Vehicle secondary heat exchange system, vehicle air conditioner and vehicle

Abstract

The utility model relates to a vehicle secondary heat exchange system, a vehicle air conditioner and a vehicle. The heat exchange system comprises an evaporator, a compressor, an evaporative condenser and an economizer which are connected in sequence. The first end of the economizer is connected with the evaporator; the second end of the economizer is connected with the evaporative condenser; the third end of the economizer is connected with an air supply port of the compressor; a bypass throttling pipeline is led out between the evaporator and the economizer and connected to the fourth end of the economizer. The heat exchange performance of the heat exchange system can be improved, meanwhile, the exhaust temperature of the compressor can be reduced, and the situation that the reliability of the compressor is affected due to high exhaust temperature is avoided.

Description

Technical Field

[0001] The present application relates to the technical field of vehicle air conditioners, and particularly to a vehicle secondary heat exchange system, a vehicle air conditioner and a vehicle. Background Art

[0002] Based on the current industry's demand for the use of environmentally friendly refrigerants, currently each vehicle manufacturer is actively carrying out the replacement work of environmentally friendly refrigerants. Since R290 (propane) is a naturally occurring substance with an ODP (ozone depletion potential) of 0 and a GWP (global warming potential) of 0.03, it is a completely environmentally friendly refrigerant, and many vehicle manufacturers have started the research and development work of R290 heat pump systems.

[0003] Currently, the vehicle R290 heat pump system adopts a secondary heat exchange system. Since the heat exchange efficiency of the secondary heat exchange system is lower than that of the primary heat exchange system (direct heat pump), currently it is necessary to increase the heat exchange performance to make up for the energy loss brought by the secondary heat exchange system. In related technologies, through the application of a gas-injected compressor, the gas-injected enthalpy increase method is used to improve the heat exchange performance. As Figure 1 shown, a bypass with high-pressure liquid is introduced from the upstream of the economizer 3 into the economizer 3 for heat exchange, and then the compressor 4 is gas-injected through a gas injection pipeline. This gas injection method has a high gas injection temperature, which easily leads to a high exhaust temperature of the compressor 4, and then affects the reliability of the compressor 4.

[0004] Therefore, it is very necessary to develop a vehicle secondary heat exchange system, a vehicle air conditioner and a vehicle to overcome the above-mentioned difficulties. Summary of the Utility Model

[0005] The present application aims to solve at least one of the technical problems existing in the above-mentioned prior art. For this purpose, the present application provides a vehicle secondary heat exchange system, a vehicle air conditioner and a vehicle.

[0006] The first aspect of the present application provides a vehicle secondary heat exchange system, including: an evaporator, a compressor, an evaporative condenser and an economizer connected in sequence; the first end of the economizer is connected to the evaporator; the second end of the economizer is connected to the evaporative condenser; the third end of the economizer is connected to the gas injection port of the compressor; wherein, a bypass throttling pipeline is led out between the evaporator and the economizer and connected to the fourth end of the economizer.

[0007] Preferably, the first end of the economizer is communicated with the evaporator through a high-pressure subcooling pipeline; the second end of the economizer is communicated with the evaporative condenser through a high-pressure liquid pipeline; the third end of the economizer is communicated with the gas injection port of the compressor through a gas injection pipeline; the evaporator and the suction port of the compressor are communicated through a suction pipeline; the exhaust port of the compressor and the evaporative condenser are communicated through an exhaust pipeline.

[0008] Preferably, a main throttle valve is provided on the high-pressure subcooling pipeline; a gas supplement electronic expansion valve is provided on the bypass throttling pipeline; the bypass throttling pipeline is connected to the high-pressure subcooling pipeline between the main throttle valve and the economizer.

[0009] Preferably, a liquid receiver is further included, and the liquid receiver is arranged between the evaporative condenser and the economizer and is located on the high-pressure liquid pipeline.

[0010] Preferably, the evaporator is configured with a low-temperature chilled water circulation device; the low-temperature chilled water circulation device and the evaporator are circulated and connected through a low-temperature chilled water loop.

[0011] Preferably, the low-temperature chilled water loop includes a low-temperature chilled water supply pipe and a low-temperature chilled water return pipe; the evaporator is provided with a low-temperature chilled water return port and a low-temperature chilled water supply port; the low-temperature chilled water supply port is communicated with the low-temperature chilled water supply pipe; the low-temperature chilled water return port is communicated with the low-temperature chilled water return pipe.

[0012] Preferably, the evaporative condenser is configured with a high-temperature chilled water circulation device; the high-temperature chilled water circulation device and the evaporative condenser are circulated and connected through a high-temperature chilled water loop.

[0013] Preferably, the high-temperature chilled water loop includes a high-temperature chilled water supply pipe and a high-temperature chilled water return pipe; the evaporative condenser is provided with a high-temperature chilled water return port and a high-temperature chilled water supply port; the high-temperature chilled water supply port is communicated with the high-temperature chilled water supply pipe; the high-temperature chilled water return port is communicated with the high-temperature chilled water return pipe.

[0014] In the second aspect of the present application, a vehicle air conditioner is further provided, including the vehicle secondary heat exchange system described above.

[0015] In the third aspect of the present application, a vehicle is further provided, including the vehicle air conditioner described above.

[0016] Specifically, compared with the prior art, the beneficial effects of the present application are as follows:

[0017] In the vehicle secondary heat exchange system of the present application, a bypass throttling pipeline is led out from the downstream of the economizer, that is, the high-pressure subcooling pipeline, and connected to the third end of the economizer. The fourth end of the economizer supplies gas to the compressor through a gas replenishing pipeline. Compared with the gas replenishing method from the upstream of the economizer in a common secondary heat exchange system, this gas replenishing cycle method in the present application causes the high-pressure liquid to evaporate in the economizer, enabling the high-pressure liquid in the high-pressure subcooling pipeline to be further subcooled. Thus, the refrigerating capacity and refrigerating energy efficiency of the unit are effectively improved. At the same time, the downstream gas replenishing method increases the gas replenishing flow rate, can improve the gas replenishing efficiency, thereby enhancing the heat exchange performance of the system. Moreover, the gas replenishing temperature of the downstream gas replenishing is low, which can reduce the exhaust temperature of the compressor and prevent the compressor from being affected by the high exhaust temperature and affecting its reliability. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 FIG. is a schematic diagram of the principle of a vehicle secondary heat exchange system in the related art;

[0019] Figure 2 FIG. is a pressure-enthalpy diagram of a vehicle secondary heat exchange system in the related art;

[0020] Figure 3 FIG. is a schematic diagram of the principle of a vehicle secondary heat exchange system in an embodiment of the present application;

[0021] Figure 4 FIG. is a pressure-enthalpy diagram of a vehicle secondary heat exchange system in an embodiment of the present application.

[0022] Reference numerals: 1, evaporator; 2, evaporative condenser; 3, economizer; 4, compressor; 5, exhaust pipeline; 6, high-pressure liquid pipeline; 7, high-pressure subcooling pipeline; 8, main throttle valve; 9, suction pipeline; 10, bypass throttling pipeline; 11, gas replenishing pipeline; 12, gas replenishing electronic expansion valve; 13, accumulator; 14, low-temperature chilled water circulation device; 15, low-temperature chilled water supply pipe; 16, low-temperature chilled water return pipe; 17, high-temperature chilled water circulation device; 18, high-temperature chilled water supply pipe; 19, high-temperature chilled water return pipe. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0023] In order to make the objectives, technical solutions and advantages of the present application clearer, the present application will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0024] It should be noted that the drawings provided in this embodiment only illustrate the basic concept of the present application in a schematic manner. Therefore, only the components related to the present application are shown in the drawings, rather than being drawn according to the number, shape and size of the components in actual implementation. The type, quantity and proportion of each component in actual implementation can be arbitrarily changed, and the component layout type may also be more complex.

[0025] The structures, ratios, sizes, etc. shown in the drawings of this specification are only used to cooperate with the content disclosed in the specification for those skilled in this technology to understand and read, and are not used to limit the implementation conditions of this application. Therefore, they do not have substantial technical significance. Any modification of the structure, change in the ratio relationship, or adjustment of the size, without affecting the effects that this application can produce and the purposes that can be achieved, should still fall within the scope covered by the technical content disclosed in this application.

[0026] The orientation or positional relationship indicated in this specification, such as "upper", "lower", "left", "right", "middle", "longitudinal", "lateral", "horizontal", "inner", "outer", "radial", "circumferential", etc., is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation. Therefore, it cannot be understood as a limitation to this application. In addition, the terms "first" and "second" are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0027] Please refer to Figure 3 As shown, this embodiment provides a vehicle secondary heat exchange system, which will be described in detail below, including: an evaporator 1, an evaporative condenser 2, an economizer 3, and a compressor 4. The evaporator 1, the compressor 4, the evaporative condenser 2, and the economizer 3 are connected in sequence. The compressor 4 is provided with a suction port and a discharge port. The discharge port of the compressor 4 and the evaporative condenser 2 are connected through an exhaust pipe 5; the evaporative condenser 2 and the first end of the economizer 3 are connected through a high-pressure liquid pipe 6; the second end of the economizer 3 and the evaporator 1 are connected through a high-pressure subcooled pipe 7, and a main throttle valve 8 is provided on the high-pressure subcooled pipe 7; the evaporator 1 and the suction port of the compressor 4 are connected through a suction pipe 9; wherein, a bypass throttle pipe 10 is led out from the high-pressure subcooled pipe 7 between the main throttle valve 8 and the economizer 3 and connected to the third end of the economizer 3. The fourth end of the economizer 3 is connected to the gas injection port of the compressor 4 through a gas supply pipe 11, and a gas injection electronic expansion valve 12 is also provided on the bypass throttle pipe 10.

[0028] In this embodiment, a bypass throttle pipe 10 is branched from the downstream of the economizer 3, that is, from the high-pressure subcooled pipe 7. This bypass throttle pipe 10 is connected to the economizer 3, and the economizer 3 then supplies gas into the compressor 4 through the gas supply pipe 11. Compared with the method of branching the bypass throttle pipe 10 from the upstream of the economizer 3 for gas injection, in this embodiment, the bypass throttle pipe 10 is branched from the downstream of the economizer 3, which increases the gas injection flow rate, can improve the gas injection efficiency, thereby increasing the heat exchange performance of the system. At the same time, the gas injection temperature is low, which can also reduce the discharge temperature of the compressor 4 and avoid affecting the reliability of the compressor 4 due to the high discharge temperature.

[0029] In this embodiment, it should be noted that a liquid receiver 13 is also provided between the evaporative condenser 2 and the economizer 3. The liquid receiver 13 is arranged on the high-pressure liquid pipeline 6. The high-pressure liquid pipeline 6 transports the high-pressure liquid to be stored in the liquid receiver 13, and then transports it from the liquid receiver 13 into the economizer 3. The use of the liquid receiver 13 plays the functions of buffering and liquid storage.

[0030] In this embodiment, it should also be noted that the evaporator 1 is configured with a low-temperature chilled water circulation device 14. The low-temperature chilled water circulation device 14 and the evaporator 1 are circulated and connected through a low-temperature chilled water loop. The low-temperature chilled water loop includes a low-temperature chilled water supply pipe 15 and a low-temperature chilled water return pipe 16. The evaporator 1 is provided with a low-temperature chilled water return port and a low-temperature chilled water supply port. The low-temperature chilled water supply port is connected to the low-temperature chilled water supply pipe 15 to output low-temperature chilled water, and the low-temperature chilled water return port is connected to the low-temperature chilled water return pipe 16, thus forming a low-temperature chilled water loop.

[0031] The evaporative condenser 2 is configured with a high-temperature chilled water circulation device 17. The high-temperature chilled water circulation device 17 and the evaporative condenser 2 are circulated and connected through a high-temperature chilled water loop. The high-temperature chilled water loop includes a high-temperature chilled water supply pipe 18 and a high-temperature chilled water return pipe 19. The evaporative condenser 2 is provided with a high-temperature chilled water return port and a high-temperature chilled water supply port. The high-temperature chilled water supply port is connected to the high-temperature chilled water supply pipe 18 to output high-temperature chilled water, and the high-temperature chilled water return port is connected to the high-temperature chilled water return pipe 19, thus forming a high-temperature chilled water loop.

[0032] In this embodiment, it should also be noted that the economizer 3 adopts a plate heat exchanger. The compressor 4 can adopt a multi-stage centrifugal compressor.

[0033] The implementation principle of this embodiment: The specific working process is as follows: The low-temperature and low-pressure gaseous refrigerant coming out of the evaporator 1 enters the compressor 4 through the suction pipeline 9, is compressed by the compressor 4 into a high-temperature and high-pressure gaseous refrigerant, and then enters the evaporative condenser 2 through the exhaust pipeline 5;

[0034] The high-temperature and high-pressure gaseous refrigerant is condensed into a high-pressure liquid after heat exchange inside the evaporative condenser 2. The high-pressure liquid then enters the liquid receiver 13 through the high-pressure liquid pipeline 6 and then enters the economizer 3. Inside the economizer 3, the high-pressure liquid is cooled into a high-pressure subcooled liquid by the medium-temperature and medium-pressure refrigerant liquid in the heat exchange plate and then enters the main throttle valve 8 through the high-pressure subcooled pipeline 7 to be throttled and depressurized into a low-temperature and low-pressure gas-liquid refrigerant;

[0035] The low-temperature and low-pressure gas-liquid refrigerant coming out of the main throttle valve 8 enters the evaporator 1, exchanges heat with the relatively high-temperature coolant, absorbs the heat of the coolant to cool down the coolant, and then evaporates into a low-temperature and low-pressure gas. After that, it is sucked into the compressor 4 through the suction pipeline 9 and recompressed into a high-temperature and high-pressure gaseous refrigerant, and the refrigeration cycle runs repeatedly like this.

[0036] A bypass throttle pipeline 10 is led from the downstream of the economizer 3, that is, the high-pressure subcooled pipeline 7, to make part of the high-pressure subcooled liquid enter the gas injection electronic expansion valve 12. After being throttled and depressurized into a medium-temperature and medium-pressure gas-liquid refrigerant, it enters the economizer 3. The medium-temperature and medium-pressure gas-liquid refrigerant absorbs the heat of the high-pressure subcooled liquid on the main side and then evaporates into a medium-pressure gas. After that, it comes out from the fourth end of the economizer 3 and enters the medium-pressure cavity of the compressor 4 through the gas injection pipeline 11.

[0037] In this embodiment, the gas injection enthalpy-increasing technology is adopted. By injecting medium-pressure gas into the compressor 4 through the economizer 3, the deep subcooling of the high-pressure liquid before the main throttle valve 8 can be realized. Subsequently, the dryness and enthalpy value of the low-temperature and low-pressure gas-liquid refrigerant entering the evaporator 1 are reduced, thereby effectively improving the refrigeration capacity and refrigeration energy efficiency of the unit. At the same time, the economizer 3 adopts the downstream gas injection method to increase the gas injection flow rate, which can improve the gas injection efficiency, thereby increasing the heat exchange performance of the system. Moreover, the gas injection temperature of the downstream gas injection is low, which can reduce the temperature inside the compressor 4, thereby reducing the exhaust temperature of the compressor 4 and avoiding the influence of the high exhaust temperature of the compressor 4 on the reliability.

[0038] As Figure 2 shown, it is the pressure-enthalpy diagram of injecting gas into the compressor 4 through the gas injection pipeline after a bypass with high-pressure liquid is introduced from the upstream of the economizer 3 for heat exchange in the related technology; as Figure 4 shown, it is the pressure-enthalpy diagram of injecting gas into the compressor 4 through the gas injection pipeline after a bypass with high-pressure liquid is introduced from the downstream of the economizer 3 for heat exchange in the embodiment of the present application. Among them, the abscissa h is the enthalpy value, and the ordinate P is the absolute pressure. By comparison, it can be seen that by adopting the vehicle-mounted secondary heat exchange system described in this embodiment, the enthalpy value of the gas injection inlet 7` is smaller, so that the enthalpy difference (8` - 7`) between the gas injection inlet 7` and the gas injection outlet 8` can be increased. The increase of the enthalpy difference can improve the heat exchange performance of the economizer 3.

[0039] In this embodiment, the present application also provides a vehicle air conditioner including the vehicle-mounted secondary heat exchange system described above.

[0040] In this embodiment, the present application also provides a vehicle including the above-mentioned vehicle air conditioner.

[0041] The technical features of the above embodiments can be combined arbitrarily. For the sake of concise description, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, it should be considered as the scope described in this specification.

[0042] The above-described embodiments merely represent several implementation manners of the present application. The description is relatively specific and detailed, but it should not be construed as a limitation on the scope of the patent application. It should be noted that for those of ordinary skill in the art, without departing from the concept of the present application, several modifications and improvements can still be made, and these all belong to the protection scope of the present application. Therefore, the protection scope of the patent of the present application shall be subject to the appended claims.

Claims

1. A vehicle secondary heat exchange system, characterized in that, Comprising: An evaporator (1), a compressor (4), an evaporative condenser (2), and an economizer (3) connected in sequence; A first end of the economizer (3) is connected to the evaporator (1); A second end of the economizer (3) is connected to the evaporative condenser (2); A third end of the economizer (3) is connected to the gas supplement port of the compressor (4); Wherein, a bypass throttle pipeline (10) is led out between the evaporator (1) and the economizer (3) and connected to a fourth end of the economizer (3).

2. The vehicle secondary heat exchange system according to claim 1, wherein The first end of the economizer (3) is communicated with the evaporator (1) through a high-pressure subcooling pipeline (7); The second end of the economizer (3) is communicated with the evaporative condenser (2) through a high-pressure liquid pipeline (6); The third end of the economizer (3) is communicated with the gas supplement port of the compressor (4) through a gas supplement pipeline (11); The evaporator (1) and the suction port of the compressor (4) are communicated through a suction pipeline (9); The exhaust port of the compressor (4) and the evaporative condenser (2) are communicated through an exhaust pipeline (5).

3. The vehicle secondary heat exchange system according to claim 2, wherein A main throttle valve (8) is provided on the high-pressure subcooling pipeline (7); A gas supplement electronic expansion valve (12) is provided on the bypass throttle pipeline (10); The bypass throttle pipeline (10) is connected to the high-pressure subcooling pipeline (7) between the main throttle valve (8) and the economizer (3).

4. The vehicle secondary heat exchange system according to claim 2, wherein It further includes a liquid storage device (13), and the liquid storage device (13) is arranged between the evaporative condenser (2) and the economizer (3) and is located on the high-pressure liquid pipeline (6).

5. The vehicle secondary heat exchange system according to any one of claims 1-4, wherein The evaporator (1) is configured with a low-temperature chilled water circulation device (14); The low-temperature chilled water circulation device (14) and the evaporator (1) are circulated and communicated through a low-temperature chilled water loop.

6. The vehicle secondary heat exchange system according to claim 5, wherein The low-temperature chilled water loop includes a low-temperature chilled water supply pipe (15) and a low-temperature chilled water return pipe (16); The evaporator (1) is provided with a low-temperature chilled water return port and a low-temperature chilled water supply port; The low-temperature chilled water supply port is communicated with the low-temperature chilled water supply pipe (15); The low-temperature chilled water return port is communicated with the low-temperature chilled water return pipe (16).

7. The vehicle secondary heat exchange system according to any one of claims 1-4, wherein The evaporative condenser (2) is configured with a high-temperature chilled water circulation device (17); The high-temperature chilled water circulation device (17) and the evaporative condenser (2) are circulated and communicated through a high-temperature chilled water loop.

8. The vehicle secondary heat exchange system according to claim 7, wherein The high-temperature chilled water loop includes a high-temperature chilled water supply pipe (18) and a high-temperature chilled water return pipe (19); The evaporative condenser (2) is provided with a high-temperature chilled water return water port and a high-temperature chilled water supply water port; The high-temperature chilled water supply water port is communicated with the high-temperature chilled water supply pipe (18); The high-temperature chilled water return water port is communicated with the high-temperature chilled water return pipe (19).

9. A vehicle air conditioner, characterized in that: It includes the vehicle-mounted secondary heat exchange system according to any one of claims 1-8.

10. A vehicle, characterized in that: It includes the vehicle-mounted air conditioner according to claim 9.

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