CO2 heat pump system

Abstract

The invention relates to the technical field of air conditioners, in particular to a CO2 heat pump system. The invention aims to solve the problems that the CO2 heat pump system is repeatedly provided with the gas-liquid separator, the functions are superposed, and the reliability and the service life are influenced by removing the gas-liquid separator of the compressor. In order to achieve the purpose, the heat pump system comprises a compressor, a reversing valve, a heat regenerator, an ejector, a gas-liquid separator, a first throttling element and a first indoor heat exchanger, a second port of an outdoor heat exchanger communicates with a first port of the heat regenerator, and an inlet of the ejector communicates with a second port of the heat regenerator; a third port of the heat regenerator is communicated with a third connector of the reversing valve, a fourth port of the heat regenerator is communicated with an air suction port of the compressor, and an exhaust port of the gas-liquid separator is communicated with a fourth connector of the reversing valve. On the premise that the compressor is not provided with a gas-liquid separator, the heat regenerator is used for reheating the refrigerant flowing back to the compressor, it is guaranteed that air sucked by the compressor does not carry liquid, and the operation stability and reliability of the compressor are improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air conditioning, and in particular to a CO2 heat pump system. Background Art

[0002] CO2 (carbon dioxide), as a new environmentally friendly refrigerant, has become a research hotspot in the heat pump industry. The advantages and disadvantages of heat pump systems using CO2 as refrigerant are equally obvious. Its advantage is that the heating performance is generally better than that of traditional heat pumps, and its disadvantage is that the cooling efficiency is poor. Therefore, how to improve the cooling efficiency has always been an important reason hindering the promotion of CO2 heat pump systems.

[0003] In response to this problem, the invention patent with announcement number CN113203136B proposed a solution. The invention patent adopts the ejector expansion work recovery technology to greatly improve the energy efficiency of the CO2 heat pump system, and adopts a dual-temperature evaporator to further improve the energy efficiency. However, this heat pump system needs to be equipped with a gas-liquid separator to achieve dual-temperature evaporation. In actual operation, the function of the gas-liquid separator and the compressor's built-in gas-liquid separator overlap, resulting in an increase in the system refrigerant charge, a deterioration in the compressor's oil return effect, and other problems. Removing the compressor's built-in gas-liquid separator may cause the compressor to inhale liquid, thereby affecting its reliability and life.

[0004] Accordingly, the art needs a new technical solution to solve the above problems. Summary of the invention

[0005] In order to solve at least one of the above problems in the prior art, that is, to solve the problem that the CO2 heat pump system repeatedly sets up a gas-liquid separator, there is functional overlap, the refrigerant filling amount increases, and the removal of the gas-liquid separator provided by the compressor affects the reliability and life of the compressor, the present application provides a CO2 heat pump system, which includes:

[0006] compressor;

[0007] A reversing valve, the reversing valve comprising a first interface, a second interface, a third interface and a fourth interface, the first interface being in communication with an exhaust port of the compressor;

[0008] An outdoor heat exchanger, wherein a first port of the outdoor heat exchanger is in communication with a second port of the reversing valve;

[0009] A regenerator, the regenerator having a first port, a second port, a third port and a fourth port, a first heat exchange flow path formed between the first port and the second port of the regenerator, a second heat exchange flow path formed between the third port and the fourth port of the regenerator, the second port of the outdoor heat exchanger is communicated with the first port of the regenerator, the third port of the regenerator is communicated with the third interface of the reversing valve, and the fourth port of the regenerator is communicated with the suction port of the compressor;

[0010] An injector, the inlet of which is communicated with the second port of the regenerator;

[0011] A gas-liquid separator, the inlet of which is communicated with the outlet of the injector, and the exhaust port of which is communicated with the fourth interface of the reversing valve;

[0012] A first throttling element, the first port of which is communicated with the liquid discharge port of the gas-liquid separator;

[0013] A first indoor heat exchanger, the first port of which is communicated with the second port of the first throttling element, and the second port of which is communicated with the ejector port of the injector.

[0014] The above technical solution can reheat the refrigerant flowing back to the compressor by using the regenerator on the premise that the compressor is not equipped with a gas-liquid separator, ensure that the compressor sucks in without liquid, and improve the operation stability and reliability of the compressor. Moreover, the above setting method can also reduce the process of primary gas-liquid separation, reduce the refrigerant charge amount, and greatly improve the problem of oil accumulation in the gas-liquid separator.

[0015] In a preferred technical solution of the above heat pump system, the heat pump system further includes a second throttling element, and the two ports of the second throttling element are respectively communicated with the second port of the outdoor heat exchanger and the first port of the regenerator.

[0016] The above technical solution can throttle the refrigerant after flowing through the regenerator in the heating mode, and improve the heat regeneration effect of the regenerator.

[0017] In a preferred technical solution of the above heat pump system, the maximum opening degree of the second throttling element is greater than the maximum opening degree of the first throttling element.

[0018] The above setting method can avoid the influence on the heat regeneration effect in the cooling mode due to the too small opening degree of the second throttling element.

[0019] In a preferred technical solution of the above heat pump system, a first valve body is arranged on the pipeline between the second port of the outdoor heat exchanger and the first port of the regenerator. The heat pump system further includes a bypass pipeline, the first end of which is communicated between the second port of the outdoor heat exchanger and the first valve body, and the second end of which is communicated between the first valve body and the first port of the regenerator. The second throttling element is arranged on the bypass pipeline.

[0020] The above setting method can realize different flow paths in the cooling and heating modes by setting the bypass pipeline and the first valve body, and ensure that the regenerator has good effects in both the cooling and heating modes.

[0021] In the preferred technical solution of the above heat pump system, a first drying filter is further provided on the bypass pipeline, and the first drying filter is located between the second throttling element and the second end of the bypass pipeline.

[0022] With the above arrangement, by providing the first drying filter, the phenomenon of ice blockage during the throttling process can be avoided.

[0023] In the preferred technical solution of the above heat pump system, a second valve body is further provided on the bypass pipeline, and the second valve body is located between the second throttling element and the first end of the bypass pipeline.

[0024] In the preferred technical solution of the above heat pump system, the first valve body is a check valve, and the first valve body is arranged to be conductive when the refrigerant flows between the second port of the outdoor heat exchanger and the first port of the regenerator; and / or

[0025] The second valve body is a check valve, and the second valve body is arranged to be conductive when the refrigerant flows from the second end to the first end of the bypass pipeline.

[0026] In the preferred technical solution of the above heat pump system, the heat pump system further includes a second drying filter, and the second drying filter is arranged between the liquid discharge port of the gas-liquid separator and the first throttling element.

[0027] With the above arrangement, by providing the second drying filter, the phenomenon of "ice blockage" during the throttling process can be avoided.

[0028] In the preferred technical solution of the above heat pump system, the heat pump system further includes a second indoor heat exchanger, the first port of the second indoor heat exchanger is communicated with the outlet of the ejector, and the second port of the second indoor heat exchanger is communicated with the inlet of the gas-liquid separator.

[0029] In the preferred technical solution of the above heat pump system, between the second port of the first indoor heat exchanger and the second port of the second indoor heat exchanger, there is a first branch pipe with a third valve body connected, and between the second port of the second indoor heat exchanger and the second port of the regenerator, there is a second branch pipe with a fourth valve body connected.

[0030] With the above arrangement, during the heating process, the refrigerant can bypass the ejector, thereby achieving efficient heating of the heat pump system. Description of the Drawings

[0031] The present application will be described below with reference to the drawings. In the drawings:

[0032] Figure 1 is the system diagram of the CO2 heat pump system of the present application.

[0033] List of Reference Signs

[0034] 1. Compressor; 2. Reversing valve; 3. Outdoor heat exchanger; 4. Regenerator; 5. Injector; 6. Gas-liquid separator; 7. First throttling element; 8. First indoor heat exchanger; 9. Second indoor heat exchanger; 10. Second throttling element; 11. First valve body; 12. First dryer filter; 13. Second valve body; 14. Second dryer filter; 15. Third valve body; 16. Fourth valve body; 17. Fifth valve body; 18. Sixth valve body; 19. Seventh valve body; 20. Eighth valve body; 21. Bypass pipeline; 22. First branch pipe; 23. Second branch pipe. Detailed implementation manners

[0035] The preferred implementation manners of the present application will be described below with reference to the accompanying drawings. Those skilled in the art should understand that these implementation manners are only used to explain the technical principle of the present application and are not intended to limit the protection scope of the present application. For example, although the description in the accompanying drawings is based on the example of combining the first indoor heat exchanger and the second indoor heat exchanger, this setting method is not fixed. Those skilled in the art can adjust it according to needs to adapt to specific application scenarios. For example, the second indoor heat exchanger can be omitted, or more indoor heat exchangers can be added to the system, etc.

[0036] It should be noted that in the description of the present application, the terms indicating the direction or position relationship such as "upper", "lower", "left", "right", etc. are based on the direction or position relationship shown in the accompanying drawings. This is only for the convenience of description and does not indicate or imply that the device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present application. In addition, the terms "first", "second", "third", "fourth", "fifth", "sixth", "seventh", "eighth" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance. In addition, in the description of the present application, "a plurality of" means at least two.

[0037] In addition, it should also be noted that in the description of the present application, unless otherwise clearly specified and limited, the terms "communicate", "be connected", "connect" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the communication inside two elements. For those skilled in the art, the specific meanings of the above terms in the present application can be understood according to specific situations.

[0038] First, refer to Figure 1 , and describe the CO2 heat pump system of the present application.

[0039] AsFigure 1 As shown, in order to solve the problem that the CO2 heat pump system repeatedly sets up gas-liquid separators, which results in overlapping functions and increased refrigerant filling, and the removal of the compressor's own gas-liquid separator affects the compressor's reliability and life, the CO2 heat pump system of the present application includes a compressor 1, a reversing valve 2, an outdoor heat exchanger 3, a regenerator 4, an ejector 5, a gas-liquid separator 6, a first throttling element 7 and a first indoor heat exchanger 8. The compressor 1 is not equipped with a separate gas-liquid separation device, and the reversing valve 2 includes a first interface a, a second interface b, a third interface c and a fourth interface d. The first interface a is connected to the exhaust port of the compressor 1, and the second interface b is connected to the first port ( Figure 1 The regenerator 4 has a first port, a second port, a third port and a fourth port. The first port ( Figure 1 The upper left port) and the second port ( Figure 1 The first heat exchange flow path is formed between the lower left port of the middle heat exchanger 4, and the third port ( Figure 1 The lower right port) and the fourth port ( Figure 1 The second heat exchange flow path is formed between the first port of the regenerator 4 and the second port of the outdoor heat exchanger 3 ( Figure 1 The left port in the middle is connected, the second port of the regenerator 4 is connected to the inlet of the ejector 5, the third port of the regenerator 4 is connected to the third interface c of the reversing valve 2, and the fourth port of the regenerator 4 is connected to the suction port of the compressor 1.

[0040] The outlet of the ejector 5 is connected to the inlet of the gas-liquid separator 6, the exhaust port of the gas-liquid separator 6 is connected to the fourth interface d of the reversing valve 2, and the discharge port of the gas-liquid separator 6 is connected to the first port ( Figure 1 The second port of the first throttling element 7 ( Figure 1 The left side port in the middle) and the first port of the first indoor heat exchanger 8 ( Figure 1 The right side port in the middle is connected to the second port of the first indoor heat exchanger 8 ( Figure 1 The left side port in the middle is connected with the injection port of the injector 5.

[0041] Taking refrigeration operation as an example, during operation, the refrigerant discharged from the compressor 1 passes through the first interface a and the second interface b of the reversing valve 2 and enters the outdoor heat exchanger 3 to exchange heat with the outdoor air. After the heat exchange is completed, the refrigerant enters the first heat exchange flow path of the regenerator 4 to exchange heat with the refrigerant in the second heat exchange flow path. The refrigerant discharged from the regenerator 4 enters the ejector 5 from the inlet of the ejector 5 and is ejected from the outlet of the ejector 5 into the gas-liquid separator 6. The refrigerant entering the gas-liquid separator 6 is divided into two paths, wherein the gaseous refrigerant is discharged from the exhaust port of the gas-liquid separator 6, and enters the second heat exchange flow path of the regenerator 4 after passing through the fourth interface d and the third interface c of the reversing valve 2 to exchange heat with the first heat exchange flow path, remove excess liquid refrigerant, and finally flows back to the compressor 1 from the air intake of the compressor 1. The liquid refrigerant in the gas-liquid separator 6 enters the first indoor heat exchanger 8 to exchange heat with the indoor air after throttling and reducing the pressure by the first throttling element 7. The refrigerant after heat exchange flows back to the ejector 5 through the injection port of the ejector 5, mixes with the refrigerant in the ejector 5 and continues to participate in the circulation.

[0042] The above technical solution can reheat the refrigerant returning to the compressor 1 by using the regenerator 4 without configuring the gas-liquid separator 6 in the compressor 1, thereby ensuring that the compressor 1 does not inhale liquid and improving the operational stability and reliability of the compressor 1. Moreover, the above arrangement can also reduce the gas-liquid separation process once, reduce the refrigerant charge amount, and greatly improve the problem of oil storage in the gas-liquid separator 6.

[0043] The following further combines Figure 1 , the preferred implementation modes of the present application are introduced.

[0044] like Figure 1 As shown, in a preferred embodiment, the CO2 heat pump system includes a compressor 1, a reversing valve 2, an outdoor heat exchanger 3, a regenerator 4, an ejector 5, a gas-liquid separator 6, a first throttling element 7, a second throttling element 10, a first indoor heat exchanger 8, a second indoor heat exchanger 9, a first drying filter 12 and a second drying filter 14.

[0045] The exhaust port of the compressor 1 is connected to the first interface a of the reversing valve 2, and the second interface b of the reversing valve 2 is connected to the first port of the outdoor heat exchanger 3. The second port of the outdoor heat exchanger 3 is connected to the first port of the regenerator 4, and a first valve body 11 is provided on the connecting pipeline between the two. The first valve body 11 is a one-way valve in the present application, and the one-way valve is turned on when the refrigerant flows from the second end of the outdoor heat exchanger 3 to the first port of the regenerator 4. A bypass pipeline 21 is also provided between the second port of the outdoor heat exchanger 3 of the heat pump system and the first port of the regenerator 4. The first end ( Figure 1 The second end (right end) is connected to the second port of the outdoor heat exchanger 3 and the first valve body 11, and the second end ( Figure 1The left-middle end is connected between the first valve body 11 and the first port of the regenerator 4. The second throttling element 10 and the first dryer filter 12 are both arranged on the bypass pipeline 21. A first dryer filter 12 is also arranged on the bypass pipeline 21, and the first dryer filter 12 is located between the second throttling element 10 and the second end of the bypass pipeline 21. In addition, a second valve body 13 is arranged on the bypass pipeline 21, and the second valve body 13 is located between the second throttling element 10 and the first end of the bypass pipeline 21. Preferably, the second throttling element 10 is an electronic expansion valve, and the second valve body 13 is a check valve, and the check valve is conducted when the refrigerant flows from the second end to the first end of the bypass pipeline 21.

[0046] Continue to refer to Figure 1 The second port of the regenerator 4 is connected to the inlet of the ejector 5, and a fifth valve body 17 is arranged on the pipeline therebetween. The fifth valve body 17 is a check valve, and the check valve is conducted when the refrigerant flows from the second port of the regenerator 4 to the inlet of the ejector 5. The outlet of the ejector 5 is connected to the first port of the second indoor heat exchanger 9, and a sixth valve body 18 is arranged between the outlet of the ejector 5 and the first port of the second indoor heat exchanger 9. The sixth valve body 18 is a check valve, and the check valve is conducted when the refrigerant flows from the outlet of the ejector 5 to the first port of the second indoor heat exchanger 9. The second port of the second indoor heat exchanger 9 is connected to the inlet of the gas-liquid separator 6, and a seventh valve body 19 is arranged between the second port of the second indoor heat exchanger 9 and the inlet of the gas-liquid separator 6. The seventh valve body 19 is a check valve, and the check valve is conducted when the refrigerant flows from the second port of the second indoor heat exchanger 9 to the inlet of the gas-liquid separator 6.

[0047] The exhaust port of the gas-liquid separator 6 is connected to the fourth interface d of the reversing valve 2, the third interface c of the reversing valve 2 is connected to the third port of the regenerator 4, and the fourth port of the regenerator 4 is connected to the suction port of the compressor 1. The liquid discharge port of the gas-liquid separator 6 is connected to the first port of the second dryer filter 14, the second port of the second dryer filter 14 is connected to the first port of the first throttling element 7, the second port of the first throttling element 7 is connected to the first port of the first indoor heat exchanger 8, the second port of the first indoor heat exchanger 8 is connected to the injection port of the ejector 5, and an eighth valve body 20 is arranged between the second port of the first indoor heat exchanger 8 and the injection port of the ejector 5. The eighth valve body 20 is a solenoid valve.

[0048] The second port of the first indoor heat exchanger 8 is communicated with the second port of the second indoor heat exchanger 9 through a first branch pipe 22 with a third valve body 15. The first end of the first branch pipe 22 is communicated between the second port of the first indoor heat exchanger 8 and the eighth valve body 20, and the second end is communicated between the second port of the second indoor heat exchanger 9 and the seventh valve body 19. The third valve body 15 is a check valve, and the check valve is opened when the refrigerant flows from the first end to the second end of the first branch pipe 22. The second port of the second indoor heat exchanger 9 is communicated with the second port of the regenerator 4 through a second branch pipe 23 with a fourth valve body 16. The first end of the second branch pipe 23 is communicated between the sixth valve body 18 and the first port of the second indoor heat exchanger 9, and the second end is communicated between the second port of the regenerator 4 and the fifth valve body 17. The fourth valve body 16 is a check valve, and the check valve is opened when the refrigerant flows from the first end to the second end of the second branch pipe 23.

[0049] The working principle of the CO2 heat pump system of the present application will be described below in conjunction with Figure 1 .

[0050] As Figure 1 shown, when the CO2 heat pump system operates in the refrigeration mode, the first throttling element 7 is opened to a preset opening degree, and the eighth valve body 20 is opened. The refrigerant discharged from the compressor 1 enters the outdoor heat exchanger 3 through the first interface a and the second interface b of the reversing valve 2 and exchanges heat with the outdoor air. After the heat exchange is completed, the refrigerant enters the regenerator 4 and exchanges heat with the refrigerant in the first heat exchange flow path and the second heat exchange flow path. The refrigerant discharged from the regenerator 4 enters the ejector 5 from the inlet of the ejector 5 and is ejected from the outlet of the ejector 5 to the second indoor heat exchanger 9 for primary heat exchange with the indoor air. The refrigerant after the heat exchange enters the gas-liquid separator 6. The refrigerant entering the gas-liquid separator 6 is divided into two paths. The gaseous refrigerant is discharged from the exhaust port of the gas-liquid separator 6, and after passing through the fourth interface d and the third interface c of the reversing valve 2, it enters the second heat exchange flow path of the regenerator 4 for heat exchange with the first heat exchange flow path to remove the excess liquid refrigerant, and finally returns to the compressor 1 from the suction port of the compressor 1. The liquid refrigerant in the gas-liquid separator 6 is throttled and depressurized by the first throttling element 7 after passing through the second drying filter 14. The refrigerant after the throttling and depressurization enters the first indoor heat exchanger 8 for secondary heat exchange with the indoor air. The refrigerant after the heat exchange returns to the ejector 5 through the injection port of the ejector 5, mixes with the refrigerant in the ejector 5, and continues to participate in the cycle.

[0051] When the CO2 heat pump system operates in the heating mode, the first throttling element 7 is fully open, the second throttling element 10 is opened to a set opening degree, the eighth valve body 20 is closed, and the reversing valve 2 reverses. The refrigerant discharged from the compressor 1 enters the gas-liquid separator 6 through the exhaust port of the gas-liquid separator 6 after passing through the first interface a and the fourth interface d of the reversing valve 2. All the refrigerant entering the gas-liquid separator 6 is discharged through the drain port, and after passing through the second drying filter 14 and the first throttling element 7, it enters the first indoor heat exchanger 8 to exchange heat with indoor air for the first time. The refrigerant after heat exchange enters the second indoor heat exchanger 9 through the first branch to exchange heat with indoor air for the second time. The refrigerant after heat exchange enters the first heat exchange flow path of the regenerator 4 through the second branch and exchanges heat with the refrigerant in the second heat exchange flow path. The refrigerant discharged from the first heat exchange flow path of the regenerator 4 is dried by the first drying filter 12 on the bypass pipeline 21 and then enters the second throttling element 10 for throttling and pressure reduction. The refrigerant after throttling and pressure reduction exchanges heat with outdoor air through the outdoor heat exchanger 3, and then enters the second heat exchange flow path of the regenerator 4 through the second interface b and the third interface c of the reversing valve 2 to exchange heat with the first heat exchange flow path to remove excess liquid refrigerant, and finally returns to the compressor 1 through the suction port of the compressor 1.

[0052] In the above preferred embodiments, the regenerator 4 can be used to reheat the refrigerant flowing back during refrigeration or heating. For example, it can ensure that the refrigerant returns to the compressor 1 without liquid, improving the operation stability and reliability of the compressor 1. By setting the second throttling element 10, the refrigerant can be throttled after flowing through the regenerator 4 in the heating mode, improving the heat regeneration effect of the regenerator 4. By setting the bypass pipeline 21 and the first valve body 11, different flow paths in the refrigeration and heating modes can be realized, ensuring that the regenerator 4 has good effects in both the refrigeration and heating modes. By setting the first drying filter 12 and the second drying filter 14, the phenomenon of ice blockage during throttling can be avoided. By setting the first branch and the second branch, the refrigerant can bypass the ejector 5 during the heating process, thus realizing the high-efficiency heating of the heat pump system.

[0053] Of course, the above preferred embodiments are only used to illustrate the principle of the present application and are not intended to limit the protection scope of the present application. Without departing from the principle of the present application, those skilled in the art can adjust the above settings so that the present application can be applied to more specific application scenarios.

[0054] For example, in an alternative embodiment, the setting of the second throttling element 10 is not necessary, and those skilled in the art can choose whether to set the second throttling element 10 based on specific application scenarios. For example, when the heat pump system is only used for refrigeration, the setting of the second throttling element 10 can be omitted.

[0055] For another example, in an alternative embodiment, the installation position of the second throttling element 10 is not fixed. On the premise that refrigerant throttling can be achieved, its installation position can be adjusted. For example, the bypass pipeline 21 can be omitted, and the second throttling element 10 can be directly installed between the second port of the outdoor heat exchanger 3 and the first port of the regenerator 4. Further, in this case, to prevent the second throttling element 10 from obstructing refrigerant flow, a second throttling element 10 with a larger specification can be selected during model selection, that is, the maximum opening degree of the second throttling element 10 is greater than the maximum opening degree of the first throttling element 7. In this way, during the refrigeration operation, the refrigerant throttling can be avoided by adjusting the opening degree of the second throttling element 10, thereby affecting the heat exchange effect of the regenerator 4.

[0056] For another example, in another alternative embodiment, the installation of the first valve body 11 is not necessary. Those skilled in the art can also selectively cancel the installation of this valve body and instead use the second throttling element 10 to achieve the on-off function of the bypass pipeline 21.

[0057] For another example, in another alternative embodiment, the installation of the first dryer filter 12 and the second dryer filter 14 is not unique. Those skilled in the art can also selectively cancel the installation of at least one of them, and such a change does not deviate from the principle of this application.

[0058] For another example, in another alternative embodiment, the installation of the second indoor heat exchanger 9 is only preferred. Those skilled in the art can choose whether to install the second indoor heat exchanger 9 based on the specific application scenario. In the case of not installing the second indoor heat exchanger 9, the outlet of the ejector 5 can be directly connected to the inlet of the gas-liquid separator 6.

[0059] For another example, in an alternative embodiment, the installation of the first branch pipe 22 and the second branch pipe 23 is only exemplary. On the premise that normal refrigerant flow can be achieved, those skilled in the art can choose whether to install the first branch pipe 22 and the second branch pipe 23 based on specific requirements. In the case of not installing both, the refrigerant can still circulate through the ejector 5.

[0060] For another example, the specific structural forms of the first valve body 11, the second valve body 13... the eighth valve body 20 in the above embodiments are not unique. Those skilled in the art can replace them as long as the corresponding functions can be achieved. For example, a check valve can be replaced with a solenoid valve or other electrically controlled valves, and a solenoid valve can be replaced with an electronic expansion valve or other electrically controlled valves, etc. In addition, the installation of the first valve body 11, the second valve body 13... the eighth valve body 20 is not necessary either. Under the condition that normal refrigerant circulation can be achieved, those skilled in the art can selectively omit one or more of them.

[0061] Of course, the above-mentioned alternative embodiments, as well as between the alternative embodiments and the preferred embodiments, can also be used in a cross-combination manner, so as to combine new embodiments to be applicable to more specific application scenarios.

[0062] Those skilled in the art can understand that although some of the embodiments described herein include certain features included in other embodiments rather than other features, the combination of features of different embodiments means that it is within the scope of the present application and forms different embodiments. For example, in the claims of the present application, any one of the claimed embodiments can be used in any combination.

[0063] So far, the technical solutions of the present application have been described in conjunction with the preferred embodiments shown in the accompanying drawings. However, it is easy for those skilled in the art to understand that the protection scope of the present application is obviously not limited to these specific embodiments. Without departing from the principle of the present application, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after these changes or substitutions will fall within the protection scope of the present application.

Claims

1. A heat pump system, characterized in that, The heat pump system includes: A compressor; A reversing valve, which includes a first interface, a second interface, a third interface, and a fourth interface, and the first interface is communicated with the exhaust port of the compressor; An outdoor heat exchanger, and a first port of the outdoor heat exchanger is communicated with the second interface of the reversing valve; A regenerator, which has a first port, a second port, a third port, and a fourth port. A first heat exchange flow path is formed between the first port and the second port of the regenerator, and a second heat exchange flow path is formed between the third port and the fourth port of the regenerator. A second port of the outdoor heat exchanger is communicated with the first port of the regenerator, the third port of the regenerator is communicated with the third interface of the reversing valve, and the fourth port of the regenerator is communicated with the suction port of the compressor; An ejector, and an inlet of the ejector is communicated with the second port of the regenerator; A gas-liquid separator, an inlet of the gas-liquid separator is communicated with the outlet of the ejector, and an exhaust port of the gas-liquid separator is communicated with the fourth interface of the reversing valve; A first throttling element, and a first port of the first throttling element is communicated with the liquid discharge port of the gas-liquid separator; A first indoor heat exchanger, a first port of the first indoor heat exchanger is communicated with the second port of the first throttling element, and a second port of the first indoor heat exchanger is communicated with the injection port of the ejector.

2. The heat pump system according to claim 1, characterized in that, The heat pump system further includes a second throttling element, and two ports of the second throttling element are respectively communicated with the second port of the outdoor heat exchanger and the first port of the regenerator.

3. The heat pump system according to claim 2, wherein The maximum opening degree of the second throttling element is greater than the maximum opening degree of the first throttling element.

4. The heat pump system according to claim 2, characterized in that, A first valve body is arranged on the pipeline between the second port of the outdoor heat exchanger and the first port of the regenerator. The heat pump system further includes a bypass pipeline, a first end of the bypass pipeline is communicated between the second port of the outdoor heat exchanger and the first valve body, and a second end is communicated between the first valve body and the first port of the regenerator. The second throttling element is arranged on the bypass pipeline.

5. The heat pump system according to claim 4, characterized in that, A first drying filter is further arranged on the bypass pipeline, and the first drying filter is located between the second throttling element and the second end of the bypass pipeline.

6. The heat pump system according to claim 4, wherein A second valve body is further arranged on the bypass pipeline, and the second valve body is located between the second throttling element and the first end of the bypass pipeline.

7. The heat pump system according to claim 6, characterized in that, The first valve body is a check valve, and the first valve body is arranged to be conductive when the refrigerant flows from the second port of the outdoor heat exchanger to the first port of the regenerator; and / or The second valve body is a check valve, and the second valve body is arranged to be conductive when the refrigerant flows from the second end to the first end of the bypass pipeline.

8. The heat pump system according to claim 1, characterized in that, The heat pump system further includes a second drying filter, and the second drying filter is arranged between the liquid discharge port of the gas-liquid separator and the first throttling element.

9. The heat pump system according to claim 1, characterized in that The heat pump system further includes a second indoor heat exchanger, a first port of the second indoor heat exchanger is communicated with the outlet of the ejector, and a second port of the second indoor heat exchanger is communicated with the inlet of the gas-liquid separator.

10. The heat pump system according to claim 9, characterized in that, The second port of the first indoor heat exchanger is communicated with the second port of the second indoor heat exchanger through a first branch pipe with a third valve body, and the second port of the second indoor heat exchanger is communicated with the second port of the regenerator through a second branch pipe with a fourth valve body.

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