Heat pump system

Abstract

The utility model relates to the technical field of heat pumps, and discloses a heat pump system which comprises a refrigerant circulation loop and a bypass branch, the refrigerant circulation loop is sequentially connected with a compressor, a condenser, a first gas-liquid separator, a throttle valve and an evaporator, the first gas-liquid separator is provided with a refrigerant inlet, a liquid refrigerant outlet and a gaseous refrigerant outlet, and the bypass branch is connected with the compressor. The refrigerant inlet is connected with an outlet of the condenser, the liquid refrigerant outlet and an inlet of the throttling valve are connected with one end of the bypass branch, the gas refrigerant outlet is connected with the other end of the bypass branch, and the other end of the bypass branch is connected with a pipeline between the throttling valve and the evaporator; and the switching mechanism is used for switching on or switching off the bypass branch. By arranging the first gaseous separator and the bypass branch, gaseous refrigerants in the refrigerant circulation loop can bypass the throttling valve and directly enter the evaporator, so that the problem of air blockage of the throttling valve is avoided, and meanwhile, the purpose of defrosting a frost layer on the surface of the evaporator can be achieved.

Description

Technical Field

[0001] This utility model relates to the field of heat pump technology, and in particular to a heat pump system. Background Technology

[0002] The basic working process of a heat pump system includes four main steps: compression, condensation, expansion, and evaporation. As a highly efficient and environmentally friendly energy conversion device, heat pumps can extract heat from low-temperature heat sources and transfer it to high-temperature heat sources, and are widely used in heating and hot water supply.

[0003] However, traditional heat pump systems may encounter the following two problems when operating at low ambient temperatures. First, under the influence of ambient temperature, frost is prone to form on the surface of the evaporator. If the frost is not removed in time, it will hinder heat exchange, reducing the evaporation efficiency of the evaporator and the heating effect of the heat pump system. Second, during the operation of the heat pump system, the refrigerant inside may not be sufficiently subcooled. This causes some refrigerant to flow through the expansion valve in gaseous form, leading to gas blockage in the expansion valve and shortening its service life. Utility Model Content

[0004] The technical problem solved by this utility model is to provide a heat pump system that effectively solves the problem of reduced heating effect caused by frost on the evaporator surface, and the problem of damage to the expansion valve caused by insufficient refrigerant cooling.

[0005] The above-mentioned technical problems are solved by the following technical solutions:

[0006] A heat pump system, comprising:

[0007] The refrigerant circulation loop includes a refrigerant inlet and a bypass branch. The refrigerant circulation loop is sequentially connected to a compressor, a condenser, a first gas-liquid separator, a throttle valve, and an evaporator. The first gas-liquid separator has a refrigerant inlet, a liquid refrigerant outlet, and a gaseous refrigerant outlet. The refrigerant inlet is connected to the outlet of the condenser, and the liquid refrigerant outlet is connected to the inlet of the throttle valve. One end of the bypass branch is connected to the gaseous refrigerant outlet, and the other end is connected to the pipeline between the throttle valve and the evaporator.

[0008] A switching mechanism for turning the bypass branch on or off.

[0009] Compared with the prior art, the heat pump system described in this utility model has the following advantages: By setting a first gas-liquid separator between the condenser and the expansion valve, the gaseous and liquid refrigerants in the refrigerant circulation loop can be separated. Then, by connecting the liquid refrigerant outlet of the first gas-liquid separator to the inlet of the expansion valve and the gaseous refrigerant outlet of the first gas-liquid separator to a bypass branch, the separated gaseous and liquid refrigerants can flow out of the first gas-liquid separator through different paths. This avoids the problem of gas blockage in the expansion valve caused by gaseous refrigerant flowing through it, thereby extending the service life of the expansion valve. Specifically, during the operation of the heat pump system, the expansion valve is in the open state, so the liquid refrigerant in the first gas-liquid separator continuously flows into the expansion valve through the liquid refrigerant outlet to maintain the normal refrigerant circulation process. The gaseous refrigerant remains in the first gas-liquid separator, achieving initial separation from the liquid refrigerant. However, as the gaseous refrigerant continues to accumulate in the first gas-liquid separator, the switching mechanism needs to be activated to allow the gaseous refrigerant in the first gas-liquid separator to bypass the throttle valve and directly enter the evaporator through the gaseous refrigerant outlet and bypass branch. This not only prevents the separated gaseous refrigerant from flowing back into the throttle valve from the liquid refrigerant outlet, thus avoiding air blockage in the throttle valve, but also regulates the pressure inside the first gas-liquid separator, preventing excessive pressure buildup due to excessive gaseous refrigerant accumulation.

[0010] Secondly, by connecting the gaseous refrigerant outlet of the first gas-liquid separator to a bypass branch, this invention can also achieve the purpose of defrosting the frost layer on the evaporator surface. Specifically, since the refrigerant flowing into the first gas-liquid separator from the condenser outlet still has a relatively high temperature, and the refrigerant does not exchange heat within the first gas-liquid separator, the gaseous refrigerant flowing out of the first gas-liquid separator releases a large amount of heat after flowing into the evaporator. Under the influence of this heat, the frost layer on the evaporator surface will completely melt in a short time. Furthermore, to ensure the defrosting effect and efficiency, the expansion valve needs to be closed during the defrosting operation of the heat pump system. This ensures that the gaseous refrigerant can completely enter the evaporator through the bypass branch, maximizing heat utilization and shortening the defrosting time.

[0011] In one embodiment, the condenser has a heat exchange channel and a refrigerant channel that exchange heat with each other, and the two ends of the refrigerant channel are respectively connected to the compressor outlet and the refrigerant inlet; the heat exchange channel is used for external water connection.

[0012] In one embodiment, the switching mechanism includes a level sensor for detecting the liquid level inside the first gas-liquid separator and a solenoid valve disposed on the bypass branch.

[0013] In one embodiment, the gaseous refrigerant outlet is located at the top of the first gas-liquid separator; the switching mechanism includes a valve body and a valve core, the valve body is installed at the gaseous refrigerant outlet, the valve body is provided with a fluid channel, one end of the fluid channel is connected to the bypass branch, and the other end is connected to the interior of the first gas-liquid separator; the valve core is located inside the first gas-liquid separator, and when the liquid level of the liquid refrigerant reaches a preset height inside the first gas-liquid separator, at least a portion of the valve core extends into the fluid channel to close the fluid channel.

[0014] In one embodiment, the fluid channel includes a first flow section communicating with the bypass branch and a second flow section communicating with the interior of the first gas-liquid separator. The diameter of the first flow section is smaller than the diameter of the second flow section. A guide plate is provided at the port of the second flow section away from the first flow section. The guide plate is provided with a guide hole and a flow passage hole disposed around the guide hole. The guide hole is clearance-fitted with the valve core. When the liquid level of the liquid refrigerant reaches a preset height in the first gas-liquid separator, at least a portion of the valve core extends into the second flow section through the guide hole and closes the first flow section.

[0015] In one embodiment, the valve core includes a float and a valve stem connected to the float. When the liquid level of the liquid refrigerant reaches a preset height within the first gas-liquid separator, at least a portion of the valve stem extends through the guide hole into the second flow section and closes the first flow section.

[0016] In one embodiment, a limiting member is provided on the side wall of the valve stem located within the second flow section, the limiting member being adapted to abut against the upper surface of the guide plate.

[0017] In one embodiment, the fluid channel further includes a transition section located between the first flow section and the second flow section, wherein the diameter of the transition section decreases from the second flow section to the first flow section; the shape of the end of the valve stem near the first flow section is adapted to the shape of the small end of the transition section, and when the liquid level of the liquid refrigerant reaches a preset height in the first gas-liquid separator, the outer side wall of the end of the valve stem fits against the inner side wall of the small end of the transition section to close the first flow section.

[0018] In one embodiment, the heat pump system further includes a regenerator having a first heat exchange channel and a second heat exchange channel that exchange heat with each other. The first heat exchange channel is connected to a pipeline between the outlet of the condenser and the refrigerant inlet; the second heat exchange channel is connected to a pipeline between the outlet of the evaporator and the return port of the compressor.

[0019] In one embodiment, a second gas-liquid separator is also provided on the refrigerant circulation loop between the evaporator and the compressor; the heat pump system also includes a fan for driving air to flow sequentially through the evaporator. Attached Figure Description

[0020] To more clearly illustrate the specific embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0021] Figure 1 This is a connection diagram of a heat pump system according to an embodiment of the present utility model;

[0022] Figure 2 for Figure 1 A magnified view of part A in the middle;

[0023] Figure 3 for Figure 2 A schematic diagram of the switch mechanism in the open state;

[0024] Figure 4 for Figure 2 A schematic diagram of the switch mechanism in the closed state.

[0025] Explanation of reference numerals in the attached figures:

[0026] 1. Compressor; 2. Condenser; 201. Heat exchange channel; 202. Refrigerant channel; 3. First gas-liquid separator; 301. Refrigerant inlet; 302. Liquid refrigerant outlet; 303. Gaseous refrigerant outlet; 4. Throttling valve; 5. Evaporator; 6. Switching mechanism; 601. Valve body; 6011. Fluid channel; 6012. First flow section; 6013. Second flow section; 6014. Transition flow section; 602. Valve core; 6021. Valve stem; 6022. Float; 7. Guide plate; 701. Guide hole; 702. Flow hole; 8. Limiting element; 9. Regenerator; 901. First heat exchange channel; 902. Second heat exchange channel; 10. Second gas-liquid separator; 11. Fan; 12. Bypass branch. Detailed Implementation

[0027] 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 some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0028] In the description of this application, it should be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0029] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, unless otherwise stated, "a plurality of" means two or more.

[0030] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0031] The following is combined Figures 1 to 4 The following describes embodiments of the present invention.

[0032] According to embodiments of the present invention, such as Figure 1 As shown, a heat pump system is provided, including a refrigerant circulation loop, a bypass branch 12, and a switching mechanism 6.

[0033] Specifically, the refrigerant circulation loop is sequentially connected to a compressor 1, a condenser 2, a first gas-liquid separator 3, a throttle valve 4, and an evaporator 5. The first gas-liquid separator 3 is provided with a refrigerant inlet 301, a liquid refrigerant outlet 302, and a gaseous refrigerant outlet 303. The refrigerant inlet 301 is connected to the outlet of the condenser 2, the liquid refrigerant outlet 302 is connected to the inlet of the throttle valve 4, one end of the bypass branch 12 is connected to the gaseous refrigerant outlet 303, and the other end is connected to the pipeline between the throttle valve 4 and the evaporator 5. The switching mechanism 6 is used to open or close the bypass branch 12.

[0034] This embodiment of the invention separates the gaseous and liquid refrigerant in the refrigerant circulation loop by setting a first gas-liquid separator 3 between the condenser 2 and the expansion valve 4. The liquid refrigerant outlet 302 of the first gas-liquid separator 33 is then connected to the inlet of the expansion valve 4, and the gaseous refrigerant outlet 303 of the first gas-liquid separator 3 is connected to the bypass branch 12. This allows the separated gaseous and liquid refrigerant to flow out of the first gas-liquid separator 3 via different paths, thus avoiding the problem of gas blockage in the expansion valve 4 caused by gaseous refrigerant flowing through it, thereby extending the service life of the expansion valve 4. Specifically, during the operation of the heat pump system, the expansion valve 4 is in the open state, so the liquid refrigerant in the first gas-liquid separator 3 continuously flows into the expansion valve 4 through the liquid refrigerant outlet 302 to maintain the normal refrigerant circulation process. The gaseous refrigerant will remain in the first gas-liquid separator 3, achieving initial separation from the liquid refrigerant. However, as the gaseous refrigerant continues to accumulate in the first gas-liquid separator 3, the switching mechanism 6 needs to be activated to allow the gaseous refrigerant in the first gas-liquid separator 3 to bypass the throttle valve 4 and directly enter the evaporator 5 through the gaseous refrigerant outlet 303 and the bypass branch 12. In this way, not only can the separated gaseous refrigerant be prevented from flowing back into the throttle valve 4 from the liquid refrigerant outlet 302, thus avoiding air blockage in the throttle valve 4, but the pressure inside the first gas-liquid separator 3 can also be regulated to avoid excessive pressure inside the first gas-liquid separator 3 due to excessive accumulation of gaseous refrigerant.

[0035] Secondly, in this embodiment, connecting the gaseous refrigerant outlet 303 of the first gas-liquid separator 3 to the bypass branch 12 can also achieve the purpose of defrosting the frost layer on the surface of the evaporator 5. Specifically, since the refrigerant flowing into the first gas-liquid separator 3 from the outlet of the condenser 2 still has a high temperature, and the refrigerant does not exchange heat in the first gas-liquid separator 3, the gaseous refrigerant flowing out of the first gas-liquid separator 3 will release a large amount of heat after flowing into the evaporator 5. Under the influence of this heat, the frost layer on the surface of the evaporator 5 will completely melt in a short time. Furthermore, in order to ensure the defrosting effect and defrosting efficiency, the throttling valve 4 needs to be closed when the heat pump system performs defrosting operation, so as to ensure that the gaseous refrigerant can completely enter the evaporator 5 through the bypass branch 12, thereby maximizing heat utilization and shortening the defrosting time.

[0036] It should be noted that the refrigerant flowing in the refrigerant circulation loop in this embodiment can be a single refrigerant or a mixed refrigerant. The mixed refrigerant is a refrigerant composed of a mixture of multiple non-azeotropic working fluids.

[0037] In one embodiment, the condenser 2 has a heat exchange channel 201 and a refrigerant channel 202 that exchange heat with each other. The two ends of the refrigerant channel 202 are connected to the compressor 1 outlet and the refrigerant inlet 301, respectively. The heat exchange channel 201 is used for external water connection. It can be understood that in order to ensure the defrosting effect of the heat pump system in defrosting mode, the heat exchange channel 201 needs to be closed. In this way, the high-temperature refrigerant in the refrigerant channel 202 will not exchange heat, thereby allowing the refrigerant to carry more heat into the evaporator 5, improving defrosting efficiency and defrosting effect.

[0038] It should be noted that the heat pump system in this embodiment also has a heating mode. Specifically, the heating mode refers to the process of introducing cold water into the heat exchange channel 201 of the condenser 2, using the heat carried by the high-temperature refrigerant in the refrigerant channel 202 to heat the cold water in the heat exchange channel 201, thereby achieving the purpose of outputting hot water.

[0039] In one embodiment, the switching mechanism 6 includes a level sensor for detecting the liquid level inside the first gas-liquid separator 3 and a solenoid valve disposed on the bypass branch 12. Furthermore, in this embodiment, the level sensor and the solenoid valve are electrically connected to the controller. This not only enables accurate detection of the liquid level inside the first gas-liquid separator 3, preventing gaseous refrigerant from flowing into the throttle valve 4, but also allows for automated control of the opening and closing of the solenoid valve.

[0040] In one embodiment, such as Figure 2 As shown, the gaseous refrigerant outlet 303 is located at the top of the first gas-liquid separator 3; the switching mechanism 6 includes a valve body 601 and a valve core 602. The valve body 601 is installed at the gaseous refrigerant outlet 303, and a fluid channel 6011 is provided inside the valve body 601. One end of the fluid channel 6011 is connected to the bypass branch 12, and the other end is connected to the interior of the first gas-liquid separator 3; the valve core 602 is located inside the first gas-liquid separator 3. When the liquid level of the liquid refrigerant reaches a preset height inside the first gas-liquid separator 3, under the buoyancy of the liquid refrigerant, at least part of the valve core 602 extends into the fluid channel 6011 to close the fluid channel 6011. It can be understood that if the liquid level of the liquid refrigerant is lower than the preset height inside the first gas-liquid separator 3, the valve core 602 will move down as the liquid level drops until the fluid channel 6011 is opened. Furthermore, the preset height in this application is determined based on the heat pump system described in this application and the amount of refrigerant required for heating. In different heat pump systems or different heating demand environments, the preset height can be adjusted according to actual needs.

[0041] It should be noted that in this embodiment, the valve core 602 is placed inside the first gas-liquid separator 3, which makes it easier for the valve core 602 to come into contact with the liquid refrigerant inside the first gas-liquid separator 3. This not only improves the response sensitivity of the switching mechanism 6 to changes in liquid level, but also avoids the situation where the valve core 602 can only close the fluid channel 6011 when the liquid refrigerant is at a high level. This ensures that enough liquid refrigerant can flow from the first gas-liquid separator 3 to the throttle valve 4 and the evaporator 5, thereby ensuring that the heat pump system can maintain normal heating performance.

[0042] In one embodiment, such as Figure 3 and Figure 4 As shown, the fluid channel 6011 includes a first flow section 6012 connected to the bypass branch 12 and a second flow section 6013 connected to the interior of the first gas-liquid separator 3. The diameter of the first flow section 6012 is smaller than the diameter of the second flow section 6013. A guide plate 7 is provided at the port of the second flow section 6013 away from the first flow section 6012. The guide plate 7 is provided with a guide hole 701 and a flow passage hole 702 disposed around the guide hole 701. The guide hole 701 is coaxially arranged with the first flow section 6012 and is clearance-fitted with the valve core 602. When the liquid level of the liquid refrigerant reaches a preset height in the first gas-liquid separator 3, under the buoyancy of the liquid refrigerant, at least part of the valve core 602 extends into the second flow section 6013 through the guide hole 701 and closes the first flow section 6012. The second flow section 6013 is connected to the interior of the first gas-liquid separator 3 through the flow passage hole 702. In this embodiment, the diameter of the second flow section 6013 is increased. This provides more installation space for workers, allowing them to easily install the guide plate 7 and valve core 602 within the second flow section 6013. It also increases the amount of gaseous refrigerant flowing into the fluid channel 6011, reducing the impact of reduced effective area at the inlet of the fluid channel 6011 due to obstruction by the guide plate 7 and valve core 602. Secondly, this embodiment provides a guide hole 701 on the guide plate 7, coaxially aligned with the first flow section 6012. This ensures that the valve core 602 always moves up and down along the axial direction of the guide hole 701, preventing displacement of the valve core 602 during movement and guaranteeing the reliability of the switching mechanism 6. Furthermore, this embodiment provides a flow-through hole 702 on the guide plate 7, reducing the obstruction effect of the guide plate 7 on the flow of gaseous refrigerant and allowing more gaseous refrigerant to flow into the second flow section 6013.

[0043] It should be noted that this embodiment does not impose any special limitations on the shape and number of the flow holes 702, as long as the gaseous refrigerant can flow into the second flow section 6013 through the flow holes 702.

[0044] In one example, there are multiple flow holes 702, which are spaced apart around the guide hole 701.

[0045] In another example, the flow passage 702 is annular in shape, and the annular flow passage 702 surrounds the periphery of the guide hole 701.

[0046] Furthermore, in this embodiment, the cross-sectional area of ​​the guide plate 7 is not greater than the cross-sectional area of ​​the second flow section 6013.

[0047] In one embodiment, the valve core 602 includes a float 6022 and a valve stem 6021 connected to the float 6022. When the liquid level of the liquid refrigerant reaches a preset height within the first gas-liquid separator 3, at least a portion of the valve stem 6021 extends through the guide hole 701 into the second flow section 6013 and closes the first flow section 6012. By providing the float 6022, the contact area between the valve stem 6021 and the liquid refrigerant can be increased, thereby increasing the buoyancy of the float 6022 and ensuring that the valve stem 6021 can effectively close the first flow section 6012.

[0048] In one embodiment, such as Figure 3 and Figure 4 As shown, the diameter of the float 6022 is larger than the diameter of the end of the valve stem 6021 connected to the float 6022. It can be understood that increasing the diameter of the float 6022 allows the float 6022 assembly to more sensitively sense changes in liquid level, and also enables the float 6022 to drive the valve stem 6021 upwards even at lower liquid levels.

[0049] In one embodiment, there are multiple floats 6022, which are arranged sequentially along the circumference of the valve stem 6021. Compared to a single float 6022, this embodiment, by setting multiple floats 6022, can apply force to the valve stem 6021 from multiple directions simultaneously, avoiding the problem of tilting of the valve stem 6021 due to uneven force at a single point, and ensuring that the valve stem 6021 maintains a stable axial movement trajectory during lifting and lowering.

[0050] In one embodiment, such as Figure 3 and Figure 4 As shown, a limiting member 8 is provided on the side wall of the valve core 602 located in the second flow section 6013. The limiting member 8 is adapted to abut against the upper surface of the guide plate 7. In this embodiment, by providing the limiting member 8 on the side wall of the valve core 602, it is possible to prevent the valve core 602 from falling off the guide plate 7 during the axial downward movement along the guide hole 701.

[0051] It should be noted that in this embodiment, the limiting member 8 can be a disc, or one or more limiting blocks arranged circumferentially on the outer wall of the valve core 602. Specifically, this utility model does not make specific limitations, as long as the limiting member 8 can abut against the upper surface of the guide plate 7 to restrict the downward movement tendency of the valve core 602.

[0052] In one embodiment, such as Figure 3 and Figure 4 As shown, the fluid channel 6011 also includes a transition section 6014 located between the first flow section 6012 and the second flow section 6013. From the second flow section 6013 to the first flow section 6012, the diameter of the transition section 6014 decreases. The shape of the end of the valve stem 6021 near the first flow section 6012 is adapted to the shape of the small end of the transition section 6014. When the liquid level of the liquid refrigerant reaches a preset height in the first gas-liquid separator 3, under the buoyancy of the liquid refrigerant, the float ball 6022 drives the valve stem 6021 to move upward, so that the outer wall of its end fits against the inner wall of the small end of the transition section 6014, and closes the first flow section 6012. This embodiment, by setting a transitional flow section 6014 with a decreasing diameter between the first flow section 6012 and the second flow section 6013, can naturally guide the valve stem 6021 to the connection point between the first flow section 6012 and the transitional flow section 6014 through the pipe change of the transitional flow section 6014, reducing the possibility that the valve stem 6021 will fail to close the first flow section 6012 due to movement deviation. Furthermore, this embodiment adapts the shape of the end of the valve stem 6021 near the first flow section 6012 to the shape of the small end of the transitional flow section 6014, thereby improving the fit between the two and achieving effective sealing of the first flow section 6012.

[0053] In one embodiment, such as Figure 1 As shown, the heat pump system also includes a regenerator 9, which has a first heat exchange channel 901 and a second heat exchange channel 902 for mutual heat exchange. The first heat exchange channel 901 is connected to the pipeline between the outlet of the condenser 2 and the refrigerant inlet 301; the second heat exchange channel 902 is connected to the pipeline between the outlet of the evaporator 5 and the return port of the compressor 1. In this embodiment, the regenerator 9 is installed in the heat pump system, which can increase the subcooling of the refrigerant, reduce throttling losses during the throttling process, and improve the heating performance of the heat pump system. Specifically, in heating mode, the refrigerant temperature flowing into the first heat exchange channel 901 from the outlet of condenser 2 is higher than the refrigerant temperature flowing into the second heat exchange channel 902 from the outlet of evaporator 5. Therefore, the refrigerant in the second heat exchange channel 902 will exchange heat with the refrigerant in the first heat exchange channel 901, allowing the refrigerant in the first heat exchange channel 901 to flow to the throttling valve 4 at a lower temperature. This reduces throttling losses during the throttling process, allowing more liquid refrigerant to enter the evaporator 5 for evaporation and heat absorption, thus improving the heating performance of the heat pump system.

[0054] In one embodiment, such as Figure 1As shown, a second gas-liquid separator 10 is also provided in the refrigerant circulation loop, located between the evaporator 5 and the compressor 1; the heat pump system also includes a fan 11, which drives air to flow sequentially through the evaporator 5. In this embodiment, by setting the second gas-liquid separator 10 between the outlet of the evaporator 5 and the inlet of the compressor 1, the unvaporized liquid refrigerant exiting the evaporator 5 can be separated, preventing the liquid refrigerant from entering the compressor 1, protecting the compressor 1, and extending its service life. Furthermore, by setting the fan 11 on one side of the evaporator 5, the airflow can continuously pass through the evaporator 5, increasing the evaporation rate of the liquid refrigerant within the evaporator 5.

[0055] In the specific implementation of the above embodiments, the technical features can be combined in any non-contradictory way. For the sake of brevity, not all possible combinations of the above technical features are described. However, as long as the combination of these technical features is not contradictory, it should be considered to be within the scope of this specification.

[0056] The specific embodiments described above are merely illustrative of several implementations of this utility model, and while the descriptions are detailed, they should not be construed as limiting the scope of this utility model patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this utility model, and these all fall within the protection scope of this utility model. Therefore, the protection scope of this utility model patent should be determined by the appended claims.

Claims

1. A heat pump system, characterized in that, include: The refrigerant circulation loop and bypass branch (12) are connected in sequence to a compressor (1), a condenser (2), a first gas-liquid separator (3), a throttle valve (4), and an evaporator (5). The first gas-liquid separator (3) is provided with a refrigerant inlet (301), a liquid refrigerant outlet (302), and a gaseous refrigerant outlet (303). The refrigerant inlet (301) is connected to the outlet of the condenser (2), and the liquid refrigerant outlet (302) is connected to the inlet of the throttle valve (4). One end of the bypass branch (12) is connected to the gaseous refrigerant outlet (303), and the other end is connected to the pipeline between the throttle valve (4) and the evaporator (5). A switching mechanism (6) is used to turn on or off the bypass branch (12).

2. The heat pump system according to claim 1, characterized in that: The condenser (2) has a heat exchange channel (201) and a refrigerant channel (202) for mutual heat exchange. The two ends of the refrigerant channel (202) are connected to the outlet of the compressor (1) and the refrigerant inlet (301) respectively. The heat exchange channel (201) is used for external water connection.

3. The heat pump system according to claim 1, characterized in that: The switching mechanism (6) includes a liquid level sensor for detecting the liquid level inside the first gas-liquid separator (3) and a solenoid valve disposed on the bypass branch (12).

4. The heat pump system according to claim 1, characterized in that: The gaseous refrigerant outlet (303) is located at the top of the first gas-liquid separator (3); the switching mechanism (6) includes a valve body (601) and a valve core (602). The valve body (601) is installed at the gaseous refrigerant outlet (303). A fluid channel (6011) is provided inside the valve body (601). One end of the fluid channel (6011) is connected to the bypass branch (12), and the other end is connected to the interior of the first gas-liquid separator (3). The valve core (602) is located inside the first gas-liquid separator (3). When the liquid level of the liquid refrigerant reaches a preset height inside the first gas-liquid separator (3), at least part of the valve core (602) extends into the fluid channel (6011) to close the fluid channel (6011).

5. The heat pump system according to claim 4, characterized in that: The fluid channel (6011) includes a first flow section (6012) communicating with the bypass branch (12) and a second flow section (6013) communicating with the interior of the first gas-liquid separator (3). The diameter of the first flow section (6012) is smaller than the diameter of the second flow section (6013). A guide plate (7) is provided at the port of the second flow section (6013) away from the first flow section (6012). The guide plate (7) is provided with a guide hole (701) and a flow passage hole (702) disposed around the guide hole (701). The guide hole (701) is clearance-fitted with the valve core (602). When the liquid level of the liquid refrigerant reaches a preset height in the first gas-liquid separator (3), at least part of the valve core (602) extends into the second flow section (6013) through the guide hole (701) and closes the first flow section (6012).

6. The heat pump system according to claim 5, characterized in that: The valve core (602) includes a float (6022) and a valve stem (6021) connected to the float (6022). When the liquid level of the liquid refrigerant reaches a preset height in the first gas-liquid separator (3), at least a portion of the valve stem (6021) extends through the guide hole (701) into the second flow section (6013) and closes the first flow section (6012).

7. The heat pump system according to claim 6, characterized in that: A limiting member (8) is located on the side wall of the valve stem (6021) within the second flow section (6013), the limiting member (8) being adapted to abut against the upper surface of the guide plate (7).

8. The heat pump system according to claim 6, characterized in that: The fluid channel (6011) also includes a transition section (6014) located between the first flow section (6012) and the second flow section (6013). The diameter of the transition section (6014) decreases from the second flow section (6013) to the first flow section (6012). The shape of the end of the valve stem (6021) near the first flow section (6012) is adapted to the shape of the small end of the transition section (6014). When the liquid level of the liquid refrigerant reaches a preset height in the first gas-liquid separator (3), the outer side wall of the end of the valve stem (6021) fits against the inner side wall of the small end of the transition section (6014) to close the first flow section (6012).

9. The heat pump system according to any one of claims 1 to 8, characterized in that: The heat pump system also includes a regenerator (9), which has a first heat exchange channel (901) and a second heat exchange channel (902) for mutual heat exchange. The first heat exchange channel (901) is connected to the pipeline between the outlet of the condenser (2) and the refrigerant inlet (301); the second heat exchange channel (902) is connected to the pipeline between the outlet of the evaporator (5) and the return port of the compressor (1).

10. The heat pump system according to any one of claims 1 to 8, characterized in that: The refrigerant circulation loop is also provided with a second gas-liquid separator (10) located between the evaporator (5) and the compressor (1); the heat pump system also includes a fan (11), which is used to drive air to flow through the evaporator (5) in sequence.

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