Secondary heat exchange system and air supply control method

Abstract

The invention provides a secondary heat exchange system and an air supply control method. The secondary heat exchange system comprises a compressor, a water-cooling condenser, a first expansion valve, a flash tank, a second expansion valve and a battery cooler which are sequentially communicated through pipelines. The air outlet of the flash tank is further communicated with an air supply port of the compressor; by adopting the system design of the flash tank, a gas-liquid mixture throttled by the first expansion valve enters the flash tank to be subjected to gas-liquid separation, and gas enters the compressor through the connecting pipeline to be supplemented, so that the gas suction amount of the compressor and the heating amount of the system are increased, the gas supplementing efficiency is improved, and the heat exchange performance of the system is improved. Meanwhile, the air supply pressure can be controlled to control the exhaust temperature of the compressor, the exhaust temperature is prevented from being too high, the compressor is protected, the reliability of the secondary heat exchange system is improved, and the service life is prolonged.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicle heat pump systems, and in particular to a secondary heat exchange system and an air replenishment control method. Background Art

[0002] Based on the current industry demand for the use of environmentally friendly refrigerants, various OEMs are currently actively working on the replacement of environmentally friendly refrigerants. Since R290 (propane) is a naturally occurring substance, its ODP (ozone depletion potential) is 0 and its GWP (global warming potential) is 0.03. It is a completely environmentally friendly refrigerant. The R290 heat pump system can perform well under both high and low temperature conditions. Especially in low temperature environments, the R290 heat pump system has significant heating advantages and is therefore highly respected in the industry. Many OEMs have begun research and development of the R290 heat pump system.

[0003] At present, the automotive R290 heat pump system adopts a secondary heat exchange system with intermediate air supply. Since the heat exchange efficiency of the secondary heat exchange system is lower than that of the primary heat exchange system (direct heat pump), it is currently necessary to increase the heat exchange performance to compensate for the energy loss caused by the secondary heat exchange system. Summary of the invention

[0004] In view of the above problems existing in the prior art, the present invention provides a secondary heat exchange system and an air replenishment control method to improve the technical problem that the heat exchange efficiency of the existing secondary heat exchange system is lower than that of the primary heat exchange system and the energy loss caused by the secondary heat exchange system needs to be compensated.

[0005] To achieve the above-mentioned purpose and other related purposes, the first aspect of the present invention provides a secondary heat exchange system, which includes a compressor, a water-cooled condenser, a first expansion valve, a flasher, a second expansion valve and a battery cooler; the refrigerant inlet of the water-cooled condenser is connected to the air outlet of the compressor; the inlet of the first expansion valve is connected to the refrigerant outlet of the water-cooled condenser; the liquid inlet of the flasher is connected to the outlet of the first expansion valve; the air outlet of the flasher is connected to the air supply port of the compressor; the inlet of the second expansion valve is connected to the liquid outlet of the flasher; the first inlet of the battery cooler is connected to the outlet of the second expansion valve; and the first outlet of the battery cooler is connected to the air inlet of the compressor.

[0006] In one embodiment of the secondary heat exchange system of the present invention, a liquid storage tank is provided on the connecting pipeline between the refrigerant outlet of the water-cooled condenser and the inlet of the first expansion valve.

[0007] In one embodiment of the secondary heat exchange system of the present invention, a first temperature and pressure sensor is arranged on the connecting pipeline between the air outlet of the compressor and the refrigerant inlet of the water-cooled condenser, and a third temperature and pressure sensor is arranged on the connecting pipeline between the first outlet of the battery cooler and the air inlet of the compressor.

[0008] In an embodiment of the secondary heat exchange system of the present invention, a second temperature and pressure sensor is provided on the connecting pipeline between the air outlet of the flasher and the air supply port of the compressor.

[0009] In an embodiment of the secondary heat exchange system of the present invention, a fourth temperature and pressure sensor is provided on the connecting pipeline between the liquid outlet of the flasher and the inlet of the second expansion valve.

[0010] The second aspect of the present invention further provides a gas replenishment control method, the gas replenishment control method comprising:

[0011] Acquire a first pressure of a connecting pipe between a compressor and a water-cooled condenser, and a second pressure of a connecting pipe between a battery cooler and a compressor;

[0012] Determine the upper limit and lower limit of the air supply pressure of the connecting pipeline between the flasher and the compressor according to the first pressure and the second pressure;

[0013] The first expansion valve is controlled so that the target air supply pressure of the connecting pipeline between the flash generator and the compressor is between the upper limit air supply pressure and the lower limit air supply pressure.

[0014] In an embodiment of the air supply control method of the present invention, controlling the first expansion valve so that the target air supply pressure of the connecting pipeline between the flash generator and the compressor is between the upper limit air supply pressure and the lower limit air supply pressure includes:

[0015] When the target air supply pressure is less than the lower limit air supply pressure, the opening of the first expansion valve is controlled to increase so that the target air supply pressure is increased to be higher than the lower limit air supply pressure;

[0016] When the target inflated gas pressure is greater than the upper limit inflated gas pressure, the opening of the first expansion valve is controlled to decrease, so that the target inflated gas pressure is reduced to be lower than the upper limit inflated gas pressure.

[0017] In an embodiment of the air supply control method of the present invention, the air supply control method further comprises controlling the first expansion valve to adjust the target air supply pressure according to the air supply superheat.

[0018] In an embodiment of the air supply control method of the present invention, controlling the first expansion valve to adjust the target air supply pressure according to the air supply superheat comprises:

[0019] Collect the target air supply pressure and target air supply temperature to obtain the air supply superheat;

[0020] When the air supply superheat is within the set superheat interval, the first expansion valve is controlled to adjust the target air supply pressure to be between the lower limit air supply pressure and the upper limit air supply pressure;

[0021] When the supplementary air superheat is outside the set superheat range, the first expansion valve is controlled to adjust the target supplementary air pressure to be within the calibrated supplementary air pressure range corresponding to the set superheat range.

[0022] In an embodiment of the gas replenishment control method of the present invention, the gas replenishment control method further includes acquiring a first liquid pressure between the flasher and the second expansion valve, and calibrating the target gas replenishment pressure by using the first liquid pressure.

[0023] The secondary heat exchange system and air supply control method of the present invention adopts the system design of the flasher, so that the gas-liquid mixture after throttling by the first expansion valve enters the flasher for gas-liquid separation, and the gas enters the compressor through the connecting pipeline for air supply, thereby increasing the air intake of the compressor and the heating capacity of the system, improving the air supply efficiency, and thus increasing the heat exchange performance of the system. At the same time, the exhaust temperature of the compressor can be controlled by controlling the air supply pressure to prevent the exhaust temperature from being too high, thereby protecting the compressor and improving the reliability and life of the system. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present invention. For ordinary technicians in this field, other embodiments can be obtained based on these drawings without paying creative work.

[0025] Figure 1 This is a schematic diagram of the system principle in one embodiment of the secondary heat exchange system of the present invention;

[0026] Figure 2 This is a schematic diagram of the system principle in another embodiment of the secondary heat exchange system of the present invention.

[0027] Component number description

[0028] 100, compressor; 200, water-cooled condenser; 210, refrigerant inlet; 220, refrigerant outlet; 230, coolant inlet; 240, coolant outlet; 300, liquid storage tank; 400, first expansion valve; 500, flasher; 600, second expansion valve; 700, battery cooler; 710, first inlet; 720, first outlet; 730, second inlet; 740, second outlet; 800, first temperature and pressure sensor; 900, second temperature and pressure sensor; 1000, third temperature and pressure sensor; 1100, fourth temperature and pressure sensor; 1200, high-temperature coolant circulation system; 1300, low-temperature coolant circulation system. DETAILED DESCRIPTION

[0029] The following is an explanation of the embodiments of the present invention by specific examples, and those skilled in the art can easily understand other advantages and effects of the present invention from the contents disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and the details in this specification can also be modified or changed in various ways based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that the features in the following embodiments and the embodiments can be combined with each other without conflict. It should also be understood that the terms used in the embodiments of the present invention are intended to describe specific embodiments, rather than to limit the scope of protection of the present invention. The test methods for which specific conditions are not specified in the following examples are usually carried out under conventional conditions or according to the conditions recommended by the manufacturers.

[0030] When numerical ranges are given in the embodiments, it should be understood that unless otherwise specified in the present invention, both endpoints of each numerical range and any value between the two endpoints can be selected. Unless otherwise defined, all technical and scientific terms used in the present invention are familiar to those skilled in the art and the description of the present invention, and any method, device and material of the prior art similar or equivalent to the method, device and material in the embodiments of the present invention can also be used to implement the present invention.

[0031] It should be noted that the terms such as "upper", "lower", "left", "right", "middle" and "one" etc. used in this specification are only for the convenience of description and are not intended to limit the scope of implementation of the present invention. Changes or adjustments to their relative relationships, without substantially changing the technical content, should also be regarded as the scope of implementation of the present invention.

[0032] See also Figure 1 to Figure 2 The present invention provides a secondary heat exchange system and an air supply control method. By adopting a flash igniter system design, the gas-liquid mixture after throttling enters the flash igniter for gas-liquid separation, and the gas directly enters the air supply circuit, which increases the air supply flow rate and improves the air supply efficiency, thereby increasing the heat exchange performance of the system.

[0033] See also Figure 1 In order to achieve the above-mentioned and other related purposes, the present invention provides a secondary heat exchange system in a first aspect, which includes a compressor 100, a water-cooled condenser 200, a first expansion valve 400, a flasher 500, a second expansion valve 600 and a battery cooler 700. The compressor 100 compresses low-temperature and low-pressure refrigerant vapor into high-temperature and high-pressure hot steam, and drives the refrigerant in the entire secondary heat exchange system to flow continuously in the system to achieve heat transfer.

[0034] See also Figure 2 The air outlet of the compressor 100 is connected to the refrigerant inlet 210 of the water-cooled condenser 200 through a pipeline. The water-cooled condenser 200 condenses the high-temperature and high-pressure gas refrigerant into a high-pressure liquid through a heat exchange process. The refrigerant outlet 220 of the water-cooled condenser 200 is connected to the liquid inlet of the liquid storage tank 300 through a pipeline. The liquid storage tank 300 stores the high-pressure liquid refrigerant condensed by the water-cooled condenser 200; wherein, the water-cooled condenser 200 also includes a coolant inlet 230 and a coolant outlet 240. The coolant inlet 230 and the coolant outlet 240 of the water-cooled condenser 200 serve as the water inlet and water outlet of the coolant for heat exchange with the refrigerant in the water-cooled condenser 200, and are used for heat exchange with the refrigerant. The coolant has a large specific heat capacity, and it can effectively absorb and take away the heat of the refrigerant, so that the refrigerant gradually condenses into a liquid state, and the temperature of the coolant rises after absorbing the heat. The coolant outlet 240 of the water-cooled condenser 200 is connected to the inlet of the high-temperature coolant circulation system 1200, and the coolant inlet 230 of the water-cooled condenser 200 is connected to the outlet of the high-temperature coolant circulation system 1200. In this embodiment, the high-temperature coolant circulation system 1200 can be any suitable type of device used for heat exchange and cooling of the coolant in other heat exchange systems of the vehicle, and is used to cool the coolant after heat exchange in the water-cooled condenser 200 and then re-enter the water-cooled condenser 200 for heat exchange.

[0035] In the present embodiment, the secondary heat exchange system further includes a liquid storage tank 300, which is disposed on a connecting pipeline between the refrigerant outlet of the water-cooled condenser 200 and the inlet of the first expansion valve 400. Specifically, the inlet pipeline of the first expansion valve 400 is connected to the outlet of the liquid storage tank 300, and converts the high-pressure liquid refrigerant transported by the liquid storage tank 300 into a low-pressure refrigerant liquid, and produces a small amount of flash gas; the outlet pipeline of the first expansion valve 400 is connected to the liquid inlet of the flasher 500, and the first expansion valve 400 passes the throttled gas-liquid mixture into the flasher 500 for gas-liquid separation. The gas outlet of the flasher 500 is connected to the air replenishment port of the compressor 100, and the flash gas enters the compressor 100 through the connecting pipeline to replenish air, thereby increasing the air intake of the compressor 100; the inlet pipeline of the second expansion valve 600 is connected to the liquid outlet of the flasher 500; please refer to Figure 2 The first inlet 710 of the battery cooler 700 is connected to the outlet of the second expansion valve 600, and the battery cooler 700 also includes a second outlet 740 and a second inlet 730; the second outlet 740 of the battery cooler 700 is connected to the inlet of the low-temperature coolant circulation system 1300, and the second inlet 730 of the battery cooler 700 is connected to the outlet of the low-temperature coolant circulation system 1300. The battery cooler 700 uses the refrigerant flowing out of the second expansion valve 600 to exchange heat with the coolant of the low-temperature coolant circulation system 1300. The first outlet 720 of the battery cooler 700 is connected to the air inlet of the compressor 100, and the refrigerant gas after heat exchange at the first outlet 720 of the battery cooler 700 is introduced into the compressor 100 for compression and circulation again. In this embodiment, the low-temperature coolant circulation system 1300 can be any suitable type of device used in other heat exchange systems of the vehicle to heat exchange and heat up the coolant in the low-temperature coolant circulation system 1300, such as the coolant heat exchange and cooling of the battery thermal management system. The heat exchange of the battery cooler 700 absorbs the heat in the battery cooling circuit to help maintain the battery within the optimal operating temperature range, thereby improving the performance and life of the battery.

[0036] The first expansion valve 400 and the second expansion valve 600 can adopt electronic expansion valves or thermal expansion valves; in order to ensure that the refrigerant flow rate can be adjusted according to a preset program and realize the intelligence and accuracy of the refrigerant flow rate control, in this embodiment, the first expansion valve 400 and the second expansion valve 600 adopt electronic expansion valves to meet more precise air replenishment control needs.

[0037] In one embodiment of the secondary heat exchange system of the present invention, a first temperature and pressure sensor 800 is arranged on the connecting pipeline between the air outlet of the compressor 100 and the refrigerant inlet 210 of the water-cooled condenser 200. The first temperature and pressure sensor 800 is used to monitor the exhaust pressure and exhaust temperature of the air outlet of the compressor 100. The first pressure, i.e., the high-pressure pressure Pd, is read by the first temperature and pressure sensor 800, and the upper limit air replenishment pressure Pmax is determined according to the high-pressure pressure Pd.

[0038] In one embodiment of the secondary heat exchange system of the present invention, a third temperature and pressure sensor 1000 is arranged on the connecting pipeline between the first outlet of the battery cooler 700 and the air inlet of the compressor 100. The third temperature and pressure sensor 1000 is used to monitor the intake pressure and intake temperature of the air inlet of the compressor 100. The intake pressure, that is, the low pressure Ps, is read by the third temperature and pressure sensor 1000, so as to determine the lower limit air replenishment pressure Pmin according to the low pressure Ps.

[0039] In one embodiment of the secondary heat exchange system of the present invention, a second temperature and pressure sensor 900 is provided on the connecting pipeline between the air outlet of the flasher 500 and the air supply port of the compressor 100. The second temperature and pressure sensor 900 is used to monitor the air supply pressure and air supply temperature of the air supply port of the compressor 100. The air supply pressure, i.e., the target air supply pressure Pd, is read by the second temperature and pressure sensor 900, and the opening of the first expansion valve 400 is controlled by the control system according to the parameters of the target air supply pressure Pd, so that the target air supply pressure Pd is between the upper limit air supply pressure and the lower limit air supply pressure.

[0040] In one embodiment of the secondary heat exchange system of the present invention, a fourth temperature and pressure sensor 1100 is provided on the connecting pipeline between the liquid outlet of the flasher 500 and the inlet of the second expansion valve 600, and the liquid pressure Pc at the liquid outlet of the flasher 500 is obtained by the fourth temperature and pressure sensor 1100, and the gas replenishment pressure entering the calculation is calibrated by comparing the target gas replenishment pressure Pb with the first liquid pressure Pc.

[0041] In an embodiment of the secondary heat exchange system of the present invention, the first temperature and pressure sensor 800, the second temperature and pressure sensor 900, the third temperature and pressure sensor 1000 and the fourth temperature and pressure sensor 1100 may be integrated temperature and pressure sensors, which may be obtained through general commercial means. It should be noted that in other embodiments, the temperature and pressure sensors may also be a combination of a separate temperature sensor and a pressure sensor to monitor the temperature and pressure in the pipeline at the installation location.

[0042] The second aspect of the present invention further provides a gas replenishment control method, the gas replenishment control method comprising:

[0043] The first pressure of the connecting pipeline between the compressor 100 and the water-cooled condenser 200 is obtained. The first pressure is read from the first temperature and pressure sensor 800, that is, the high pressure Pd. The second pressure of the connecting pipeline between the battery cooler 700 and the compressor 100 is obtained. The second pressure is read from the third temperature and pressure sensor 1000, that is, the low pressure Ps.

[0044] The upper limit air supply pressure and the lower limit air supply pressure of the connecting pipeline between the flasher 500 and the compressor 100, i.e., the upper limit Pmax and the lower limit Pmin, are determined based on the acquired first pressure and the second pressure; the opening of the first expansion valve 400 is controlled by the control system so that the target air supply pressure Pb of the connecting pipeline between the flasher 500 and the compressor 100 is between the upper limit air supply pressure and the lower limit air supply pressure.

[0045] The upper limit Pmax and the lower limit Pmin in the present invention can be obtained based on experience or experiments. In one embodiment of the present invention, the method for determining the upper limit Pmax and the lower limit Pmin based on the high pressure Pd and the low pressure Ps includes obtaining by: Pmax = (a*Pd + b*Ps) / 2; Pmin = √(c*Pd + d*Ps); wherein the coefficients a, b, c, d are calibration coefficients, and the values ​​of a, b, c, d are all greater than 0 and less than or equal to 1, and can be obtained through experiments. Through experimental calibration, the upper limit and lower limit of air supply pressure that make the system performance reach the optimal level under different ambient temperatures and system loads can be found, and they correspond to the optimal air supply pressures of the system under different working conditions.

[0046] In an embodiment of the air supply control method of the present invention, the steps of controlling the first expansion valve 400 so that the target air supply pressure of the connecting pipeline between the flasher 500 and the compressor 100 is between the upper limit air supply pressure and the lower limit air supply pressure include:

[0047] When the target inflated gas pressure Pd is less than the lower limit inflated gas pressure Pmin, the difference (Pb-Pmin) is calculated, and the opening value of the first expansion valve 400 is obtained through the PID control algorithm, so that the opening of the first expansion valve 400 is increased through the control system to increase the refrigerant flow rate and increase the inflated gas pressure, so that the target inflated gas pressure Pd is increased to be higher than the lower limit inflated gas pressure Pmin;

[0048] On the contrary, when the target inflatable gas pressure Pd is greater than the upper limit inflatable gas pressure Pmax, the difference (Pmax-Pb) is calculated, and the opening value of the first expansion valve 400 is obtained through the PID control algorithm, so that the opening of the first expansion valve 400 is controlled to decrease through the control system, so that the target inflatable gas pressure Pd is reduced to be lower than the upper limit inflatable gas pressure Pmax. It should be noted that, in this embodiment, the PID control algorithm is a feedback control algorithm widely used in industrial control systems, and its algorithm and principle are well known in the industry, and will not be repeated here.

[0049] In an embodiment of the air supply control method of the present invention, the air supply control method further comprises controlling the first expansion valve 400 to adjust the target air supply pressure Pd according to the air supply superheat SH.

[0050] In an embodiment of the air supply control method of the present invention, controlling the first expansion valve 400 to adjust the target air supply pressure Pd according to the air supply superheat SH includes:

[0051] The target supply air pressure Pd and the target supply air temperature Tb are collected by the second temperature and pressure sensor 900 to obtain the supply air superheat; the method for obtaining the target supply air superheat SH is: first obtain the target supply air pressure Pd and the target supply air temperature Tb, and the saturation temperature Tsat at this target supply air pressure Pd can be obtained through the refrigerant properties, and the difference between the target supply air temperature Tb and the saturation temperature Tsat is calculated to obtain the supply air superheat, that is: SH = Tb-Tsat.

[0052] When the supply air superheat SH is between the set superheat range (SH1, SH2), the first expansion valve 400 is controlled to adjust the target supply air pressure Pb to be between the lower limit supply air pressure Pmin and the upper limit supply air pressure Pmax; when the supply air superheat SH is outside the set superheat range (SH1, SH2), that is, when SH<SH1 or SH>SH2, the first expansion valve 400 is controlled to adjust the target supply air pressure Pb to be between the calibrated supply air pressure range (Pb1, Pb2) corresponding to the set superheat range (SH1, SH2).

[0053] In this embodiment, the method for further determining Pb1 and Pb2 is: calibrate according to the relationship between the supplementary air pressure and the supplementary air superheat, wherein Pb1 is the supplementary air pressure correspondingly measured by the first temperature and pressure sensor 800 when the supplementary air superheat is SH1; Pb2 is the supplementary air pressure correspondingly measured by the second temperature and pressure sensor 900 when the supplementary air superheat is SH2. The determination of SH1 and SH2 is to calibrate the corresponding relationship between the superheat and the supplementary air pressure through experiments according to actual conditions.

[0054] In one embodiment of the air supply control method of the present invention, the air supply control method also includes obtaining the first liquid pressure Pc between the flasher 500 and the second expansion valve 600, and calibrating the target air supply pressure entering the calculation by comparing the first liquid pressure Pc with the target air supply pressure Pb. Specifically; if (Pc-Pb)>2bar or (Pc-Pb)<-2bar, then the target air supply pressure correction value Pb' entering the calculation is = (Pb+Pc) / 2; wherein Pb is the target air supply pressure measured by the second temperature and pressure sensor 900; conversely, in other cases, the correction value Pb' of the target air supply pressure entering the calculation is the target air supply pressure Pb obtained by the second temperature and pressure sensor 900, that is, the target air supply pressure Pb entering the calculation does not need to be corrected.

[0055] The secondary heat exchange system and air replenishment control method of the present invention adopt a flasher system design, so that the gas-liquid mixture after throttling by the first expansion valve enters the flasher for gas-liquid separation, and the gas enters the air replenishment port of the compressor through the connecting pipeline for air replenishment, thereby increasing the air intake of the compressor and the heating capacity of the system, improving the air replenishment efficiency, and thus increasing the heat exchange performance of the system. At the same time, the air replenishment pressure can be controlled to control the exhaust temperature of the compressor, increase the heat exchange performance, prevent the exhaust temperature from being too high, thereby protecting the compressor and improving the reliability and life of the system. The air replenishment control method of the present invention can achieve the stability of system control, optimize the air replenishment process, and further improve the performance of the secondary heat exchange system. Therefore, the present invention effectively overcomes some practical problems in the prior art and has a high utilization value and use significance.

[0056] The above embodiments are merely illustrative of the principles and effects of the present invention, and are not intended to limit the present invention. Anyone familiar with the art may modify or alter the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or alterations made by a person of ordinary skill in the art without departing from the spirit and technical concept disclosed by the present invention shall still be covered by the claims of the present invention.

Claims

1. A secondary heat exchange system, characterized in that: include: compressor; A water-cooled condenser, wherein a refrigerant inlet of the water-cooled condenser is connected to an air outlet of the compressor; a first expansion valve, wherein an inlet of the first expansion valve is connected to a refrigerant outlet of the water-cooled condenser; A flasher, wherein the liquid inlet of the flasher is connected to the outlet of the first expansion valve; the gas outlet of the flasher is connected to the gas supply port of the compressor; a second expansion valve, wherein the inlet of the second expansion valve is connected to the liquid outlet of the flash device; A battery cooler, wherein a first inlet of the battery cooler is connected to an outlet of the second expansion valve; and a first outlet of the battery cooler is connected to an air inlet of the compressor.

2. The secondary heat exchange system according to claim 1, characterized in that: A liquid storage tank is arranged on the connecting pipeline between the refrigerant outlet of the water-cooled condenser and the inlet of the first expansion valve.

3. The secondary heat exchange system according to claim 1, characterized in that: A first temperature and pressure sensor is provided on the connecting pipeline between the air outlet of the compressor and the refrigerant inlet of the water-cooled condenser; A third temperature and pressure sensor is disposed on a connecting pipeline between the first outlet of the battery cooler and the air inlet of the compressor.

4. The secondary heat exchange system according to claim 1, characterized in that: A second temperature and pressure sensor is arranged on the connecting pipeline between the air outlet of the flasher and the air supply port of the compressor.

5. The secondary heat exchange system according to claim 1, characterized in that: A fourth temperature and pressure sensor is arranged on the connecting pipeline between the liquid outlet of the flasher and the inlet of the second expansion valve.

6. A gas replenishment control method, characterized in that: include: Acquire a first pressure of a connecting pipe between a compressor and a water-cooled condenser, and a second pressure of a connecting pipe between a battery cooler and a compressor; Determine the upper limit and lower limit of the air supply pressure of the connecting pipeline between the flasher and the compressor according to the first pressure and the second pressure; The first expansion valve is controlled so that the target air supply pressure of the connecting pipeline between the flash generator and the compressor is between the upper limit air supply pressure and the lower limit air supply pressure.

7. The air supply control method according to claim 6, characterized in that: Controlling the first expansion valve so that the target air supply pressure of the connecting pipeline between the flash generator and the compressor is between the upper limit air supply pressure and the lower limit air supply pressure includes: When the target air supply pressure is less than the lower limit air supply pressure, the opening of the first expansion valve is controlled to increase so that the target air supply pressure is increased to be higher than the lower limit air supply pressure; When the target inflated gas pressure is greater than the upper limit inflated gas pressure, the opening of the first expansion valve is controlled to decrease, so that the target inflated gas pressure is reduced to be lower than the upper limit inflated gas pressure.

8. The air supply control method according to claim 6, characterized in that: The air supply control method further includes controlling the first expansion valve to adjust the target air supply pressure according to the air supply superheat.

9. The air supply control method according to claim 8, characterized in that: Controlling the first expansion valve to adjust the target supply air pressure according to the supply air superheat includes: Collect the target air supply pressure and target air supply temperature to obtain the air supply superheat; When the air supply superheat is within the set superheat interval, the first expansion valve is controlled to adjust the target air supply pressure to be between the lower limit air supply pressure and the upper limit air supply pressure; When the supplementary air superheat is outside the set superheat range, the first expansion valve is controlled to adjust the target supplementary air pressure to be within the calibrated supplementary air pressure range corresponding to the set superheat range.

10. The air supply control method according to claim 6, characterized in that: The gas supplement control method further comprises: A first liquid pressure between the flash device and the second expansion valve is obtained, and a target gas replenishment pressure is calibrated according to the first liquid pressure.

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