Dehumidification control method, system and vehicle of heat pump system

Abstract

The application provides a dehumidification control method and system of a heat pump system and a vehicle. The method comprises: after receiving a passenger cabin dehumidification request, determining a compressor refrigeration side rotating speed request based on a passenger cabin refrigeration requirement; determining a compressor heating side rotating speed request based on a passenger cabin heating requirement; taking the larger one of the compressor refrigeration side rotating speed request and the compressor heating side rotating speed request as a compressor target rotating speed request; and controlling the compressor based on the compressor target rotating speed request. The application can cancel the PTC heater and reduce the system energy consumption in the dehumidification mode.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of vehicles, in particular to a dehumidification control method and system of a heat pump system and a vehicle. BACKGROUND

[0002] With the development of new energy and the improvement of environmental awareness, the market share of electric vehicles is gradually increasing. In order to improve the energy utilization rate of electric vehicles and reduce the power consumption of the whole vehicle, more and more electric vehicles are equipped with heat pump systems. The mainstream dehumidification scheme of the heat pump system is: under the dehumidification of the evaporator, the PTC heater (high-pressure liquid or air heater) is used to heat the passenger compartment to improve the temperature in the passenger compartment. However, this method consumes additional electric energy and increases the energy consumption of the heat pump system. SUMMARY

[0003] The purpose of the embodiments of the present application is to provide a dehumidification control method, system and vehicle of a heat pump system, which can cancel the PTC heater and reduce the system energy consumption in the dehumidification mode.

[0004] One aspect of the embodiments of the present application provides a control method of a heat pump system. The method comprises: after receiving a passenger compartment dehumidification request, determining a compressor refrigeration side rotation speed request based on a passenger compartment refrigeration demand; determining a compressor heating side rotation speed request based on a passenger compartment heating demand; taking the larger one of the compressor refrigeration side rotation speed request and the compressor heating side rotation speed request as a compressor target rotation speed request; and controlling the compressor based on the compressor target rotation speed request.

[0005] Further, the determination of the compressor refrigeration side rotation speed request based on the passenger compartment refrigeration demand comprises: obtaining a first feedforward rotation speed of the compressor feedforward control based on an evaporator target temperature and an air conditioner air blower target air volume; obtaining an actual evaporator temperature; obtaining a first feedback rotation speed of the compressor closed-loop feedback control based on the actual evaporator temperature and the evaporator target temperature; and obtaining the compressor refrigeration side rotation speed request based on the first feedforward rotation speed and the first feedback rotation speed.

[0006] The determination of the compressor heating side rotation speed request based on the passenger compartment heating demand comprises: obtaining a second feedforward rotation speed of the compressor feedforward control based on a passenger compartment circuit heater core target temperature and a heater core target air volume; obtaining an actual passenger compartment water temperature of the passenger compartment circuit; obtaining a second feedback rotation speed of the compressor closed-loop feedback control based on the actual passenger compartment water temperature and a passenger compartment target water temperature; and obtaining the compressor heating side rotation speed request based on the second feedforward rotation speed and the second feedback rotation speed.

[0007] Further, the heat pump system comprises a first throttling valve, one end of the first throttling valve is connected to the exhaust port of the compressor through the condenser, the other end of the first throttling valve is connected to the suction port of the compressor through the cooler, and the method further comprises: when the actual temperature of the evaporator is higher than the target temperature of the evaporator, or the actual water temperature of the passenger cabin is lower than the target water temperature of the passenger cabin, it is determined that the cold energy is excessive or the heat energy is insufficient, and the first throttling valve is controlled to be opened; when the actual temperature of the evaporator is lower than the target temperature of the evaporator, or the actual water temperature of the passenger cabin is higher than the target water temperature of the passenger cabin, it is determined that the cold energy is insufficient or the heat energy is excessive, and the first throttling valve is controlled to be closed.

[0008] Further, the method further comprises: obtaining the battery temperature of the vehicle; when the battery temperature is higher than a first preset battery temperature threshold, it is determined that the battery has waste heat utilization, the battery circuit is controlled to release heat to the refrigerant circuit, and the passenger cabin is further heated; when the battery temperature is not higher than the first preset battery temperature threshold, it is determined that the battery has no waste heat utilization, the electric drive circuit and the environment heat exchange circuit are controlled to be connected in series and release heat to the refrigerant circuit, and the passenger cabin is further heated; when the battery temperature is lower than a second preset battery temperature threshold, it is determined that the battery can store heat, and the passenger cabin circuit releases heat to the battery circuit; and when the battery temperature is not lower than the second preset battery temperature threshold, it is determined that the battery cannot store heat, and the passenger cabin circuit releases heat to the electric drive circuit and the environment heat exchange circuit connected in series.

[0009] Further, the method further comprises: controlling the opening degree of the first throttling valve, comprising:

[0010] According to the target temperature of the evaporator, the corresponding evaporator saturation pressure is obtained by consulting the refrigerant property table;

[0011] According to the evaporator saturation pressure, a first opening degree of the first throttling valve closed-loop low-pressure control is obtained by biasing a predetermined pressure value downward; the compressor suction superheat degree and the compressor discharge superheat degree are obtained;

[0012] Based on the compressor suction superheat degree and the compressor discharge superheat degree, a second opening degree of the first throttling valve closed-loop superheat degree control is obtained; and

[0013] The first throttling valve is controlled with the smaller one of the first opening degree and the second opening degree.

[0014] Further, the environment heat exchange circuit comprises a radiator, the radiator comprises a fan, and the method further comprises: controlling the rotating speed of the fan, comprising:

[0015] According to the heat pump demand, a first rotating speed of the fan is determined;

[0016] determining a second rotating speed of the fan according to a heat dissipation requirement of the electric drive itself in the electric drive circuit;

[0017] when the difference between the actual water temperature of the passenger cabin and the absolute water temperature of the passenger cabin is less than a predetermined value, or the difference between the target water temperature of the passenger cabin and the actual water temperature of the passenger cabin is higher than a predetermined value, controlling heat dissipation through the environmental heat exchange circuit, and obtaining a third rotating speed of the fan closed-loop control with a target of the smaller one of the difference between the absolute water temperature of the passenger cabin and a predetermined temperature value and the sum of the target water temperature of the passenger cabin and the predetermined temperature value; when the above conditions are not met, controlling the third rotating speed to be 0; and

[0018] controlling the fan with the larger one of the first rotating speed, the second rotating speed and the third rotating speed.

[0019] Further, the heat pump system further comprises a third throttling valve, one end of the third throttling valve being connected to the cooler, the other end of the third throttling valve being connected to the suction port of the compressor through an evaporator, and the method further comprises: controlling the opening degree of the third throttling valve, comprising:

[0020] obtaining a first opening degree of the third throttling valve closed-loop control based on the actual temperature of the evaporator and the target temperature of the evaporator;

[0021] obtaining a compressor rotating speed and an actual superheat degree of the evaporator;

[0022] obtaining a feedforward opening degree of the third throttling valve feedforward control based on the compressor rotating speed;

[0023] obtaining a feedback opening degree of the third throttling valve closed-loop feedback control based on the actual superheat degree of the evaporator and the target superheat degree of the evaporator;

[0024] obtaining a second opening degree of the third throttling valve based on the feedforward opening degree and the feedback opening degree; and

[0025] controlling the third throttling valve with the smaller one of the first opening degree and the second opening degree.

[0026] Further, the battery circuit comprises a battery water pump, and the electric drive circuit comprises an electric drive water pump, and the method further comprises: controlling a rotating speed of the battery water pump, comprising:

[0027] when the first throttling valve is opened to absorb heat from the battery circuit, determining a first rotating speed of the battery water pump based on actual requirements;

[0028] obtaining a second rotating speed of the battery water pump based on the battery's own requirement;

[0029] determining a third rotation speed of the battery water pump based on actual demand when the battery circuit is releasing heat;

[0030] controlling the battery water pump at one of the first rotation speed and the third rotation speed and the greater of the second rotation speed;

[0031] controlling the rotation speed of the electric drive water pump, comprising:

[0032] obtaining a first rotation speed of the electric drive water pump according to heat pump demand when the first throttle valve is open to absorb heat from the electric drive circuit;

[0033] obtaining a second rotation speed of the electric drive water pump based on heat dissipation demand of the electric drive itself; and

[0034] controlling the electric drive water pump at the greater of the first rotation speed and the second rotation speed.

[0035] Another aspect of the embodiments of the present application provides a dehumidification control system of a heat pump system. The dehumidification control system comprises a memory, a processor, and a computer program stored in the memory and executable on the processor, and the processor implements the steps of the dehumidification control method of the heat pump system as described above when executing the computer program.

[0036] Yet another aspect of the embodiments of the present application provides a vehicle. The vehicle comprises a heat pump system and a dehumidification control system of the heat pump system as described above, and the dehumidification control system is used to control the heat pump system.

[0037] The dehumidification control method of the heat pump system of the present application can cancel the intervention of the high-pressure PTC heater in the dehumidification working condition, and only use the high-pressure compressor to cool and condense the passenger cabin, and at the same time use the compressor to heat the passenger cabin, and without switching between high-temperature and low-temperature dehumidification modes, and as much as possible to meet the passenger cabin dehumidification comfort and energy consumption requirements. BRIEF DESCRIPTION OF DRAWINGS

[0038] Figure 1 A structural schematic diagram of a heat pump system of an embodiment of the present application.

[0039] Figure 2 A flowchart of a control method of a heat pump system of an embodiment of the present application.

[0040] Figure 3 A structural schematic diagram of a heat pump system of an embodiment of the present application when absorbing battery waste heat.

[0041] Figure 4 A structural schematic diagram of a heat pump system of an embodiment of the present application when absorbing electric drive waste heat and ambient temperature.

[0042] Figure 5 Structure diagram of a heat pump system according to an embodiment of the present application when storing heat in the battery.

[0043] Figure 6 Structure diagram of a heat pump system according to an embodiment of the present application when discharging heat to the electric drive circuit and the ambient heat exchange circuit.

[0044] Figure 7 Adjustment diagram of various elements in a heat pump system according to an embodiment of the present application in a dehumidification working condition.

[0045] Figure 8 Schematic block diagram of a dehumidification control system of a heat pump system according to an embodiment of the present application. DETAILED DESCRIPTION

[0046] The exemplary embodiments will be described in detail herein with reference to the attached drawings. The following description is made with reference to the accompanying drawings in which like reference numerals refer to like elements, and the term "exemplary" is used herein to mean "serving as an example, instance, or illustration". The following description is not intended to limit the scope of the present application, but is merely intended to describe exemplary embodiments of the present application.

[0047] The dehumidification control method, system and vehicle of the heat pump system according to the present application will be described in detail below with reference to the accompanying drawings. The features in the following embodiments and implementation manners can be combined with each other without conflict.

[0048] Figure 1 A structure diagram of a heat pump system 100 according to an embodiment of the present application is disclosed. As shown in Figure 1 The heat pump system 100 includes a refrigerant circuit 110, a passenger cabin circuit 140, a battery circuit 150, an electric drive circuit 160 and an ambient heat exchange circuit 170.

[0049] The refrigerant circuit 110 includes a first refrigerant circuit 120 and a second refrigerant circuit 130. The first refrigerant circuit 120 includes a compressor 111, a condenser 112, a first expansion valve BEXV, a chiller 113, and a second expansion valve AEXV. An exhaust port of the compressor 111 is connected to a first end of the condenser 112, a second end of the condenser 112 is connected to one end of the first expansion valve BEXV, the other end of the first expansion valve BEXV is connected to a first end of the chiller 113, a second end of the chiller 113 is connected to a suction port of the compressor 111, two ends of the second expansion valve AEXV are respectively connected to the suction port and the exhaust port of the compressor 111 in correspondence, and a third end and a fourth end of the chiller 113 are respectively connected to a third end and a fifth end of a nine-way valve 180. The second refrigerant circuit 130 includes a third expansion valve EEXV and an evaporator 114. One end of the third expansion valve EEXV is connected to the second end of the chiller 113, and the other end of the third expansion valve EEXV is connected to the suction port of the compressor 111 through the evaporator 114.

[0050] The heat pump system 100 further includes the nine-way valve 180 and a three-way valve HCTV. The refrigerant circuit 110 and the passenger cabin circuit 140 can be selectively communicated with the battery circuit 150, the electric drive circuit 160, and the environment heat exchange circuit 170 through the nine-way valve 180 and the three-way valve HCTV.

[0051] The passenger cabin circuit 140 includes a heater core Hex and a heater core water pump HCWP. The heater core Hex is arranged corresponding to the evaporator 114, one end of the heater core water pump HCWP is connected to a third end of the condenser 112, the other end of the heater core water pump HCWP is connected to one end of the heater core Hex and a second end of the nine-way valve 180, and the other end of the heater core Hex is connected to a third end of the three-way valve HCTV. A first end and a second end of the three-way valve HCTV are respectively connected to a fourth end of the condenser 112 and an eighth end of the nine-way valve 180.

[0052] The battery circuit 150 includes a battery 151 and a battery water pump BCPF, and two ends of the battery circuit 150 are respectively connected to a fourth end and a sixth end of the nine-way valve 180.

[0053] The electric drive circuit 160 includes an electric drive 161 and an electric drive water pump EDCP, and two ends of the electric drive circuit 160 are respectively connected to a first end and a ninth end of the nine-way valve 180.

[0054] The environment heat exchange circuit 170 includes a radiator 171, one end of the radiator 171 is connected to a seventh end of the nine-way valve 180, and the other end of the radiator 171 is connected to a ninth end of the nine-way valve 180 and one end of the electric drive water pump EDCP.

[0055] The application provides a dehumidification control method of a heat pump system 100. Figure 2A flowchart of a dehumidification control method of the heat pump system 100 of one embodiment of the present application is disclosed. As shown in Figure 2 The control method of the heat pump system 100 of one embodiment of the present application can include steps S11 to S15.

[0056] In step S11, it is determined whether a passenger cabin dehumidification request is received. When the result of the determination is “Yes”, the process proceeds to steps S12 and S13. Otherwise, the process returns to step S1 to continue the determination.

[0057] In step S12, after receiving the passenger cabin dehumidification request, the compressor refrigeration-side rotation speed request can be determined based on the passenger cabin refrigeration demand.

[0058] In some embodiments, the determination of the compressor refrigeration-side rotation speed request based on the passenger cabin refrigeration demand in step S12 can further include steps S121 to S124.

[0059] In step S121, a first feedforward rotation speed of the compressor pre-feedforward control can be obtained based on the evaporator target temperature and the air conditioning blower target air volume.

[0060] In step S122, the evaporator actual temperature is obtained.

[0061] In step S123, a first feedback rotation speed of the compressor 111 closed-loop feedback control can be obtained based on the evaporator actual temperature and the evaporator target temperature.

[0062] In step S124, the compressor refrigeration-side rotation speed request can be obtained based on the first feedforward rotation speed obtained in step S121 and the first feedback rotation speed obtained in step S123.

[0063] In step S13, the compressor heating-side rotation speed request can be determined based on the passenger cabin heating demand.

[0064] In some embodiments, the determination of the compressor heating-side rotation speed request based on the passenger cabin heating demand in step S13 can further include steps S131 to S134.

[0065] In step S131, a second feedforward rotation speed of the compressor 111 pre-feedforward control can be obtained based on the warm air core target temperature and the warm air core target air volume.

[0066] In step S132, the passenger cabin loop 140 actual water temperature is obtained.

[0067] In step S133, a second feedback rotation speed of the compressor 111 closed-loop feedback control can be obtained based on the passenger cabin actual water temperature and the passenger cabin target water temperature.

[0068] In step S134, a compressor heating-side rotational speed request is obtained based on the second feedforward rotational speed obtained in step S131 and the second feedback rotational speed obtained in step S133.

[0069] In step S14, the larger one of the compressor cooling-side rotational speed request and the compressor heating-side rotational speed request is taken as the compressor target rotational speed request.

[0070] In step S15, the compressor 111 can be controlled based on the compressor target rotational speed request.

[0071] The dehumidification control method of the heat pump system 100 of the present application can cancel the intervention of the high-pressure PTC heater in the dehumidification working condition, and only use the high-pressure compressor 111 to cool and condense the passenger cabin, while using the compressor 111 to heat the passenger cabin, without switching between high-temperature and low-temperature dehumidification modes, so as to meet the dehumidification comfort and energy consumption requirements of the passenger cabin as much as possible.

[0072] The dehumidification control method of the heat pump system 100 of the present application takes the larger one of the compressor cooling-side rotational speed request and the compressor heating-side rotational speed request, so that a single compressor can meet the dehumidification demand in spring and autumn, the same set of logic is used, there is no switching between high-temperature and low-temperature dehumidification, the control is smoother, and the complexity of the software is greatly simplified.

[0073] Continuing to refer to Figure 2 In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further include step S21 and step S22.

[0074] In step S21, it is judged whether the cooling and heating simultaneously reach the target temperature, i.e., whether the actual temperature of the evaporator is equal to the target temperature of the evaporator, or whether the actual water temperature of the passenger cabin is equal to the target water temperature of the passenger cabin.

[0075] When the cooling and heating do not simultaneously reach the target temperature, i.e., the actual temperature of the evaporator is higher than the target temperature of the evaporator, or the actual water temperature of the passenger cabin is lower than the target water temperature of the passenger cabin, the process enters step S22. In step S22, the first throttling valve BEXV is controlled to be opened.

[0076] In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further include step S23 to step S25.

[0077] In step S23, the battery temperature of the vehicle is obtained, and it is judged whether the battery 151 has waste heat. When the result of the judgment is “yes”, the process enters step S24. Otherwise, the process enters step S25.

[0078] In step S24, when the battery temperature is higher than a first preset battery temperature threshold, it can be determined that the battery 151 has waste heat utilization, at this time, the heat pump system 100 can be controlled to be in a heating mode. Figure 3The mode of absorbing the waste heat of the battery shown can control the battery circuit 150 to release heat to the refrigerant circuit 110 through the nine-way valve 180, so as to heat the passenger cabin and reduce the temperature of the battery.

[0079] In step S25, when the battery temperature is not higher than the first preset battery temperature threshold, it can be determined that the battery 151 has no waste heat utilization, at this time, the heat pump system 100 can be controlled to be in the mode of absorbing the waste heat of the electric drive. Figure 4 The mode of absorbing the waste heat of the battery shown can control the battery circuit 150 to release heat to the refrigerant circuit 110 through the nine-way valve 180, so as to heat the passenger cabin and reduce the temperature of the battery.

[0080] In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further include step S26.

[0081] When the cold energy is insufficient or the heat energy is excessive, that is, when the actual temperature of the evaporator is lower than the target temperature of the evaporator, or the actual water temperature of the passenger cabin is higher than the target water temperature of the passenger cabin, the process enters step S26. In step S26, the first throttling valve BEXV is controlled to be closed, and the opening degree of the three-way valve HCTV is controlled based on the target water temperature of the passenger cabin.

[0082] In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further include steps S27 to S29.

[0083] In step S27, the battery temperature of the vehicle is obtained, and it is judged whether the battery 151 can store heat. When the result of the judgment is "yes", the process enters step S28. Otherwise, the process enters step S29.

[0084] In step S28, when the battery temperature is lower than the second preset battery temperature threshold, it can be determined that the battery 151 can store heat, at this time, the heat pump system 100 can be controlled to be in the mode of storing heat of the battery. Figure 5 The mode of storing heat of the battery shown can control the passenger cabin circuit 140 to communicate with the battery circuit 150 through the nine-way valve 180 and the three-way valve HCTV, and control the passenger cabin circuit 140 to release heat to the battery circuit 150, so as to dissipate the excess heat to the battery 151.

[0085] In step S29, when the battery temperature is not lower than the second preset battery temperature threshold, it is determined that the battery 151 cannot store heat, at this time, the heat pump system 100 can be controlled to be in the mode of absorbing the waste heat of the electric drive. Figure 6The mode of heat release to the electric drive circuit 160 and the ambient heat exchange circuit 170 shown can be controlled by the nine-way valve 180 and the three-way valve HCTV to control the electric drive circuit 160 and the ambient heat exchange circuit 170 to be in series communication and in communication with the passenger cabin circuit 140, and the passenger cabin circuit 140 can be controlled to release heat to the electric drive circuit 160 and the ambient heat exchange circuit 170 in series communication, so that the excess heat can be dissipated to the electric drive 161 and the environment.

[0086] The dehumidification control method of the heat pump system 100 of the present application cancels the intervention of the high-pressure PTC heater for heating in the dehumidification working condition, and takes the optimal utilization of energy between the battery 151, the electric drive 161, the passenger cabin, and the environment as the principle, and in combination with the structure of the nine-way valve 180, the heat of the electric drive 161, the battery 151, the radiator 171, the condenser 112, and the heater core Hex can be transferred without limitation, thereby reducing the system energy consumption.

[0087] The dehumidification control method of the heat pump system 100 of the present application cancels the intervention of the high-pressure PTC heater for heating in the dehumidification working condition, and takes the optimal utilization of energy between the battery 151, the electric drive 161, the passenger cabin, and the environment as the principle, and in combination with the structure of the nine-way valve 180, the heat of the electric drive 161, the battery 151, the radiator 171, the condenser 112, and the heater core Hex can be transferred without limitation, thereby reducing the system energy consumption. Figure 7 The dehumidification control method of the heat pump system 100 of the present application cancels the intervention of the high-pressure PTC heater for heating in the dehumidification working condition, and takes the optimal utilization of energy between the battery 151, the electric drive 161, the passenger cabin, and the environment as the principle, and in combination with the structure of the nine-way valve 180, the heat of the electric drive 161, the battery 151, the radiator 171, the condenser 112, and the heater core Hex can be transferred without limitation, thereby reducing the system energy consumption.

[0088] Figure 7 The adjustment schematic diagram of various elements in the heat pump system 100 in the dehumidification working condition of an embodiment of the present application is disclosed. As shown in Figure 7 The dehumidification control method of the heat pump system 100 of the present application cancels the intervention of the high-pressure PTC heater for heating in the dehumidification working condition, and takes the optimal utilization of energy between the battery 151, the electric drive 161, the passenger cabin, and the environment as the principle, and in combination with the structure of the nine-way valve 180, the heat of the electric drive 161, the battery 151, the radiator 171, the condenser 112, and the heater core Hex can be transferred without limitation, thereby reducing the system energy consumption.

[0089] In some embodiments, step S30 can further include steps S31 to S33.

[0090] In step S31, low-pressure control: according to the evaporator target temperature, the corresponding evaporator saturation pressure can be obtained by consulting the refrigerant property table, and then the first opening degree of the first throttling valve BEXV for closed-loop low-pressure control can be obtained by biasing a predetermined pressure value downward from the evaporator saturation pressure.

[0091] In step S32, superheat degree control: the compressor suction superheat degree and the compressor discharge superheat degree are obtained, and then the second opening degree of the first throttling valve BEXV closed-loop superheat degree control can be obtained based on the compressor suction superheat degree and the compressor discharge superheat degree. Specifically, the compressor actual suction pressure, the compressor actual suction temperature, the compressor actual discharge pressure and the compressor actual discharge temperature are obtained; the compressor actual suction pressure corresponding saturated temperature can be obtained by consulting the refrigerant property table according to the compressor actual suction pressure, and the compressor actual discharge pressure corresponding saturated temperature can be obtained by consulting the refrigerant property table according to the compressor actual discharge pressure; then, the compressor actual suction superheat degree can be obtained by subtracting the compressor actual suction pressure corresponding saturated temperature from the compressor actual suction temperature, and the compressor actual discharge superheat degree can be obtained by subtracting the compressor actual discharge pressure corresponding saturated temperature from the compressor actual discharge temperature. The smaller one of the opening degree of the first throttling valve BEXV closed-loop control obtained according to the compressor suction superheat degree and the opening degree of the first throttling valve BEXV obtained according to the compressor discharge superheat degree can be taken as the second opening degree of the first throttling valve BEXV closed-loop superheat degree control.

[0092] In step S33, the first throttling valve BEXV is controlled at the smaller one of the first opening degree obtained in step S31 and the second opening degree obtained in step S32.

[0093] The heat sink 171 comprises a fan. In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further comprise step S40. In step S40, the rotating speed of the fan is controlled.

[0094] In some embodiments, step S40 can further comprise steps S41 to S43.

[0095] In step S41, heat pump demand: the first rotating speed of the fan can be determined according to the heat pump demand.

[0096] In step S42, electric drive heat dissipation: the second rotating speed of the fan can be determined according to the electric drive 161 itself heat dissipation demand in the electric drive circuit 160.

[0097] In step S43, the HCTV opens the high-pressure heat dissipation: when the difference between the actual cabin water temperature and the absolute cabin water temperature is less than a predetermined value, or the difference between the target cabin water temperature and the actual cabin water temperature is higher than a predetermined value, it indicates that the absolute state of the cabin water temperature is too high or the relative state of the cabin water temperature is too high, at this time, the three-way valve HCTV can be controlled to open to dissipate heat through the environmental heat exchange circuit 170, and the third speed of the fan closed-loop control can be obtained by taking the smaller one of the difference between the absolute cabin water temperature and the predetermined temperature value and the sum of the target cabin water temperature and the predetermined temperature value, for example, min(cabin absolute water temperature-5 degrees, cabin relative water temperature+5 degrees). Otherwise, when the above conditions of the absolute state of the cabin water temperature being too high and the relative state of the cabin water temperature being too high are not met, the three-way valve HCTV is closed, and the third speed is 0 at this time.

[0098] In step S44, the fan is controlled at the larger one of the first speed obtained in step S41, the second speed obtained in step S42, and the third speed obtained in step S43.

[0099] In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further include step S50. In step S50, the heating flow control: the speed of the heating water pump HCWP can be determined based on the passenger cabin heating demand, and then the heating water pump HCWP can be controlled based on the speed of the heating water pump HCWP.

[0100] In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further include step S50. In step S60, the opening of the third throttling valve EEXV is controlled.

[0101] In some embodiments, step S60 can further include steps S61 to S63.

[0102] In step S61, the evaporation temperature difference control: the first opening of the third throttling valve EEXV for closed-loop control can be obtained based on the actual evaporator temperature and the target evaporator temperature.

[0103] In step S62, the evaporation superheat control: the compressor speed and the actual evaporator superheat are obtained, the feedforward opening of the third throttling valve EEXV for feedforward control can be obtained based on the compressor speed, the feedback opening of the third throttling valve EEXV for closed-loop feedback control can be obtained based on the actual evaporator superheat and the target evaporator superheat; then, the second opening of the third throttling valve EEXV can be obtained based on the feedforward opening and the feedback opening.

[0104] In step S63, the third throttling valve EEXV is controlled at the smaller one of the first opening obtained in step S61 and the second opening obtained in step S62.

[0105] In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further include step S70. In step S70, the rotation speed of the battery water pump BCPF is controlled.

[0106] In some embodiments, step S70 can further include steps S71 to S74.

[0107] In step S71, BEXV open water pump speed: when the first throttle valve BEXV is opened to absorb heat from the battery circuit 150, a first rotation speed of the battery water pump BCPF is determined based on the actual demand.

[0108] In step S72, battery 151 demand water pump speed: a second rotation speed of the battery water pump BCPF can be obtained based on the battery 151 itself demand.

[0109] In step S73, HCTV open water pump speed: when the three-way valve HCTV is opened to give heat to the battery circuit 150, a third rotation speed of the battery water pump BCPF is determined based on the actual demand.

[0110] In step S74, the battery water pump BCPF is controlled with one of the first rotation speed obtained in step S71 and the third rotation speed obtained in step S73 and the larger one of the second rotation speed obtained in step S72.

[0111] In some embodiments, the dehumidification control method of the heat pump system 100 of the present application can further include step S80. In step S80, the rotation speed of the electric drive water pump EDCP is controlled.

[0112] In some embodiments, step S80 can further include steps S81 to S83.

[0113] In step S81, heat pump demand heat dissipation: when the first throttle valve BEXV is opened to absorb heat from the electric drive circuit 160, a first rotation speed of the electric drive water pump EDCP can be obtained according to the heat pump demand.

[0114] In step S82, electric drive 161 demand heat dissipation: a second rotation speed of the electric drive water pump EDCP can be obtained based on the heat dissipation demand of the electric drive 161 itself.

[0115] In step S83, the electric drive water pump EDCP is controlled with the larger one of the first rotation speed obtained in step S81 and the second rotation speed obtained in step S82.

[0116] After the heat pump system 100 is controlled to enter the corresponding mode in Figures 3 to 6 , the dehumidification control method of the heat pump system 100 of the present application can further include steps S90 to S93. Figure 7The system controls the various components in the heat pump system 100 to ensure that the cabin water temperature and the evaporator 114 temperature reach the target temperature.

[0117] The dehumidification control method of the heat pump system 100 of this application allows for the following dehumidification conditions: when there is excess cooling capacity and insufficient heat capacity in the passenger cabin, the first throttle valve BEXV can be adjusted to utilize the heat absorption of the chiller 113, the electric drive circuit 160+ ambient temperature, or the waste heat from the battery 151 to increase the evaporation temperature, prevent evaporation frost, and also reduce the electric drive temperature or battery temperature. When there is excess heat capacity and insufficient cooling capacity in the passenger cabin, the three-way valve HCTV opens, dissipating the waste heat to the battery 151 or radiating it into the air, ensuring that the battery 151 operates within a better temperature range and storing the heat in the battery 151. The heat can be released again later according to the operating conditions to supplement the heating of the passenger cabin.

[0118] This application also provides a computer-readable storage medium. A computer program is stored on the computer-readable storage medium. When executed by a processor, the computer program implements the steps of the dehumidification control method for the heat pump system as described above.

[0119] This application also provides a dehumidification control system 200 for a heat pump system. Figure 8 A schematic block diagram of a dehumidification control system for a heat pump system according to an embodiment of this application is shown. Figure 6 As shown, a dehumidification control system 200 of a heat pump system according to one embodiment of this application includes a processor 201, an internal bus 202, a network interface 203, a memory 204, and a non-volatile memory 205. It may also include other hardware required for various operations. The processor 201 can read the corresponding computer program from the non-volatile memory 205 into the memory 204 and then run it to implement the steps of the dehumidification control method of the heat pump system as described above. Of course, besides software implementation, this application does not exclude other implementation methods, such as logic devices or a combination of hardware and software, etc. That is to say, the execution entity of the following processing flow is not limited to individual logic units, but can also be hardware or logic components.

[0120] The dehumidification control system 200 of the heat pump system of this application can have similar beneficial technical effects to the dehumidification control method of the heat pump system described above, so it will not be described again here.

[0121] This application also provides a vehicle. The vehicle includes a heat pump system 100 and a dehumidification control system 200 for the heat pump system as described above. The dehumidification control system 200 can control the heat pump system 100.

[0122] The dehumidification control method, system, storage medium and vehicle of the heat pump system provided by the embodiments of the present application are described in detail above. The dehumidification control method, system, storage medium and vehicle of the heat pump system of the embodiments of the present application are described by applying specific examples in this paper, and the above embodiment is only used to help understand the core idea of the present application and does not limit the present application. It should be pointed out that, for those skilled in the art, without departing from the spirit and principles of the present application, some improvements and modifications can be made to the present application, and these improvements and modifications should also fall within the protection scope of the appended claims of the present application.

Claims

1. A dehumidification control method of a heat pump system, characterized by, The method comprises: determining a compressor refrigeration-side rotating speed request based on passenger cabin refrigeration demand after receiving a passenger cabin dehumidification request; determining a compressor heating-side rotating speed request based on passenger cabin heating demand; taking the greater one of the compressor refrigeration-side rotating speed request and the compressor heating-side rotating speed request as a compressor target rotating speed request; and controlling the compressor based on the compressor target rotating speed request.

2. The method of claim 1, wherein, The determination of the compressor refrigeration-side rotating speed request based on passenger cabin refrigeration demand comprises: obtaining a first feedforward rotating speed of the compressor feedforward control based on an evaporator target temperature and an air conditioner air blower target air volume; obtaining an evaporator actual temperature; obtaining a first feedback rotating speed of the compressor closed-loop feedback control based on the evaporator actual temperature and the evaporator target temperature; and obtaining the compressor refrigeration-side rotating speed request based on the first feedforward rotating speed and the first feedback rotating speed. The determination of the compressor heating-side rotating speed request based on passenger cabin heating demand comprises: obtaining a second feedforward rotating speed of the compressor feedforward control based on a passenger cabin loop warm air core target temperature and a warm air core target air volume; obtaining a passenger cabin actual water temperature of the passenger cabin loop; obtaining a second feedback rotating speed of the compressor closed-loop feedback control based on the passenger cabin actual water temperature and a passenger cabin target water temperature; and obtaining the compressor heating-side rotating speed request based on the second feedforward rotating speed and the second feedback rotating speed.

3. The method of claim 2, wherein, The heat pump system comprises a first throttling valve, one end of the first throttling valve is connected to a discharge port of a compressor through a condenser, the other end of the first throttling valve is connected to a suction port of the compressor through a cooler, and the method further comprises: when the evaporator actual temperature is higher than the evaporator target temperature or the passenger cabin actual water temperature is lower than the passenger cabin target water temperature, determining that there is excess cold or insufficient heat, and then controlling the first throttling valve to open; when the evaporator actual temperature is lower than the evaporator target temperature or the passenger cabin actual water temperature is higher than the passenger cabin target water temperature, determining that there is insufficient cold or excess heat, and then controlling the first throttling valve to close.

4. The method of claim 3, wherein, Further comprising: obtaining a battery temperature of a vehicle; when the battery temperature is higher than a first preset battery temperature threshold, determining that the battery has waste heat utilization, then controlling a battery loop to release heat to a refrigerant loop, and further heating the passenger cabin; when the battery temperature is not higher than the first preset battery temperature threshold, determining that the battery has no waste heat utilization, then controlling an electric drive loop and an environment heat exchange loop to be connected in series and release heat to the refrigerant loop, and further heating the passenger cabin; when the battery temperature is lower than a second preset battery temperature threshold, determining that the battery can store heat, then controlling the passenger cabin loop to release heat to the battery loop; and when the battery temperature is not lower than the second preset battery temperature threshold, determining that the battery cannot store heat, then controlling the passenger cabin loop to release heat to the electric drive loop and the environment heat exchange loop connected in series.

5. The method of claim 3, wherein, Further comprising: controlling the opening degree of the first throttling valve, comprising: obtaining a corresponding evaporator saturation pressure by consulting a refrigerant property table according to the evaporator target temperature; The first opening degree of the first throttling valve closed-loop low-pressure control is obtained according to the evaporator saturation pressure being biased downward by a predetermined pressure value; The compressor suction superheat degree and the compressor discharge superheat degree are obtained; The second opening degree of the first throttling valve closed-loop superheat degree control is obtained based on the compressor suction superheat degree and the compressor discharge superheat degree; and The first throttling valve is controlled at the smaller one of the first opening degree and the second opening degree.

6. The method of claim 4, wherein, The environmental heat exchange circuit comprises a radiator comprising a fan, and the method further comprises: The rotating speed of the fan is controlled, comprising: A first rotating speed of the fan is determined according to the heat pump demand; A second rotating speed of the fan is determined according to the electric drive itself heat dissipation demand in the electric drive circuit; When the difference between the actual cabin water temperature and the absolute cabin water temperature is less than a predetermined value, or the difference between the target cabin water temperature and the actual cabin water temperature is higher than a predetermined value, the third rotating speed of the fan closed-loop control is obtained with the smaller one of the difference between the absolute cabin water temperature and a predetermined temperature value and the sum of the target cabin water temperature and the predetermined temperature value as a target; when the above conditions are not met, the third rotating speed is controlled to be 0; and The fan is controlled at the larger one of the first rotating speed, the second rotating speed and the third rotating speed.

7. The method of claim 4, wherein, The heat pump system further comprises a third throttling valve, one end of the third throttling valve being connected to the cooler, and the other end of the third throttling valve being connected to the suction port of the compressor through the evaporator, and the method further comprises: The opening degree of the third throttling valve is controlled, comprising: A first opening degree of the third throttling valve closed-loop control is obtained based on the actual evaporator temperature and the target evaporator temperature; The compressor rotating speed and the actual evaporator superheat degree are obtained; A feedforward opening degree of the third throttling valve feedforward control is obtained based on the compressor rotating speed; A feedback opening degree of the third throttling valve closed-loop feedback control is obtained based on the actual evaporator superheat degree and the target evaporator superheat degree; A second opening degree of the third throttling valve is obtained based on the feedforward opening degree and the feedback opening degree; and The third throttling valve is controlled at the smaller one of the first opening degree and the second opening degree.

8. The method of claim 4, wherein, The battery circuit comprises a battery water pump, and the electric drive circuit comprises an electric drive water pump, and the method further comprises: The rotating speed of the battery water pump is controlled, comprising: A first rotating speed of the battery water pump is determined based on the actual demand when the first throttling valve is opened to absorb heat from the battery circuit; A second rotating speed of the battery water pump is obtained based on the battery itself demand; A third rotating speed of the battery water pump is determined based on the actual demand when heat is given to the battery circuit; and The battery water pump is controlled at the larger one of the first rotating speed and the third rotating speed and the second rotating speed; The rotating speed of the electric drive water pump is controlled, comprising: A first rotating speed of the electric drive water pump is obtained according to the heat pump demand when the first throttling valve is opened to absorb heat from the electric drive circuit; obtaining a second rotating speed of the electric drive water pump based on self-heat dissipation requirement of the electric drive; controlling the electric drive water pump at a larger one of the first rotating speed and the second rotating speed.

9. A dehumidification control system for a heat pump system, characterized by, A computer program product comprising a memory, a processor and a computer program stored on the memory and loadable on the processor, characterized in that the processor implements the steps of the dehumidification control method of the heat pump system according to any one of claims 1 to 8 when executing the computer program.

10. A vehicle characterized by comprising: A dehumidification control system of a heat pump system, comprising the heat pump system and the dehumidification control system according to claim 9, the dehumidification control system being configured to control the heat pump system.

Images