Double-evaporation heat pump system, control method and vehicle

Abstract

According to the double-evaporation heat pump system, the compression reversing part, the front end heat exchange part, the throttling assembly and the tail end heat exchange part are communicated to form a two-way heat pump cycle, a simple rectification structure with two one-way valves is adopted, high-pressure refrigerants are shunted from the two ends of the two-way main throttler, the refrigerants are supplied to the dehumidification evaporator through the dehumidification throttler, and therefore the heat exchange efficiency is improved. Refrigeration and dehumidification under all working conditions of the vehicle are met, the dehumidification evaporator and the main heat exchanger form a double-evaporation structure, and idling of the main heat exchanger is avoided; the size of the air conditioning box can be kept unchanged while the evaporation heat exchange area is doubled, or the heat exchange capacity is kept unchanged while the thickness of the dehumidification evaporator is reduced, and therefore the purposes of reducing wind resistance and improving energy efficiency are achieved. The operation control method is simple and reliable, the electrically-driven vehicle provided by the invention is low in cost and high in energy efficiency, and comfort and driving safety are guaranteed.

Description

Technical Field

[0001] The present invention belongs to the technical field of vehicles, and particularly relates to a dual-evaporation heat pump system, a control method, and a vehicle. Background Art

[0002] To ensure driving safety and cabin comfort, the vehicle air-conditioning boxes in the prior art all adopt a two-stage heat exchange structure of front cooling and rear heating to achieve cabin refrigeration, heating, dehumidification, and defogging. On the one hand, due to the small space of the air-conditioning box, the design of the frontal area of the front-stage refrigeration evaporator is limited. On the other hand, the heat exchanger for rear-stage heating is often in an idle state, resulting in difficulty in improving the energy efficiency of the thermal management system. This defect is particularly prominent in electric vehicles with limited battery capacity. Summary of the Invention

[0003] To overcome the defect of low energy efficiency in the prior art, the present invention discloses a dual-evaporation heat pump system, which simply and low-costly improves the energy efficiency of the thermal management system.

[0004] A technical solution of a dual-evaporation heat pump system disclosed by the present invention, a dual-evaporation heat pump system, includes a compression and commutation part, a front-end heat exchange part, a throttling assembly, and a terminal heat exchange part that are interconnected to form a heat pump cycle. The compression and commutation part includes a compressor and a commutation valve that are connected to form a refrigerant compression and commutation structure. The front-end heat exchange part includes a heat source heat exchanger. The throttling assembly includes a two-way main throttle, a first one-way valve, a second one-way valve, and a dehumidification throttle. The inlets of the first one-way valve and the second one-way valve are respectively connected to both ends of the two-way main throttle, and the outlets of the first one-way valve and the second one-way valve are connected to the inlet of the dehumidification throttle. The terminal heat exchange part includes an air-conditioning box and a dehumidification evaporator and a main heat exchanger arranged in sequence along the wind direction therein. The two commutation ports of the compression and commutation part are respectively connected to the gaseous refrigerant interfaces of the heat source heat exchanger and the main heat exchanger. The liquid refrigerant interfaces of the heat source heat exchanger and the main heat exchanger are respectively connected to both ends of the two-way main throttle. The liquid and gaseous refrigerant interfaces of the dehumidification evaporator are respectively connected to the outlet of the dehumidification throttle and the low-pressure inlet of the compression and commutation part.

[0005] Further, the front-end heat exchange part further includes a first circulation pump and an electric drive heat exchanger. The heat source heat exchanger is a three-medium heat exchanger with a three-channel structure. The first circulation pump, the heat source heat exchanger, and the electric drive heat exchanger are connected in series to form a first circulation loop.

[0006] Optionally, the front-end heat exchange part further includes a first circulation pump, an electric drive heat exchanger, and an out-of-cabin radiator. The heat source heat exchanger is a plate heat exchanger with a two-channel structure. The first circulation pump, the heat source heat exchanger, the electric drive heat exchanger, and the out-of-cabin radiator are connected in series to form a first circulation loop.

[0007] Further, the throttling component further includes a cold plate throttler, and the end heat exchange part further includes a battery direct cooling plate. The inlet of the cold plate throttler is communicated with the inlet of the dehumidifying throttler, the outlet of the cold plate throttler is communicated with the liquid refrigerant interface of the battery direct cooling plate, and the gas refrigerant interface of the battery direct cooling plate is communicated with the low-pressure inlet of the compression commutation part or the medium-pressure air supplement and enthalpy increase inlet.

[0008] Optionally, the end heat exchange part further includes a second circulation pump and a battery heat exchanger. The main heat exchanger is a three-medium heat exchanger with a three-channel structure. The second circulation pump, the main heat exchanger, and the battery heat exchanger are connected in series to form a second circulation loop.

[0009] Further, a multi-way valve is further included. The first circulation loop and the second circulation loop are communicated with each other through the multi-way valve. By adjusting the valve core of the multi-way valve, three different cycles of battery electric drive heat dissipation, direct heat recovery, and indirect heat recovery are formed.

[0010] The present invention also discloses a control method, including three operating modes of refrigeration, heating, and constant temperature dehumidification, and the dual-evaporation heat pump system described in any one of the preceding items.

[0011] The present invention also discloses a vehicle, and the thermal management system of the vehicle is the dual-evaporation heat pump system described in any one of the preceding items.

[0012] The dual-evaporation heat pump system disclosed by the present invention adopts a simple rectification structure with two one-way valves to split high-pressure refrigerant from both ends of the bidirectional main throttler, and supplies refrigerant to the dehumidifying evaporator through the dehumidifying throttler to meet the refrigeration and dehumidification under all working conditions of the vehicle. The dehumidifying evaporator and the main heat exchanger form a dual-evaporation structure, avoiding the idle of the main heat exchanger; it can double the evaporation heat exchange area while keeping the volume of the air conditioner box unchanged, or reduce the thickness of the dehumidifying evaporator while keeping the heat exchange capacity unchanged, so as to achieve the purpose of reducing wind resistance and improving energy efficiency; its operation control method is simple and reliable, and the electric drive vehicle of the present invention has low cost, high energy efficiency, and guaranteed comfort and driving safety. Description of the Drawings Figure 1 is the first commutation basic structure schematic diagram of the dual-evaporation heat pump system of the present invention; Figure 2 is the second commutation basic structure schematic diagram of the dual-evaporation heat pump system of the present invention; Figure 3 is the first schematic diagram of the dual-evaporation heat pump system of the present invention including electric drive heat management; Figure 4 is the second schematic diagram of the dual-evaporation heat pump system of the present invention including electric drive heat management; Figure 5 is the first schematic diagram of the dual-evaporation heat pump system of the present invention including battery heat management; Figure 6 is the second schematic diagram of the dual-evaporation heat pump system of the present invention including battery heat management.

[0014] Reference numerals: 1, compression and commutation section; 10, compressor; 11, commutation valve; 111, first valve; 112, second valve; 113, third valve; 114, fourth valve; 2, front-end heat exchange section; 20, first circulation pump; 21, heat source heat exchanger; 22, electric drive heat exchanger; 23, out-of-cabin radiator; 3, throttling assembly; 30, two-way main throttle; 31, first check valve; 32, second check valve; 33, dehumidification throttle; 34, cold plate throttle; 4, end heat exchange section; 40, second circulation pump; 41, main heat exchanger; 42, dehumidification evaporator; 43, battery direct cold plate; 44, battery heat exchanger. Detailed implementation manners

[0015] As Figure 1 , Figure 2 shown, it is a schematic diagram of the basic principle structure of the dual-evaporation heat pump system of the present invention, including a compression and commutation section 1, a front-end heat exchange section 2, a throttling assembly 3, and an end heat exchange section 4 that are interconnected to form a heat pump cycle. The compression and commutation section 1 includes a compressor 10 and a commutation valve 11 that are connected to form a refrigerant compression and commutation structure. In Figure 1 the basic principle structure of the dual-evaporation heat pump system shown, the commutation valve 11 uses a single four-way valve to complete refrigerant commutation. In Figure 2 the basic principle structure of the dual-evaporation heat pump system shown, the commutation valve 11 uses 4 globe valves combined with each other to complete refrigerant commutation. The functions of these two different commutation structures are completely the same in the solution of the present invention, and their commutation principles are basic common knowledge in the art. The front-end heat exchange section 2 includes a heat source heat exchanger 21. The throttling assembly 3 includes a two-way main throttle 30, a first check valve 31, a second check valve 32, and a dehumidification throttle 33. The inlets of the first check valve 31 and the second check valve 32 are respectively connected to both ends of the two-way main throttle 30, and the outlets of the first check valve 31 and the second check valve 32 are connected to the inlet of the dehumidification throttle 33. The end heat exchange section 4 includes an air-conditioning box and a dehumidification evaporator 42 and a main heat exchanger 41 arranged in sequence along the wind direction therein. The two commutation ports of the compression and commutation section 1 are respectively connected to the gaseous refrigerant interfaces of the heat source heat exchanger 21 and the main heat exchanger 41. The liquid refrigerant interfaces of the heat source heat exchanger 21 and the main heat exchanger 41 are respectively connected to both ends of the two-way main throttle 30. The liquid and gaseous refrigerant interfaces of the dehumidification evaporator 42 are respectively connected to the outlet of the dehumidification throttle 33 and the low-pressure inlet of the compression and commutation section 1.

[0016] The dual-evaporation heat pump system of this embodiment adopts a simple rectification structure with two one-way valves to split high-pressure refrigerant from both ends of the two-way main throttle 30 and supply refrigerant to the dehumidifying evaporator 42 through the dehumidifying throttle 33, meeting the refrigeration and dehumidification requirements under all vehicle operating conditions. The dehumidifying evaporator 42 and the main heat exchanger 41 form a dual-evaporation structure, avoiding the idleness of the main heat exchanger 41. It can double the evaporation heat exchange area while keeping the volume of the air-conditioning box unchanged, or reduce the thickness of the dehumidifying evaporator while maintaining the heat exchange capacity, thereby achieving the purpose of reducing wind resistance and improving energy efficiency.

[0017] As Figure 3 shown, the dual-evaporation heat pump system of the present invention includes a first structure for electric drive heat management, including the aforementioned basic structure. The front-end heat exchange part 2 further includes a first circulation pump 20 and an electric drive heat exchanger 22. The heat source heat exchanger 21 is a three-medium heat exchanger with a three-channel structure. The first circulation pump 20, the heat source heat exchanger 21, and the electric drive heat exchanger 22 are connected in series to form a first circulation loop.

[0018] In the dual-evaporation heat pump system of this embodiment, the electric drive heat exchanger 22 can not only discharge the electric drive waste heat to the ambient air outside the vehicle through the heat source heat exchanger 21 with a three-medium structure, but also conveniently realize the heat pump cycle to recover the electric drive waste heat and improve energy efficiency. It can also directly use the heat generated by the electric drive to defrost the heat source heat exchanger 21, achieving efficient defrosting without reversing the refrigerant in the heat pump system.

[0019] As Figure 4 shown, the dual-evaporation heat pump system of the present invention includes a second structure for electric drive heat management, including the aforementioned basic structure. The front-end heat exchange part 2 further includes a first circulation pump 20, an electric drive heat exchanger 22, and an out-of-cabin radiator 23. The heat source heat exchanger 21 is a plate heat exchanger with a two-channel structure. The first circulation pump 20, the heat source heat exchanger 21, the electric drive heat exchanger 22, and the out-of-cabin radiator 23 are connected in series to form a first circulation loop.

[0020] In the dual-evaporation heat pump system of this embodiment, the heat source heat exchanger 21 is a plate heat exchanger with a two-channel structure, which is more convenient for the integration of the heat pump system and simplifies the heat exchange between the vehicle and the outside of the cabin. The first circulation loop formed by connecting the first circulation pump 20, the heat source heat exchanger 21, the electric drive heat exchanger 22, and the out-of-cabin radiator 23 exchanges heat step by step to discharge the heat pump and electric drive waste heat together to the ambient air outside the vehicle through the out-of-cabin radiator 23. It can also conveniently realize the heat pump cycle to directly recover the electric drive waste heat through the heat source heat exchanger 21 with a two-channel plate structure and improve energy efficiency. It can also directly use the heat generated by the electric drive to defrost the out-of-cabin radiator 23, achieving efficient defrosting without reversing the refrigerant in the heat pump system.

[0021] As Figure 5As shown, the dual evaporator heat pump system of the present invention includes a first structure of battery thermal management, including the aforementioned basic structure, the throttling component 3 also includes a cold plate throttle 34, the terminal heat exchange part 4 also includes a battery direct cooling plate 43, the inlet of the cold plate throttle 34 is connected to the inlet of the dehumidification throttle 33, the outlet of the cold plate throttle 34 is connected to the liquid refrigerant interface of the battery direct cooling plate 43, and the gaseous refrigerant interface of the battery direct cooling plate 43 is connected to the low-pressure inlet or the medium-pressure air replenishment inlet of the compression reversing part 1.

[0022] The dual evaporation heat pump system of this embodiment adopts a direct expansion evaporation method of the battery direct cooling plate 43 to ensure the battery charging and discharging temperature, and has a simple structure, low cost and fast cooling.

[0023] like Figure 6 As shown, the dual evaporator heat pump system of the present invention includes a second structure of battery thermal management, including the aforementioned basic structure, the terminal heat exchange unit 4 also includes a second circulation pump 40 and a battery heat exchanger 44, the main heat exchanger 41 is a three-medium heat exchanger with a three-channel structure, and the second circulation pump 40, the main heat exchanger 41, and the battery heat exchanger 44 are connected in series to form a second circulation loop.

[0024] The dual evaporation heat pump system of the present embodiment adopts a second circulation loop driven by a second circulation pump 40, which simply and conveniently realizes the heat exchange between the main heat exchanger 41 and the battery heat exchanger 44, has high temperature control accuracy and is widely used. The second circulation pump 40 of the present embodiment can select either an ordinary liquid circulation pump or a high-efficiency phase-change fluorine pump.

[0025] The dual evaporator heat pump system of the present invention also includes a multi-way valve, the first circulation loop and the second circulation loop are interconnected via the multi-way valve, and the valve core of the multi-way valve is adjusted to form three different cycles of battery electric drive heat dissipation, direct heat recovery, and indirect heat recovery; the multi-way valve structure and the three different cycles formed are technologies that have been widely used in the field and will not be elaborated here.

[0026] The present invention provides a control method, including three operation modes of cooling, heating and constant temperature dehumidification and Figures 1 to 6 For any of the double evaporator heat pump systems shown, the three operating modes are described in detail as follows: In the refrigeration mode, the refrigerant compressed to high pressure by the compressor 10 is reversed by the four-way valve 11 (or the reversing valve group composed of the first valve 111, the first valve 112, the first valve 113, and the first valve 114), and is output from the first reversing port of the compression reversing section 1. It flows through the heat source heat exchanger 21 to release heat and condense into a liquid refrigerant. One path flows through the two-way main throttle 30 into the main heat exchanger 41 for refrigeration evaporation, and returns to the suction port of the compressor 10 through the second reversing port of the compression reversing section 1. The other path flows through the first one-way valve 31 and the dehumidification throttle 33, and flows into the dehumidification evaporator 42 for refrigeration evaporation, and returns to the suction port of the compressor 10 through the low-pressure interface of the compression reversing section 1. The refrigerants after evaporation in the two paths are combined into one path, forming a front and rear double-evaporation refrigeration cycle structure of the dehumidification evaporator 42 and the main heat exchanger 41; In the heating mode: the refrigerant compressed to high pressure by the compressor 10 is reversed by the four-way valve 11 (or the reversing valve group composed of the first valve 111, the first valve 112, the first valve 113, and the first valve 114), and is output from the second reversing port of the compression reversing section 1. It flows through the main heat exchanger 41 to release heat and condense into a liquid refrigerant, flows through the two-way main throttle 30 into the heat source heat exchanger 21 for refrigeration evaporation, and returns to the suction port of the compressor 10 through the first reversing port of the compression reversing section 1, forming a simple heat pump cycle structure that absorbs low-grade heat energy from the heat source heat exchanger 21, compresses it into high-grade heat energy by the compressor 10, and condenses and releases heat in the main heat exchanger 41; In the constant temperature and dehumidification mode: the refrigerant compressed to high pressure by the compressor 10 is reversed by the four-way valve 11 (or the reversing valve group composed of the first valve 111, the first valve 112, the first valve 113, and the first valve 114), and is output from the second reversing port of the compression reversing section 1. It flows through the main heat exchanger 41 to release heat and condense into a liquid refrigerant. One path flows through the two-way main throttle 30 into the heat source heat exchanger 21 for refrigeration evaporation, and returns to the suction port of the compressor 10 through the first reversing port of the compression reversing section 1. The other path flows through the first one-way valve 31 and the dehumidification throttle 33, and flows into the dehumidification evaporator 42 for evaporation and cooling and dehumidification, and returns to the suction port of the compressor 10 through the low-pressure interface of the compression reversing section 1. The refrigerants after evaporation in the two paths are combined into one path, forming a constant temperature or heating heat pump cycle structure in which the air in the air handling unit is first dehumidified by the dehumidification evaporator 42 and then reheated by the main heat exchanger 41.

[0027] A vehicle of the present invention, the thermal management system of the vehicle adopts the dual-evaporation heat pump system described in any one of the preceding items, with simple structure, stable operation, high energy efficiency, small volume, and low cost.

Claims

1. A double-evaporation heat pump system, comprising a compression and commutation part (1), a front-end heat exchange part (2), a throttling component (3) and a terminal heat exchange part (4) that are interconnected to form a heat pump cycle, characterized in that, The compression reversing part (1) comprises a compressor (10) and a reversing valve (11) which are connected to form a refrigerant compression reversing structure; the front end heat exchange part (2) comprises a heat source heat exchanger (21); the throttling assembly (3) comprises a two-way main throttle (30), a first one-way valve (31), a second one-way valve (32) and a dehumidification throttle (33); the inlets of the first one-way valve (31) and the second one-way valve (32) are respectively connected to the two ends of the two-way main throttle (30); the outlets of the first one-way valve (31) and the second one-way valve (32) are connected to the dehumidification throttle (33); ), the terminal heat exchange section (4) comprises an air conditioning box and a dehumidification evaporator (42) and a main heat exchanger (41) arranged in sequence along the wind direction; the two reversing ports of the compression reversing section (1) are respectively connected to the gaseous refrigerant interfaces of the heat source heat exchanger (21) and the main heat exchanger (41); the liquid refrigerant interfaces of the heat source heat exchanger (21) and the main heat exchanger (41) are respectively connected to the two ends of the bidirectional main throttle (30); the liquid and gaseous refrigerant interfaces of the dehumidification evaporator (42) are respectively connected to the outlet of the dehumidification throttle (33) and the low-pressure inlet of the compression reversing section (1).

2. The double-evaporation heat pump system according to claim 1, characterized in that, The front-end heat exchange unit (2) further comprises a first circulation pump (20) and an electrically driven heat exchanger (22); the heat source heat exchanger (21) is a three-medium heat exchanger with a three-channel structure; the first circulation pump (20), the heat source heat exchanger (21) and the electrically driven heat exchanger (22) are connected in series to form a first circulation loop.

3. The double-evaporation heat pump system according to claim 1, wherein, The front end heat exchange unit (2) further comprises a first circulation pump (20), an electric drive heat exchanger (22), and an offboard radiator (23); the heat source heat exchanger (21) is a plate heat exchanger with a two-channel structure; the first circulation pump (20), the heat source heat exchanger (21), the electric drive heat exchanger (22), and the offboard radiator (23) are connected in series to form a first circulation loop.

4. The double-evaporation heat pump system according to any one of claims 1 to 3, characterized in that, The throttling assembly (3) further includes a cold plate throttle (34), and the terminal heat exchange portion (4) further includes a battery direct cooling plate (43). The inlet of the cold plate throttle (34) is connected to the inlet of the dehumidification throttle (33), and the outlet of the cold plate throttle (34) is connected to the liquid refrigerant interface of the battery direct cooling plate (43). The gaseous refrigerant interface of the battery direct cooling plate (43) is connected to the low-pressure inlet or the medium-pressure air replenishment inlet of the compression reversing portion (1).

5. The double-evaporation heat pump system according to any one of claims 1 to 3, characterized in that The terminal heat exchange unit (4) further comprises a second circulation pump (40) and a battery heat exchanger (44); the main heat exchanger (41) is a three-medium heat exchanger with a three-channel structure; the second circulation pump (40), the main heat exchanger (41) and the battery heat exchanger (44) are connected in series to form a second circulation loop.

6. The dual-evaporation heat pump system according to claim 5, characterized in that, It also includes a multi-way valve, wherein the first circulation loop and the second circulation loop are interconnected via the multi-way valve, and the valve core of the multi-way valve is adjusted to form three different circulations of battery electric drive heat dissipation, direct heat recovery, and indirect heat recovery.

7. A control method, characterized in that, The invention comprises three operation modes: cooling, heating and constant temperature dehumidification, and a dual evaporation heat pump system as described in any one of claims 1 to 6.

8. A vehicle, characterized in that, The thermal management system of the vehicle is a dual evaporator heat pump system as claimed in any one of claims 1 to 6.

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