

[0091] In some embodiments, a throttling assembly may also be provided outside the housing 110 to reduce the pressure of the working fluid input to the first end and / or the second end of the compressor.

[0092] In some embodiments, a first buffer cavity (not shown) is formed between the side of the first impeller 141 away from the first heat exchanger 120 and the end wall of the first end.

[0093] The first rotating shaft 170 is at least partially located within the first buffer cavity.

[0094] In some embodiments, a second buffer cavity (not shown) is formed between the side of the second impeller 151 away from the second heat exchanger 130 and the end wall of the second end.

[0095] The second rotating shaft 180 is at least partially located within the first buffer cavity.

[0096] The first and second buffer chambers are used to adjust the phase of the pressure wave and the velocity wave. For example, when the first pressure chamber A1 is connected to the exhaust port 21 of the compressor 20 and the second pressure chamber A2 is connected to the intake port 22 of the compressor 20, the pressure in the first pressure chamber A1 and the second pressure chamber A2 is adjusted to form a pressure waveform, thereby improving the pumping efficiency.

[0097] This application further proposes a heat pump system. In some embodiments, as shown in FIG15, the heat pump system (not shown) includes a Stirling engine 10 and a compressor. The Stirling engine 10 includes a housing 110, a first heat exchanger 120, a second heat exchanger 130, a regenerator 160, a first switching assembly 140, and a second switching assembly 150. The housing 110 has a receiving cavity (not shown). The cavity wall at the first end of the receiving cavity has a first air inlet (not shown) and a first exhaust port (not shown). The cavity wall at the second end of the receiving cavity has a second air inlet (not shown) and a second exhaust port (not shown). The first air inlet and the second air inlet are connected to the exhaust port 21 of the compressor 20, and the first exhaust port and the second exhaust port are connected to the suction port 22 of the compressor 20. The first heat exchanger 120 is disposed within the first end. The second heat exchanger 130... 0 is located in the second end; the regenerator 160 is located in the receiving cavity and is located between the first heat exchanger 120 and the second heat exchanger 130; the first switch assembly 140 is located in the first end and is located on the side of the first heat exchanger 120 away from the regenerator 160. The first switch assembly 140 is configured to selectively connect the first air inlet or the first exhaust port to the first pressure chamber A1 (not shown in the figure) located on the side of the first switch assembly 140 facing the first heat exchanger 120, so as to adjust the pressure of the first pressure chamber A1; the second switch assembly 150 is located in the second end and is located on the side of the second heat exchanger 130 away from the regenerator 160. The second switch assembly 150 is configured to selectively connect the second air inlet or the second exhaust port to the second pressure chamber A2 (not shown in the figure) located on the side of the second switch assembly 150 facing the second heat exchanger 130, so as to adjust the pressure of the second pressure chamber A2.

[0098] On the one hand, this embodiment utilizes the first switching assembly 140 to switch the compressor on and off to supply or discharge working fluid to the first pressure chamber A1, thereby regulating the pressure within the first pressure chamber A1. Similarly, the second switching assembly 150 utilizes the second switching assembly 150 to switch the compressor 20 on and off to supply or discharge working fluid to the second pressure chamber A2, thereby regulating the pressure within the second pressure chamber A2. Therefore, the combined use of the first switching assembly 140 and the second switching assembly 150 enables alternating motion of the working fluid between the first and second ends of the containment chamber, thus creating a temperature gradient in the regenerator 160 and achieving heat pumping from the low-temperature end to the high-temperature end. On the other hand, compared to existing methods that achieve heat pumping through the axial reciprocating motion of a piston relative to a piston cylinder, this embodiment achieves heat pumping through the aforementioned switching assembly. This switching assembly has high operating efficiency, improving the mechanical efficiency of the Stirling engine 10 and enhancing the sealing performance between the moving parts, i.e., the switching assembly and the housing 110. Therefore, this embodiment improves the heat pumping efficiency and reliability of the Stirling engine 10 and the heat pump system.

[0099] In some embodiments, compressor 20 includes a rotary compressor. Rotary compressors have advantages such as high mechanical efficiency and energy saving, thus improving the efficiency of the heat pump system.

[0100] In some embodiments, the rotary compressor may be a rotary compressor such as a rotor, scroll, or centrifugal compressor, which has a higher mechanical efficiency than a traditional reciprocating piston compressor.

[0101] For information on the Stirling engine 10 and its cooperation with the compressor 20, please refer to the above embodiments.

[0102] In some embodiments, as shown in FIG16, the heat pump system further includes a first medium-temperature heat exchanger 30, connected between the exhaust port 21 of the compressor 20 and the second intake port. In this embodiment, the first medium-temperature heat exchanger 30 cools the working fluid output from the compressor 20 to the second pressure chamber A2, i.e., the cold end, to achieve a temperature gradient between the working fluid in the first pressure chamber A1 and the working fluid in the second pressure chamber A2, thereby improving the pump heat efficiency.

[0103] In some embodiments, as shown in FIG16, the heat pump system further includes a second intermediate-temperature heat exchanger 40 connected between the suction port 22 of the compressor 20 and the first discharge port. The second intermediate-temperature heat exchanger 40 is used to reduce the temperature of the exhaust gas at the second discharge port, i.e., the hot end, and then return it to the compressor 20 to improve the efficiency of the compressor 20.

[0104] In some embodiments, as shown in FIG17, the heat pump system further includes a first throttling element 51 and a first buffer tank 52, both disposed outside the housing 110 and connected in series between the exhaust port 21 of the compressor 20 and the housing 110. In this embodiment, the first throttling element 51 and the first buffer tank 52 are used to reduce the pressure of the working fluid output by the compressor 20, so that the reduced-pressure working fluid is delivered to the first pressure chamber A1.

[0105] In some embodiments, as shown in FIG17, the heat pump system further includes a second throttling element 61 and a second buffer tank 62, both disposed outside the housing 110 and connected in series between the suction port 22 of the compressor 20 and the housing 110. In this embodiment, the second throttling element 61 and the second buffer tank 62 are provided on the suction port 22 side of the compressor 20, which can regulate the flow rate and pressure of the compressor 20 and ensure the normal operation of the heat pump system.

[0106] In some embodiments, the throttling element may include a capillary tube, an expansion valve, an orifice plate, etc. (Example from this application).

[0107] The Stirling engine provided in this application includes a first heat exchanger, a second heat exchanger, a regenerator, a first switching assembly, and a second switching assembly disposed within a housing cavity formed by the casing. The housing cavity has a first inlet and a first outlet on its first end wall, and a second inlet and a second outlet on its second end wall. The first and second inlets are configured to connect to the exhaust ports of the compressor, and the first and second exhaust ports are configured to connect to the suction ports of the compressor. The first heat exchanger is disposed within the first end, the second heat exchanger is disposed within the second end, and the regenerator is disposed within the housing cavity and located at the first... Between the heat exchanger and the second heat exchanger; a first switching assembly is disposed in the first end and located on the side of the first heat exchanger away from the regenerator, the first switching assembly is configured to selectively connect the first air inlet or the first exhaust port to the first pressure chamber located on the side of the first switching assembly facing the first heat exchanger, so as to adjust the pressure of the first pressure chamber; a second switching assembly is disposed in the second end and located on the side of the second heat exchanger away from the regenerator, the second switching assembly is configured to selectively connect the second air inlet or the second exhaust port to the second pressure chamber located on the side of the second switching assembly facing the second heat exchanger, so as to adjust the pressure of the second pressure chamber. In this way, on the one hand, this application utilizes a first switching assembly to switch the compressor on and off to supply or discharge working fluid to the first pressure chamber, thereby regulating the pressure within the first pressure chamber. Similarly, it utilizes a second switching assembly to switch the compressor on and off to supply or discharge working fluid to the second pressure chamber, thus regulating the pressure within the second pressure chamber. Therefore, the combined use of the first and second switching assemblies enables alternating motion of the working fluid between the first and second ends of the chamber, thereby creating a temperature gradient in the regenerator and achieving heat pumping from the low-temperature end to the high-temperature end. On the other hand, compared to existing methods that achieve heat pumping through the axial reciprocating motion of a piston relative to a piston cylinder, this application achieves heat pumping through a switching assembly. The switching assembly has high operating efficiency, improving the mechanical efficiency of the Stirling engine and enhancing the sealing between the moving parts, i.e., the switching assembly and the housing. Therefore, this application can improve the heat pumping efficiency and reliability of the Stirling engine.

[0108] Furthermore, the heat pump system of this application uses a rotary compressor, which has higher mechanical efficiency than a reciprocating piston compressor, a wider adjustable range, and adjustable compressor frequency and rotor speed. Moreover, the heat pump system of this application is simple, efficient, highly reliable, and has a long service life; this application eliminates the crankshaft drive mechanism, resulting in a more compact and lightweight overall structure and higher mechanical efficiency.

[0109] The above are merely embodiments of this application and do not limit the patent scope of this application. Any equivalent structural or procedural transformations made using the content of this application's specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of this application.

Claims

1. A Stirling engine, wherein, The Stirling engine includes: The housing has a receiving cavity. The cavity wall at the first end of the receiving cavity has a first air inlet and a first air outlet. The cavity wall at the second end of the receiving cavity has a second air inlet and a second air outlet. The first air inlet and the second air inlet are configured to communicate with the exhaust port of the compressor. The first exhaust port and the second exhaust port are configured to communicate with the intake port of the compressor. The first heat exchanger is located inside the first end; The second heat exchanger is located inside the second end; A regenerator is disposed within the receiving cavity and located between the first heat exchanger and the second heat exchanger; A first switching assembly is disposed within the first end and located on the side of the first heat exchanger away from the regenerator. The first switching assembly is configured to selectively connect the first air inlet or the first exhaust outlet to a first pressure chamber located on the side of the first switching assembly facing the first heat exchanger, so as to adjust the pressure of the first pressure chamber. A second switching assembly is disposed within the second end and located on the side of the second heat exchanger away from the regenerator. The second switching assembly is configured to selectively connect the second air inlet or the second exhaust outlet to a second pressure chamber located on the side of the second switching assembly facing the second heat exchanger, so as to adjust the pressure of the second pressure chamber.

2. The Stirling engine according to claim 1, wherein, The first switching assembly includes a first rotating wheel, which is sealed to the inner wall of the first end and rotatably disposed thereon; the first rotating wheel is provided with a first flow channel communicating with the first pressure chamber on the side near the first heat exchanger, and the first flow channel extends to the first outer peripheral wall of the first rotating wheel to form a first air port communicating with the first flow channel on the first outer peripheral wall; when the first rotating wheel rotates relative to the first pressure chamber, it selectively connects the first air port with the first air inlet or the first exhaust port; The second switching assembly includes a second rotating wheel, which is sealed to the inner wall of the second end and rotatably disposed thereon; the second rotating wheel is provided with a second flow channel communicating with the second pressure chamber on the side near the second heat exchanger, and the second flow channel extends to the second outer peripheral wall of the second rotating wheel to form a second air port communicating with the second flow channel on the second outer peripheral wall; when the second rotating wheel rotates relative to the second pressure chamber, it selectively connects the second air port with the second air inlet or the second exhaust port.

3. The Stirling engine according to claim 2, wherein, The first air inlet and the first exhaust outlet are arranged along the diameter direction of the first rotor; The second air inlet and the second exhaust outlet are arranged along the diameter of the second rotor.

4. The Stirling engine according to claim 3, wherein, The dimension of the first flow channel along the circumference of the first impeller is half the circumference of the first impeller; The dimension of the second flow channel along the circumference of the second impeller is half the circumference of the second impeller.

5. The Stirling engine according to claim 4, wherein, The first flow channel is semi-circular in shape; The second flow channel is arranged in a semi-circular shape.

6. The Stirling engine according to claim 4, wherein, The first and second rotating wheels are configured to rotate in the same direction and at the same speed; During rotation, the phase difference between the first flow channel and the second flow channel is 90°.

7. The Stirling engine according to claim 6, wherein, During rotation, the first flow channel leads the second flow channel along the direction of rotation.

8. The Stirling engine according to claim 1, wherein, The working stages of the Stirling heat engine include: isothermal compression stage, isochoric cooling stage, isothermal expansion stage, and isochoric heating stage. The first pressure chamber and the second pressure chamber are respectively connected to the exhaust port of the compressor, and the Stirling engine is in the isothermal compression stage; The first pressure chamber is connected to the exhaust port of the compressor, and the second pressure chamber is connected to the intake port of the compressor, and the Stirling engine is in the isochoric cooling stage; The first pressure chamber and the second pressure chamber are respectively connected to the suction port of the compressor, and the Stirling engine is in the isothermal expansion stage; The first pressure chamber is connected to the suction port of the compressor, and the second pressure chamber is connected to the discharge port of the compressor, and the Stirling engine is in the isochoric heating stage.

9. The Stirling engine according to any one of claims 2 to 8, wherein, The Stirling engine also includes: A first rotating shaft is connected to the first rotating wheel and configured to drive the first rotating wheel to rotate relative to the housing; The second rotating shaft is connected to the second rotating wheel and is configured to drive the second rotating wheel to rotate relative to the housing.

10. The Stirling engine according to any one of claims 2 to 8, wherein, The Stirling engine also includes: The first throttling element is located between the first impeller and the first heat exchanger; The second throttling element is located between the second impeller and the second heat exchanger.

11. The Stirling engine according to any one of claims 1 to 8, wherein, A first buffer cavity is formed between the side of the first impeller away from the first heat exchanger and the end wall of the first end; A second buffer cavity is formed between the side of the second impeller away from the second heat exchanger and the end wall of the second end.

12. A heat pump system, wherein, The heat pump system includes: The Stirling engine as described in any one of claims 1 to 11; The compressor has its exhaust port connected to the first air inlet and the second air inlet, and its suction port connected to the first exhaust port and the second exhaust port.

13. The heat pump system according to claim 12, wherein, The compressor includes a rotary compressor.

14. The heat pump system according to claim 12, wherein, The heat pump system also includes: A first medium-temperature heat exchanger is connected between the exhaust port and the second intake port of the compressor.

15. The heat pump system according to claim 12, wherein, The heat pump system also includes: The second medium-temperature heat exchanger is connected between the suction port and the first discharge port of the compressor.

16. The heat pump system according to claim 12, wherein, The heat pump system also includes: The first throttling element and the first buffer tank are both located outside the housing and connected in series between the compressor's exhaust port and the housing; The second throttling element and the second buffer tank are both located outside the housing and connected in series between the compressor's intake port and the housing.

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