CN217294196U - Vehicle thermal management system and vehicle - Google Patents

Vehicle thermal management system and vehicle Download PDF

Info

Publication number
CN217294196U
CN217294196U CN202220973600.6U CN202220973600U CN217294196U CN 217294196 U CN217294196 U CN 217294196U CN 202220973600 U CN202220973600 U CN 202220973600U CN 217294196 U CN217294196 U CN 217294196U
Authority
CN
China
Prior art keywords
heat exchanger
refrigerant
outlet
transfer fluid
inlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN202220973600.6U
Other languages
Chinese (zh)
Inventor
尤古塔纳·贝努利
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mind Electronics Appliance Co Ltd
Original Assignee
Mind Electronics Appliance Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mind Electronics Appliance Co Ltd filed Critical Mind Electronics Appliance Co Ltd
Priority to CN202220973600.6U priority Critical patent/CN217294196U/en
Application granted granted Critical
Publication of CN217294196U publication Critical patent/CN217294196U/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/70—Energy storage systems for electromobility, e.g. batteries

Landscapes

  • Air-Conditioning For Vehicles (AREA)

Abstract

The utility model provides a vehicle thermal management system and vehicle. The vehicle thermal management system includes: the refrigerant fluid loop is used for flowing refrigerant fluid and comprises a compressor 1, a first heat exchanger 2, a high-pressure liquid drying tank 25, a heat transfer fluid-low-pressure refrigerant heat exchanger 22, an outdoor heat exchanger 3, a first expansion valve 4, an indoor heat exchanger 5 and a first flow path 13 which is selectively communicated or cut off; and a heat transfer fluid circuit in which the heat transfer fluid flows, the heat transfer fluid circuit including the first heat exchanger 2, the first water pump 6, the heat transfer fluid-low pressure refrigerant heat exchanger 22, and the outdoor radiator 7. The utility model discloses can reduce vehicle thermal management system's cost, and the superheat degree that need not the refrigerant of control compressor entrance equals 0 just, can reduce vehicle thermal management system's control complexity.

Description

Vehicle thermal management system and vehicle
Technical Field
The utility model relates to a vehicle thermal management technical field especially relates to a vehicle thermal management system and vehicle.
Background
At present, in a heat pump air conditioning system of an existing vehicle, a high-pressure liquid drying tank is generally arranged in front of an inlet of a compressor, and the high-pressure liquid drying tank is used for separating a refrigerant to be introduced into the compressor into a gaseous refrigerant and a liquid refrigerant and only returning the gaseous refrigerant to the compressor.
However, in such a structure, the superheat degree of the refrigerant at the inlet of the compressor needs to be controlled, so that the superheat degree of the refrigerant at the inlet of the compressor is exactly equal to 0, however, controlling the superheat degree of the refrigerant at the inlet of the compressor inevitably increases the control complexity of the vehicle thermal management system, which leads to higher control complexity of the vehicle thermal management system, and the cost is increased by arranging the high-pressure liquid drying tank in front of the inlet of the compressor.
SUMMERY OF THE UTILITY MODEL
The embodiment of the utility model provides a vehicle thermal management system and vehicle to solve current vehicle thermal management system control complexity and the higher problem of cost.
In a first aspect, an embodiment of the present invention provides a vehicle thermal management system, including:
the refrigerant fluid loop is used for flowing refrigerant fluid and comprises a compressor 1, a first heat exchanger 2, a high-pressure liquid drying tank 25, a heat transfer fluid-low-pressure refrigerant heat exchanger 22, an outdoor heat exchanger 3, a first expansion valve 4, an indoor heat exchanger 5 and a first flow path 13 which is selectively communicated or cut off;
a heat transfer fluid circuit in which a heat transfer fluid flows, the heat transfer fluid circuit including a first heat exchanger 2, a first water pump 6, a heat transfer fluid-low pressure refrigerant heat exchanger 22, and an outdoor radiator 7;
an outlet of the compressor 1 is connected with a refrigerant inlet of the first heat exchanger 2, a refrigerant outlet of the first heat exchanger 2 is connected with an inlet of the high-pressure liquid drying tank 25, a liquid outlet of the high-pressure liquid drying tank 25 is connected with an inlet of the outdoor heat exchanger 3, an outlet of the outdoor heat exchanger 3 is connected with an inlet of the first expansion valve 4 through a first connection point 44 and a second connection point 41, an outlet of the first expansion valve 4 is connected with an inlet of the indoor heat exchanger 5, an outlet of the indoor heat exchanger 5 is connected with an inlet of the first flow path 13 through a third connection point 39, and an outlet of the first flow path 13 is connected with an inlet of the compressor 1 through a fourth connection point 42 and a fifth connection point 43;
the outlet of the outdoor heat exchanger 3 is also connected with the refrigerant inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 through a first connection point 44, and the refrigerant outlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 is connected with the inlet of the compressor 1 through a fifth connection point 43;
the heat transfer fluid outlet of the first heat exchanger 2 is connected with the inlet of the outdoor radiator 7, and the outlet of the outdoor radiator 7 is connected with the heat transfer fluid inlet of the first heat exchanger 2 through a sixth connecting point 45; the first water pump 6 is provided on a flow path between the outlet of the heat transfer fluid of the first heat exchanger 2 and the inlet of the outdoor radiator 7, or the first water pump 6 is provided on a flow path between the outlet of the outdoor radiator 7 and the inlet of the heat transfer fluid of the first heat exchanger 2;
the heat transfer fluid outlet of the first heat exchanger 2 is also connected to the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 via a seventh connection point 46, and the heat transfer fluid outlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 is connected to the heat transfer fluid inlet of the first heat exchanger 2 via an eighth connection point 47 and a sixth connection point 45.
In a second aspect, an embodiment of the present invention provides a vehicle including the vehicle thermal management system of the first aspect or any one of the possible implementations of the first aspect.
The embodiment of the utility model provides a vehicle thermal management system and vehicle through set up heat transfer fluid-low pressure refrigerant heat exchanger before the compressor, makes the refrigerant that flows into the compressor and the heat transfer fluid that first heat exchanger flows out carry out the heat exchange to the refrigerant that makes the entering compressor satisfies the user demand, can reduce vehicle thermal management system's cost, and need not to control the degree of superheat of the refrigerant of compressor entrance and equals 0 just, can reduce vehicle thermal management system's control complexity.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for the embodiments or the prior art descriptions will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without inventive labor.
Fig. 1 is a schematic structural diagram of a vehicle thermal management system according to an embodiment of the present invention;
FIG. 2 is a schematic structural diagram of a vehicle thermal management system according to another embodiment of the present invention;
fig. 3 is a schematic structural diagram of a vehicle thermal management system according to still another embodiment of the present invention;
fig. 4 is a schematic structural diagram of a vehicle thermal management system according to another embodiment of the present invention.
Detailed Description
In order to make the technical solution better understood by those skilled in the art, the technical solution in the embodiment of the present invention will be clearly described below with reference to the drawings in the embodiment of the present invention, and it is obvious that the described embodiment is a part of the embodiment of the present invention, and not a whole embodiment. All other embodiments obtained by a person of ordinary skill in the art based on the embodiments in the present disclosure without any creative effort shall fall within the protection scope of the present disclosure.
The terms "include" and any other variations in the description and claims of this document and the above-described figures, mean "include but not limited to", and are intended to cover non-exclusive inclusions and not limited to the examples listed herein. Furthermore, the terms "first" and "second," etc. are used to distinguish between different objects and are not used to describe a particular order.
The following detailed description of the implementations of the present invention is made with reference to the accompanying drawings:
fig. 1 is a schematic structural diagram of a vehicle thermal management system according to an embodiment of the present invention. Referring to fig. 1, the vehicle thermal management system includes:
the refrigerant fluid loop is used for flowing refrigerant fluid and comprises a compressor 1, a first heat exchanger 2, a high-pressure liquid drying tank 25, a heat transfer fluid-low-pressure refrigerant heat exchanger 22, an outdoor heat exchanger 3, a first expansion valve 4, an indoor heat exchanger 5 and a first flow path 13 which is selectively communicated or cut off;
a heat transfer fluid circuit in which a heat transfer fluid flows, the heat transfer fluid circuit including a first heat exchanger 2, a first water pump 6, a heat transfer fluid-low pressure refrigerant heat exchanger 22, and an outdoor radiator 7;
an outlet of the compressor 1 is connected with a refrigerant inlet of the first heat exchanger 2, a refrigerant outlet of the first heat exchanger 2 is connected with an inlet of the high-pressure liquid drying tank 25, a liquid outlet of the high-pressure liquid drying tank 25 is connected with an inlet of the outdoor heat exchanger 3, an outlet of the outdoor heat exchanger 3 is connected with an inlet of the first expansion valve 4 through a first connection point 44 and a second connection point 41, an outlet of the first expansion valve 4 is connected with an inlet of the indoor heat exchanger 5, an outlet of the indoor heat exchanger 5 is connected with an inlet of the first flow path 13 through a third connection point 39, and an outlet of the first flow path 13 is connected with an inlet of the compressor 1 through a fourth connection point 42 and a fifth connection point 43;
the outlet of the outdoor heat exchanger 3 is also connected with the refrigerant inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 through a first connection point 44, and the refrigerant outlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 is connected with the inlet of the compressor 1 through a fifth connection point 43;
the heat transfer fluid outlet of the first heat exchanger 2 is connected with the inlet of the outdoor radiator 7, and the outlet of the outdoor radiator 7 is connected with the heat transfer fluid inlet of the first heat exchanger 2 through a sixth connecting point 45; the first water pump 6 is provided on a flow path between the outlet of the heat transfer fluid of the first heat exchanger 2 and the inlet of the outdoor radiator 7, or the first water pump 6 is provided on a flow path between the outlet of the outdoor radiator 7 and the inlet of the heat transfer fluid of the first heat exchanger 2;
the heat transfer fluid outlet of the first heat exchanger 2 is also connected to the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 via a seventh connection point 46, and the heat transfer fluid outlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 is connected to the heat transfer fluid inlet of the first heat exchanger 2 via an eighth connection point 47 and a sixth connection point 45.
The heat transfer fluid may be a coolant, and the refrigerant may be a refrigerant.
The first heat exchanger 2 may perform heat exchange between a heat transfer fluid and a refrigerant inside the first heat exchanger, specifically, may perform heat exchange between the refrigerant flowing out of the outlet of the compressor 1 and the heat transfer fluid flowing out of the outlet of the outdoor heat sink 7, and/or perform heat exchange between the refrigerant flowing out of the outlet of the compressor 1 and the heat transfer fluid flowing out of the heat transfer fluid-low pressure refrigerant heat exchanger 22.
The heat transfer fluid-low pressure refrigerant heat exchanger 22 may exchange heat between the heat transfer fluid and the refrigerant inside thereof, and specifically, may exchange heat between the refrigerant to be introduced into the compressor 1 and the heat transfer fluid flowing out of the first heat exchanger 2. The heat transfer fluid-low pressure refrigerant heat exchanger 22 may be a coaxial tube.
The high-pressure liquid drying tank 25 may be configured to perform gas-liquid separation on the refrigerant flowing out of the refrigerant outlet of the first heat exchanger 2, so that the liquid refrigerant flows out of the liquid outlet.
The seventh connection point 46 has an internal diameter of less than 3mm through a pipe extending from the heat-transfer fluid inlet of the heat-transfer fluid-low pressure refrigerant heat exchanger 22 and the heat-transfer fluid outlet of the heat-transfer fluid-low pressure refrigerant heat exchanger 22 to the eighth connection point 47, and the flow rate of the heat-transfer fluid is less than 2L/min. That is, the inner diameters of the pipe from the seventh connection point 46 to the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22, the pipe for the heat transfer fluid to flow through inside the heat transfer fluid-low pressure refrigerant heat exchanger 22, and the pipe from the heat transfer fluid outlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 to the eighth connection point 47 are all less than 3mm, and the flow rate of the heat transfer fluid is less than 2L/min.
In the embodiment, the heat transfer fluid-low-pressure refrigerant heat exchanger is arranged in front of the compressor, so that the refrigerant flowing into the compressor exchanges heat with the heat transfer fluid flowing out of the first heat exchanger, the refrigerant entering the compressor meets the use requirement, the cost of the vehicle heat management system can be reduced, the superheat degree of the refrigerant at the inlet of the compressor is not required to be controlled to be equal to 0, and the control complexity of the vehicle heat management system can be reduced.
In some embodiments, referring to fig. 2 and 4, the refrigerant fluid circuit further includes a second flow path 8 selectively opened or closed, a third flow path 9 selectively opened or closed, a first throttling flow path 11, a first through flow path 12, a fourth flow path 14 selectively opened or closed, and a first check valve 15;
the liquid outlet of the high-pressure liquid drying tank 25 is connected with the inlet of the second flow path 8, the outlet of the indoor heat exchanger 5 is connected with the inlet of the first check valve 15 through a third connection point 39, and the outlet of the second flow path 8 and the outlet of the first check valve 15 are both selectively connected with the inlet of the outdoor heat exchanger 3 through the first throttling flow path 11 or the first through flow path 12 through a ninth connection point 38;
a liquid outlet of the high-pressure liquid drying tank 25 is connected to an inlet of the first expansion valve 4 via the third flow path 9;
the outlet of the outdoor heat exchanger 3 is also connected to the refrigerant inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 via the first connection point 44 and the fourth flow path 14.
The first throttling flow path 11 is a flow path that can throttle and block the refrigerant and can adjust the flow rate and pressure of the refrigerant during throttling. The first flow passage 12 is a passage through which the refrigerant can be conducted and blocked.
The second flow path 8, the third flow path 9, and the fourth flow path 14 are selectively opened or closed, and for example, a closing valve may be provided in each flow path.
The first check valve 15 is used for controlling the flow path to be communicated only in one direction.
In the embodiment, the circulation of the refrigerants under different modes can be realized through the plurality of flow paths and the first check valve, so that the vehicle thermal management system has multiple working modes and stronger functionality.
In some embodiments, referring to fig. 2-4, the heat transfer fluid circuit further comprises an indoor warm air core 10;
the heat transfer fluid outlet of the first heat exchanger 2 is connected with the inlet of the outdoor radiator 7 through the first water pump 6, the heat transfer fluid outlet of the first heat exchanger 2 is further connected with the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 and the inlet of the indoor warm air core 10 through the first water pump 6 and the seventh connection point 46, the heat transfer fluid outlet of the first heat exchanger 2 is selectively communicated with the inlet of the outdoor radiator 7, the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 and the inlet of the indoor warm air core 10, and the outlet of the indoor warm air core 10 is connected with the heat transfer fluid inlet of the first heat exchanger 2 through the eighth connection point 47 and the sixth connection point 45.
The present embodiment enables the vehicle thermal management system to increase the heat pump heating mode and the dehumidification mode by adding the indoor warm air core 10 and by the connection relationship between the indoor warm air core 10 and other devices.
In some embodiments, referring to fig. 3 and 4, the refrigerant fluid circuit further includes a second heat exchanger 16 and a second expansion valve 17;
the heat transfer fluid circuit further comprises a second heat exchanger 16, a battery pack 18 and a second water pump 19;
the outlet of the outdoor heat exchanger 3 and the outlet of the third flow path 9 are both connected with the refrigerant inlet of the second heat exchanger 16 through a second connection point 41 and a second expansion valve 17, and the refrigerant outlet of the second heat exchanger 16 is connected with the inlet of the compressor 1 through a fourth connection point 42 and a fifth connection point 43;
a first heat transfer fluid outlet of the second heat exchanger 16 is connected with an inlet of the battery pack 18, and an outlet of the battery pack 18 is connected with a first heat transfer fluid inlet of the second heat exchanger 16;
a second water pump 19 is provided on a flow path between the outlet of the first heat transfer fluid of the second heat exchanger 16 and the inlet of the battery pack 18, or the second water pump 19 is provided on a flow path between the outlet of the battery pack 18 and the inlet of the first heat transfer fluid of the second heat exchanger 16.
The vehicle thermal management system can have a battery pack cooling mode and a passenger compartment cooling and battery pack cooling mode on the basis of the operation modes by adding the second heat exchanger 16, the second expansion valve 17, the battery pack 18 and the second water pump 19.
In some embodiments, referring to fig. 3 and 4, the heat transfer fluid circuit further comprises electronics 20 and a third water pump 21;
a second heat transfer fluid outlet of the second heat exchanger 16 is connected to an inlet of the electronics 20, and an outlet of the electronics 20 is connected to a second heat transfer fluid inlet of the second heat exchanger 16;
the third water pump 21 is provided on a flow path between the second heat transfer fluid outlet of the second heat exchanger 16 and the inlet of the electronic device 20, or the third water pump 21 is provided on a flow path between the outlet of the electronic device 20 and the second heat transfer fluid inlet of the second heat exchanger 16;
the electronic device 20 includes at least one of a motor, a charger, a motor controller, and a DC-DC converter.
The second heat exchanger 16 may exchange heat between a heat transfer fluid and a refrigerant inside thereof, specifically, may exchange heat between the refrigerant flowing from the second expansion valve 17 and the heat transfer fluid flowing from the battery pack 18, and may exchange heat between the refrigerant flowing from the second expansion valve 17 and the heat transfer fluid flowing from the electronic device 20.
The present embodiment can make the vehicle thermal management system have a heat recovery mode and a heat pump and heat recovery mode on the basis of the aforementioned operation mode by adding the electronic device 20 and the third water pump 21.
In some embodiments, referring to fig. 2, the refrigerant fluid circuit further comprises an internal heat exchanger 23;
the outlet of the third flow path 9 and the outlet of the outdoor heat exchanger 3 are both connected to the first refrigerant inlet of the interior heat exchanger 23 through a tenth connection point 40, the first refrigerant outlet of the interior heat exchanger 23 is connected to the inlet of the indoor heat exchanger 5 through a second connection point 41 and the first expansion valve 4, the outlet of the first flow path 13 is connected to the second refrigerant inlet of the interior heat exchanger 23 through a fourth connection point 42, and the second refrigerant outlet of the interior heat exchanger 23 is connected to the inlet of the compressor 1 through a fifth connection point 43; or,
an outlet of the exterior heat exchanger 3 is connected to a first refrigerant inlet of the interior heat exchanger 23 through a first connection point 44, an inlet of the first expansion valve 4 is connected to a first refrigerant outlet of the interior heat exchanger 23 and an outlet of the third flow path 9 through an eleventh connection point 49, an outlet of the first flow path 13 is connected to a second refrigerant inlet of the interior heat exchanger 23 through a fourth connection point 42, and a second refrigerant outlet of the interior heat exchanger 23 is connected to an inlet of the compressor 1 through a fifth connection point 43.
The internal heat exchanger 23 may exchange heat between the refrigerants passing through the two channels therein.
In some embodiments, the refrigerant fluid circuit further comprises an internal heat exchanger 23;
referring to fig. 3, the outlet of the third flow path 9 and the outlet of the outdoor heat exchanger 3 are both connected to the first refrigerant inlet of the interior heat exchanger 23 through a tenth connection point 40, the first refrigerant outlet of the interior heat exchanger 23 is connected to the inlet of the indoor heat exchanger 5 through a second connection point 41 and a first expansion valve 4, the first refrigerant outlet of the interior heat exchanger 23 is also connected to the refrigerant inlet of the second heat exchanger 16 through a second connection point 41 and a second expansion valve 17, the outlet of the first flow path 13 and the refrigerant outlet of the second heat exchanger 16 are both connected to the second refrigerant inlet of the interior heat exchanger 23 through a fourth connection point 42, and the second refrigerant outlet of the interior heat exchanger 23 is connected to the inlet of the compressor 1 through a fifth connection point 43; or,
referring to fig. 4, the outlet of the exterior heat exchanger 3 is connected to the first refrigerant inlet of the interior heat exchanger 23 through a first connection point 44, the inlets of the first expansion valve 4 and the second expansion valve 17 are both connected to the first refrigerant outlet of the interior heat exchanger 23 and the outlet of the third flow path 9, the outlets of the first flow path 13 and the second heat exchanger 16 are both connected to the second refrigerant inlet of the interior heat exchanger 23 through a fourth connection point 42, and the second refrigerant outlet of the interior heat exchanger 23 is connected to the inlet of the compressor 1 through a fifth connection point 43.
Referring to fig. 4, an inlet of the first expansion valve 4 is connected to the first refrigerant outlet of the interior heat exchanger 23 through an eleventh connection point 49 and a second connection point 41. An inlet of the first expansion valve 4 is connected to the third flow path 9 via an eleventh connection point 49. An inlet of the second expansion valve 17 is connected to a first refrigerant outlet of the internal heat exchanger 23 and an outlet of the third flow path 9 through a second connection point 41.
In some embodiments, referring to fig. 2 to 4, the refrigerant fluid circuit further includes a second check valve 24;
an outlet of the outdoor heat exchanger 3 is connected with a first refrigerant inlet of the internal heat exchanger 23 through a first connection point 44 and a second check valve 24; or,
the second check valve 24 is provided at the first refrigerant outlet of the inner heat exchanger 23.
The second check valve 24 is used to control the one-way communication of the flow path, i.e. the refrigerant can only enter the first expansion valve 4 and/or the second expansion valve 17 from the exterior heat exchanger 3 through the interior heat exchanger 23, but can not flow in reverse.
In some embodiments, referring to fig. 3, the second flow path 8 is provided with a first stop valve 26, the third flow path 9 is provided with a second stop valve 27, and the liquid outlet of the high-pressure liquid drying tank 25 is connected with the inlet of the second flow path 8 and the inlet of the third flow path 9 through a twelfth connecting point 37; or,
referring to fig. 4, the refrigerant fluid circuit further includes a first three-way valve 28, the first three-way valve 28 is located on the second flow path 8 and the third flow path 9, a port a of the first three-way valve 28 is connected to a liquid outlet of the high-pressure liquid drying tank 25, a port B of the first three-way valve 28 is connected to an inlet of the outdoor heat exchanger 3, and a port C of the first three-way valve 28 is connected to an inlet of the first expansion valve 4.
The first shut-off valve 26 may be used to control the opening or closing of the second flow path 8, and the second shut-off valve 27 may be used to control the opening or closing of the third flow path 9. Alternatively, the second flow path 8 and the third flow path 9 may be controlled to be opened or closed simultaneously by the first three-way valve 28.
In some embodiments, referring to fig. 2-4, a third stop valve 29 is disposed on the first flow path 13 and a fourth stop valve 30 is disposed on the fourth flow path 14.
The third cut-off valve 29 may be used to control the opening or closing of the first flow path 13. The fourth shutoff valve 30 may be used to control the opening or closing of the fourth flow path 14.
In some embodiments, referring to fig. 2 and 4, a third expansion valve 31 is disposed on the first throttle flow path 11, a fifth stop valve 32 is disposed on the first through flow path 12, an outlet of the second flow path 8 and an outlet of the first check valve 15 are connected to an inlet of the third expansion valve 31 and an inlet of the fifth stop valve 32 through a ninth connection point 38 and a thirteenth connection point 50, respectively, and an outlet of the third expansion valve 31 and an outlet of the fifth stop valve 32 are connected to an inlet of the outdoor heat exchanger 3 through a fourteenth connection point 51; or,
referring to fig. 3, the refrigerant fluid circuit further includes an expansion switch valve 33, an outlet of the second flow path 8 and an outlet of the first check valve 15 are both connected to an inlet of the expansion switch valve 33, an outlet of the expansion switch valve 33 is connected to an inlet of the outdoor heat exchanger 3, the first throttling flow path 11 is a throttling flow path of the expansion switch valve 33, and the first through flow path 12 is a through flow path of the expansion switch valve 33.
In order to throttle and depressurize the refrigerant through the first throttling flow path 11, the first through flow path 12 directly conducts (i.e., does not throttle) the refrigerant, and in one embodiment, as shown in fig. 2, a third expansion valve 31 may be disposed on the first throttling flow path 11, a fifth stop valve 32 may be disposed on the first through flow path 12, and the third expansion valve 31 and the fifth stop valve 32 may be connected in parallel with each other.
In another embodiment, the refrigerant fluid circuit further includes an expansion switch valve 33. The expansion switch valve 33 is equivalent to the integration of an expansion valve and a switch valve, a throttling flow channel and a through flow channel are arranged in the expansion switch valve 33, a throttling valve port and a throttling valve core are arranged in the throttling flow channel, a through flow valve port and a through flow valve core are arranged in the through flow channel, and the throttling valve core can be selectively controlled to be opened or the through flow valve core can be selectively opened according to the working mode of the vehicle thermal management system, so that the refrigerant has a throttling state of being throttled and depressurized and a through flow state of not throttling and being directly conducted when passing through the expansion switch valve 33.
In some embodiments, referring to fig. 2 and 4, the heat transfer fluid circuit further includes a second three-way valve 34, a port a of the second three-way valve 34 is connected to the outlet of the first water pump 6, a port B of the second three-way valve 34 is connected to the inlet of the outdoor radiator 7, and a port C of the second three-way valve 34 is connected to the inlet of the indoor warm air core 10 and the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 through seventh connection points 46, respectively; or,
referring to fig. 3, the heat transfer fluid circuit further includes a first two-way valve 35 and a second two-way valve 36, an outlet of the first water pump 6 is connected to an inlet of the outdoor heat sink 7 via a fifteenth connection point 48 and the first two-way valve 35, and an outlet of the first water pump 6 is further connected to an inlet of the indoor warm air core 10 and a heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger 22 via the fifteenth connection point 48, the second two-way valve 36 and the seventh connection point 46, respectively.
In this embodiment, the first heat exchanger 2 can be respectively connected to or disconnected from the outdoor heat sink 7, the indoor warm air core 10 and the heat transfer fluid-low pressure refrigerant heat exchanger 22 by a three-way valve or two-way valves.
By controlling the vehicle thermal management system, various modes of the vehicle thermal management system can be realized, and various requirements of personnel are met.
In the following, we adopt the vehicle thermal management system to implement different modes, which may specifically include: a cooling mode, a heat pump heating mode, a dehumidification mode, a battery pack cooling mode, a passenger compartment cooling and battery pack cooling mode, a heat recovery mode, and a heat pump and heat recovery mode.
In some embodiments, when the vehicle thermal management system is in a cooling mode, a refrigerant flows through the first refrigerant fluid circuit or the second refrigerant fluid circuit, and a heat transfer fluid flows through the first heat transfer fluid circuit;
referring to fig. 1, in the first refrigerant fluid circuit, the refrigerant sequentially passes through a compressor 1, a first heat exchanger 2 and a high-pressure liquid drying tank 25 and enters an outdoor heat exchanger 3, the refrigerant releases heat to the outside air in the outdoor heat exchanger 3, then enters a first expansion valve 4 through a first connection point 44 and a second connection point 41, and enters an indoor heat exchanger 5 after being subjected to pressure reduction through the first expansion valve 4, and the refrigerant returns to the compressor 1 through a third connection point 39, a first flow path 13, a fourth connection point 42 and a fifth connection point 43 after absorbing the heat of a passenger compartment in the indoor heat exchanger 5;
in the second refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2 and the high-pressure liquid drying tank 25 to enter the first expansion valve 4, the refrigerant enters the indoor heat exchanger 5 after being subjected to pressure reduction by the first expansion valve 4, and after absorbing heat of a passenger compartment in the indoor heat exchanger 5, the refrigerant returns to the compressor 1 through the third connecting point 39, the first flow path 13, the fourth connecting point 42 and the fifth connecting point 43;
in the first heat transfer fluid circuit, the heat transfer fluid flowing out of the first heat exchanger 2 enters the outdoor radiator 7 through the first water pump 6, and the heat transfer fluid returns to the first heat exchanger 2 through the sixth connection point 45 after dissipating heat to the outside air in the outdoor radiator 7;
when the vehicle thermal management system is in the cooling mode, the refrigerant releases heat to the heat transfer fluid and the heat transfer fluid absorbs heat in the first heat exchanger 2.
In this embodiment, the working mode that the refrigerant of the vehicle thermal management system flows through the first refrigerant fluid circuit and the heat transfer fluid flows through the first heat transfer fluid circuit is referred to as a first cooling mode, and the working mode that the refrigerant of the vehicle thermal management system flows through the second refrigerant fluid circuit and the heat transfer fluid flows through the first heat transfer fluid circuit is referred to as a second cooling mode.
In some possible implementations, in the first cooling mode, referring to fig. 3, the first stop valve 26 is opened, the second stop valve 27 is closed, the expansion switch valve 33 is in a flow state (i.e., the flow passage inside the expansion switch valve 33 is open and the throttle passage is closed), the third stop valve 29 is opened, the fourth stop valve 30 is closed, the first expansion valve 4 is opened, the second expansion valve 17 is closed, the first water pump 6 is opened, the first two-way valve 35 is opened, the second two-way valve 36 is closed, the second water pump 19 is closed, and the third water pump 21 is closed.
Referring to fig. 3, a refrigerant entering the compressor 1 is compressed by the compressor 1, so that a high-temperature and high-pressure gaseous refrigerant is discharged from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to a low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the outdoor radiator 7 under the pumping of the first water pump 6 and radiates heat to the outside atmosphere in the outdoor radiator 7, and the low-temperature heat transfer fluid flowing out of the outlet of the outdoor radiator 7 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature and high-pressure gaseous refrigerant. The refrigerant discharged from the refrigerant outlet of the first heat exchanger 2 releases heat to the heat transfer fluid, the refrigerant is subjected to gas-liquid separation in the high-pressure liquid drying tank 25, the liquid refrigerant is discharged from the outlet of the high-pressure liquid drying tank 25, the liquid refrigerant discharges heat to the outside atmosphere in the outdoor heat exchanger 3, the liquid refrigerant discharged from the outlet of the outdoor heat exchanger 3 enters the internal heat exchanger 23 and releases heat in the internal heat exchanger, the liquid refrigerant discharged from the first refrigerant outlet of the internal heat exchanger is throttled and depressurized by the first expansion valve 4, the low-temperature low-pressure gas-liquid two-phase refrigerant flows out of the outlet of the first expansion valve 4, the low-temperature low-pressure gas-liquid two-phase refrigerant absorbs heat of the passenger compartment in the indoor heat exchanger 5 to reduce the temperature of the passenger compartment, the refrigerant discharged from the outlet of the indoor heat exchanger 5 enters the internal heat exchanger 23, and the heat exchanger 23 obtains the heat lost by the liquid refrigerant discharged from the outlet of the outdoor heat exchanger 3 in the internal heat exchanger 23, the second refrigerant outlet of the interior heat exchanger 23 discharges the gaseous refrigerant, which is returned to the compressor 1. In the first cooling mode, the refrigerant passes through the first heat exchanger 2, releases heat by the outdoor radiator 7, and releases heat again by the outdoor heat exchanger 3. This first refrigeration mode can have better refrigeration effect and refrigeration efficiency under high temperature environment.
In some possible implementations, in the second cooling mode, referring to fig. 3, the first stop valve 26 is closed, the second stop valve 27 is opened, the expansion switch valve 33 is closed, the third stop valve 29 is opened, the fourth stop valve 30 is closed, the first expansion valve 4 is opened, the second expansion valve 17 is closed, the first water pump 6 is opened, the first two-way valve 35 is opened, the second two-way valve 36 is closed, the second water pump 19 is closed, and the third water pump 21 is closed.
As shown in fig. 3, the refrigerant entering the compressor 1 is compressed by the compressor 1, so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature coolant in the first heat exchanger 2, a high-temperature heat transfer fluid flows out of the heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the outdoor heat sink 7 by pumping of the first water pump 6 and dissipates heat to the outside atmosphere in the outdoor heat sink 7, and a low-temperature heat transfer fluid flowing out of the outlet of the outdoor heat sink 7 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature and high-pressure gaseous refrigerant. The refrigerant which radiates heat to the heat transfer fluid flows out of the refrigerant outlet of the first heat exchanger 2, the refrigerant is subjected to gas-liquid separation through the high-pressure liquid drying tank 25, the liquid refrigerant flows out of the outlet of the high-pressure liquid drying tank 25, passes through the third flow path 9, flows into the internal heat exchanger 23 and radiates heat in the internal heat exchanger 23, the liquid refrigerant flowing out of the first refrigerant outlet of the internal heat exchanger 23 is throttled and depressurized by the first expansion valve 4, the low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of the outlet of the first expansion valve 4, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the passenger compartment in the indoor heat exchanger 5 to reduce the temperature of the passenger compartment, the refrigerant flowing out of the outlet of the indoor heat exchanger 5 enters the internal heat exchanger 23, and the heat lost by the liquid refrigerant flowing out of the outlet of the high-pressure liquid drying tank 25 in the internal heat exchanger 23 is obtained, the second refrigerant outlet of the interior heat exchanger 23 discharges the gaseous refrigerant, which is returned to the compressor 1. In the second cooling mode, the refrigerant passes through the first heat exchanger 2 and releases heat by the exterior heat sink 7, and the refrigerant does not flow through the exterior heat exchanger 3. The ambient temperature during the second cooling mode application may be lower than the ambient temperature during the first cooling mode application.
In some embodiments, when the vehicle thermal management system is in the heat pump heating mode, the refrigerant flows through the third refrigerant fluid circuit or the fourth refrigerant fluid circuit, and the heat transfer fluid flows through the second heat transfer fluid circuit;
in the third refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25 and the third flow path 9 to enter the first expansion valve 4, the refrigerant enters the indoor heat exchanger 5 after being subjected to pressure reduction by the first expansion valve 4, the refrigerant releases heat to a passenger compartment in the indoor heat exchanger 5 and then enters the outdoor heat exchanger 3 through the third connection point 39, the first one-way valve 15, the ninth connection point 38 and the first throttling flow path 11, the refrigerant absorbs heat of outside air in the outdoor heat exchanger 3 and then enters the heat transfer fluid-low pressure refrigerant heat exchanger 22 through the first connection point 44 and the fourth flow path 14, and the refrigerant returns to the compressor 1 through the fifth connection point 43 after absorbing heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22;
in the fourth refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25, the second flow path 8, the ninth connection point 38 and the first throttling flow path 11 to enter the outdoor heat exchanger 3, the refrigerant enters the heat transfer fluid-low pressure refrigerant heat exchanger 22 through the first connection point 44 and the fourth flow path 14 after absorbing heat of outside air in the outdoor heat exchanger 3, and the refrigerant returns to the compressor 1 through the fifth connection point 43 after absorbing heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22;
in the second heat transfer fluid circuit, the heat transfer fluid flowing out of the first heat exchanger 2 is divided into two paths after passing through the first water pump 6 and the seventh connection point 46: one path of heat transfer fluid enters the indoor warm air core 10, and returns to the first heat exchanger 2 through the eighth connection point 47 and the sixth connection point 45 after radiating heat to the passenger compartment in the indoor warm air core 10; the other path of heat transfer fluid enters the heat transfer fluid-low pressure refrigerant heat exchanger 22, releases heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22, and returns to the first heat exchanger 2 through an eighth connection point 47 and a sixth connection point 45;
when the vehicle thermal management system is in a heat pump heating mode, in the first heat exchanger 2, the refrigerant releases heat to the heat transfer fluid, and the heat transfer fluid absorbs heat; in the heat transfer fluid-low pressure refrigerant heat exchanger 22, the refrigerant flowing out of the outdoor heat exchanger 3 and into the heat transfer fluid-low pressure refrigerant heat exchanger 22 absorbs heat, and the heat transfer fluid flowing out of the first heat exchanger 2 and into the heat transfer fluid-low pressure refrigerant heat exchanger 22 releases heat.
In this embodiment, the working mode in which the refrigerant of the vehicle thermal management system flows through the third refrigerant fluid circuit and the heat transfer fluid flows through the second heat transfer fluid circuit is referred to as a first heat pump heating mode, and the working mode in which the refrigerant of the vehicle thermal management system flows through the fourth refrigerant fluid circuit and the heat transfer fluid flows through the second heat transfer fluid circuit is referred to as a second heat pump heating mode.
In some possible implementations, in the first heat pump heating mode, referring to fig. 3, the first stop valve 26 is closed, the second stop valve 27 is opened, the expansion switch valve 33 is in a throttling state (i.e., the throttling flow passage inside the expansion switch valve 33 is on, the through flow passage is off), the third stop valve 29 is closed, the fourth stop valve 30 is opened, the first expansion valve 4 is opened, the second expansion valve 17 is closed, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is closed.
As shown in fig. 3, a refrigerant entering the compressor 1 is compressed by the compressor 1, so that a high-temperature and high-pressure gaseous refrigerant is discharged from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to a low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out from a heat transfer fluid outlet of the first heat exchanger 2, a part of the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6, and radiates heat to a passenger compartment in the indoor warm air core 10, so as to increase the temperature of the passenger compartment, and the low-temperature heat transfer fluid flowing out from an outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2, and continuously absorbs heat of the high-temperature and high-pressure gaseous refrigerant; the other part of the high-temperature heat transfer fluid flows into the heat transfer fluid-low pressure refrigerant heat exchanger 22 to release heat, and the low-temperature heat transfer fluid flowing out of the heat transfer fluid-low pressure refrigerant heat exchanger 22 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant discharged from the refrigerant outlet of the first heat exchanger 2, which has released heat from the heat transfer fluid, passes through the high pressure liquid drying tank 25 to be separated into gas and liquid, and the liquid refrigerant discharged from the outlet of the high pressure liquid drying tank 25, flows into the internal heat exchanger 23, and the liquid refrigerant in the internal heat exchanger 23 neither releases or absorbs heat (see fig. 4, the liquid refrigerant discharged from the high pressure liquid drying tank 25 may directly flow into the first expansion valve 4 through the third flow path 9), that is, at this time, the internal heat exchanger 23 serves as a through flow path, the liquid refrigerant discharged from the first refrigerant outlet of the internal heat exchanger 23 is depressurized in the first expansion valve 4, the gas-liquid two-phase refrigerant is discharged from the outlet of the first expansion valve 4, the gas-liquid two-phase refrigerant discharges heat to the passenger compartment in the indoor heat exchanger 5 to preheat the wind to be passed through the indoor warm air core 10, and the vapor enthalpy pressure of the gas refrigerant discharged from the outlet of the indoor heat exchanger 5 is reduced in the expansion switch valve 33, the outlet of the expansion switch valve 33 discharges the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant, the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs the heat of the outside air in the outdoor heat exchanger 3, the gas-liquid two-phase mixed refrigerant discharged from the outlet of the outdoor heat exchanger 3 absorbs the heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22, the heat transfer fluid-low pressure refrigerant heat exchanger 22 discharges the gaseous refrigerant, and the gaseous refrigerant returns to the compressor 1.
In the first heat pump heating mode, the indoor heat exchanger 5 and the indoor warm air core 10 both release heat to the passenger compartment, and the indoor heat exchanger 5 can preheat the air that is about to flow through the indoor warm air core 10, so that quick heating of the passenger compartment can be realized.
In some possible implementations, in the second heat pump heating mode, referring to fig. 3, the first stop valve 26 is opened, the second stop valve 27 is closed, the expansion switch valve 33 is in a throttling state (i.e., the throttling flow passage inside the expansion switch valve 33 is on, the through flow passage is off), the third stop valve 29 is closed, the fourth stop valve 30 is opened, the first expansion valve 4 is closed, the second expansion valve 17 is closed, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is closed.
As shown in fig. 3, a refrigerant entering the compressor 1 is compressed by the compressor 1, so that a high-temperature and high-pressure gaseous refrigerant is discharged from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to a low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, a part of the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6, and dissipates heat to the passenger compartment in the indoor warm air core 10, so as to increase the temperature of the passenger compartment, and the low-temperature heat transfer fluid flowing out of the indoor warm air core 10 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2, and continues to absorb heat of the high-temperature and high-pressure gaseous refrigerant; the other part of the high-temperature heat transfer fluid flows into the heat transfer fluid-low pressure refrigerant heat exchanger 22 to release heat, and the low-temperature heat transfer fluid flowing out of the heat transfer fluid-low pressure refrigerant heat exchanger 22 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant discharged from the refrigerant outlet of the first heat exchanger 2 releases heat to the heat transfer fluid, the refrigerant is subjected to gas-liquid separation in the high-pressure liquid drying tank 25, the liquid refrigerant is discharged from the outlet of the high-pressure liquid drying tank 25, the enthalpy pressure of the liquid refrigerant in the expansion switch valve 33 is reduced, a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant is discharged from the outlet of the expansion switch valve 33, the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant absorbs heat of the outside atmosphere in the outdoor heat exchanger 3, the gas-liquid two-phase mixed refrigerant discharged from the outlet of the outdoor heat exchanger 3 absorbs heat in the heat transfer fluid-low-pressure refrigerant heat exchanger 22, a gaseous refrigerant is discharged from the heat transfer fluid-low-pressure refrigerant heat exchanger 22, and the gaseous refrigerant returns to the compressor 1.
In the second heat pump heating mode, the indoor warm air core 10 releases heat to the passenger compartment, and the refrigerant does not flow through the indoor heat exchanger 5. The ambient temperature when the second heat pump heating mode is applied may be higher than the ambient temperature when the first heat pump heating mode is applied.
In some embodiments, when the vehicle thermal management system is in a dehumidification mode, the refrigerant flows through the fifth refrigerant fluid circuit or the sixth refrigerant fluid circuit, and the heat transfer fluid flows through the third heat transfer fluid circuit; or when the vehicle thermal management system is in a dehumidification mode, the refrigerant flows through the seventh refrigerant fluid loop or the eighth refrigerant fluid loop, and the heat transfer fluid flows through the second heat transfer fluid loop;
in a fifth refrigerant fluid loop, a refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25 and the third flow path 9 to enter the first expansion valve 4, the refrigerant enters the indoor heat exchanger 5 after being subjected to pressure reduction by the first expansion valve 4, and the refrigerant returns to the compressor 1 through the third connection point 39, the first flow path 13, the fourth connection point 42 and the fifth connection point 43 after absorbing heat of a passenger compartment in the indoor heat exchanger 5;
in the sixth refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25, the second flow path 8, the ninth connection point 38 and the first throttle flow path 11 to enter the outdoor heat exchanger 3, the refrigerant enters the first expansion valve 4 through the first connection point 44 and the second connection point 41 after absorbing the heat of the outside air in the outdoor heat exchanger 3, the refrigerant enters the indoor heat exchanger 5 after being subjected to pressure reduction through the first expansion valve 4, and the refrigerant returns to the compressor 1 through the third connection point 39, the first flow path 13, the fourth connection point 42 and the fifth connection point 43 after absorbing the heat of the passenger compartment in the indoor heat exchanger 5;
in the third heat transfer fluid circuit, the heat transfer fluid flowing out of the first heat exchanger 2 enters the indoor warm air core 10 through the first water pump 6 and the seventh connection point 46, and after the heat transfer fluid is radiated to the passenger compartment in the indoor warm air core 10, the heat transfer fluid returns to the first heat exchanger 2 through the eighth connection point 47 and the sixth connection point 45;
in the seventh refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1 and the first heat exchanger 2 to enter the high-pressure liquid drying tank 25, and the refrigerant flowing out of the high-pressure liquid drying tank 25 is divided into two paths: one path of refrigerant enters the first expansion valve 4 through the third flow path 9, the refrigerant enters the indoor heat exchanger 5 after being subjected to pressure reduction through the first expansion valve 4, and the refrigerant returns to the compressor 1 through the third connection point 39, the first flow path 13, the fourth connection point 42 and the fifth connection point 43 after absorbing heat of a passenger compartment in the indoor heat exchanger 5; the other path of refrigerant enters the outdoor heat exchanger 3 through the second flow path 8, the ninth connection point 38 and the first throttling flow path 11, the refrigerant enters the heat transfer fluid-low pressure refrigerant heat exchanger 22 through the first connection point 44 and the fourth flow path 14 after absorbing heat of outside air in the outdoor heat exchanger 3, and the refrigerant returns to the compressor 1 through the fifth connection point 43 after absorbing heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22;
in the eighth refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25 and the third flow path 9 and enters the first expansion valve 4, the refrigerant enters the indoor heat exchanger 5 after being subjected to pressure reduction by the first expansion valve 4, the refrigerant enters the outdoor heat exchanger 3 after absorbing heat of a passenger compartment in the indoor heat exchanger 5 and passes through the third connection point 39, the first one-way valve 15, the ninth connection point 38 and the first throttling flow path 11, the refrigerant enters the heat transfer fluid-low pressure refrigerant heat exchanger 22 after absorbing heat of outside air in the outdoor heat exchanger 3 and passes through the first connection point 44 and the fourth flow path 14, and the refrigerant returns to the compressor 1 after absorbing heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22 and passes through the fifth connection point 43;
when the vehicle thermal management system is in a dehumidification mode, in the first heat exchanger 2, the refrigerant releases heat to the heat transfer fluid, and the heat transfer fluid absorbs heat; in the heat transfer fluid-low pressure refrigerant heat exchanger 22, the refrigerant flowing out of the exterior heat exchanger 3 and entering the heat transfer fluid-low pressure refrigerant heat exchanger 22 absorbs heat, and the heat transfer fluid flowing out of the first heat exchanger 2 and entering the heat transfer fluid-low pressure refrigerant heat exchanger 22 releases heat.
In this embodiment, a working mode in which the refrigerant of the vehicle thermal management system flows through the fifth refrigerant fluid circuit, the heat transfer fluid flows through the third heat transfer fluid circuit is referred to as a first dehumidification mode, a working mode in which the refrigerant of the vehicle thermal management system flows through the sixth refrigerant fluid circuit, a working mode in which the heat transfer fluid flows through the third heat transfer fluid circuit is referred to as a second dehumidification mode, a working mode in which the refrigerant of the vehicle thermal management system flows through the seventh refrigerant fluid circuit, a working mode in which the heat transfer fluid flows through the second heat transfer fluid circuit is referred to as a third dehumidification mode, a working mode in which the refrigerant of the vehicle thermal management system flows through the eighth refrigerant fluid circuit, and a working mode in which the heat transfer fluid flows through the second heat transfer fluid circuit is referred to as a fourth dehumidification mode.
In some possible implementations, in the first dehumidification mode, referring to fig. 3, the first stop valve 26 is closed, the second stop valve 27 is opened, the expansion switch valve 33 is closed, the third stop valve 29 is opened, the fourth stop valve 30 is closed, the first expansion valve 4 is opened, the second expansion valve 17 is closed, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is closed.
As shown in fig. 3, in the first dehumidification mode, the refrigerant entering the compressor 1 is compressed by the compressor 1, so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of the heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the indoor warm air core 10 by the pumping of the first water pump 6 and dissipates heat to the passenger compartment in the indoor warm air core 10 to maintain the temperature in the passenger compartment, and the low-temperature heat transfer fluid flowing out of the outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature and high-pressure gaseous refrigerant. The refrigerant which radiates heat to the heat transfer fluid flows out of the refrigerant outlet of the first heat exchanger 2, the refrigerant is subjected to gas-liquid separation through the high-pressure liquid drying tank 25, the liquid refrigerant flows out of the outlet of the high-pressure liquid drying tank 25, the liquid refrigerant flows into the internal heat exchanger 23 and radiates heat in the internal heat exchanger 23, the liquid refrigerant flowing out of the first refrigerant outlet of the internal heat exchanger 23 is throttled and depressurized by the first expansion valve 4, the low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of the outlet of the first expansion valve 4, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the passenger compartment in the indoor heat exchanger 5, so that humid air in the passenger compartment can be condensed into water drops on the surface of the indoor heat exchanger 5, the humidity of the air in the passenger compartment is reduced, the refrigerant flowing out of the outlet of the indoor heat exchanger 5 enters the internal heat exchanger 23, and the heat lost by the internal heat exchanger 23 of the liquid refrigerant flowing out of the outlet of the high-pressure liquid drying tank 25 is obtained in the internal heat exchanger 23 The second refrigerant outlet of the interior heat exchanger 23 discharges the gaseous refrigerant, which is returned to the compressor 1. The first dehumidification mode may be applied to dehumidify the passenger compartment at an ambient temperature of 10-15 ℃.
Alternatively, a stop valve may be disposed in the flow path from the seventh connection point 46 to the heat transfer fluid-low pressure refrigerant heat exchanger 22, and the stop valve may be controlled to be turned off when the heat transfer fluid flowing out of the first heat exchanger 2 only needs to flow into the indoor warm air core 10 after passing through the second two-way valve 36, and may be controlled to be turned on when the heat transfer fluid flowing out of the first heat exchanger 2 needs to flow into both the indoor warm air core 10 and the heat transfer fluid-low pressure refrigerant heat exchanger 22 after passing through the second two-way valve 36. For example, the shutoff valve may be controlled to be closed in the first dehumidification mode, the second dehumidification mode, and the heat recovery mode.
In some possible implementations, in the second dehumidification mode, referring to fig. 3, the first stop valve 26 is opened, the second stop valve 27 is closed, the expansion switch valve 33 is in a throttling state (i.e., the throttling flow passage inside the expansion switch valve 33 is on, the through flow passage is off), the third stop valve 29 is opened, the fourth stop valve 30 is closed, the first expansion valve 4 is opened, the second expansion valve 17 is closed, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is closed.
As shown in fig. 3, in the second dehumidification mode, the refrigerant entering the compressor 1 is compressed by the compressor 1, so that the outlet of the compressor 1 discharges a high-temperature and high-pressure gaseous refrigerant, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of the heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6 and dissipates heat to the passenger compartment in the indoor warm air core 10 to maintain the temperature of the passenger compartment, and the low-temperature heat transfer fluid flowing out of the outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature and high-pressure gaseous refrigerant. The refrigerant discharged from the refrigerant outlet of the first heat exchanger 2 releases heat to the heat transfer fluid, the refrigerant undergoes gas-liquid separation in the high pressure liquid drying tank 25, the liquid refrigerant is discharged from the outlet of the high pressure liquid drying tank 25, the liquid refrigerant is reduced in isenthalpic pressure in the expansion switch valve 33, the gas-liquid two-phase mixed refrigerant is discharged from the outlet of the expansion switch valve 33, the gas-liquid two-phase mixed refrigerant absorbs the heat of the outside atmosphere in the outdoor heat exchanger 3, the liquid refrigerant discharged from the outlet of the outdoor heat exchanger 3 enters the internal heat exchanger 23 and releases heat in the internal heat exchanger 23, the liquid refrigerant discharged from the first refrigerant outlet of the internal heat exchanger 23 is throttled and reduced in pressure by the first expansion valve 4, the gas-liquid two-phase refrigerant discharged from the outlet of the first expansion valve 4 absorbs the heat of the passenger compartment in the indoor heat exchanger 5, so that the humid air in the passenger compartment is condensed into water drops on the surface of the indoor heat exchanger 5, the air humidity in the passenger compartment is reduced, the refrigerant flowing out of the outlet of the indoor heat exchanger 5 enters the internal heat exchanger 23, the heat lost in the internal heat exchanger 23 by the liquid refrigerant flowing out of the outlet of the outdoor heat exchanger 3 is obtained in the internal heat exchanger 23, and the gaseous refrigerant flows out of the second refrigerant outlet of the internal heat exchanger 23 and finally returns to the compressor 1.
The second dehumidification mode described above may be applied to dehumidify the passenger compartment when the ambient temperature is less than 5 ℃.
In some possible implementations, in the third dehumidification mode, referring to fig. 3, the first stop valve 26 is opened, the second stop valve 27 is opened, the expansion switch valve 33 is in a throttling state (i.e., the throttling flow passage inside the expansion switch valve 33 is on, the through flow passage is off), the third stop valve 29 is opened, the fourth stop valve 30 is opened, the first expansion valve 4 is opened, the second expansion valve 17 is closed, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is closed.
In a third dehumidification mode, as shown in fig. 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, a part of the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6 and radiates heat to the passenger compartment in the indoor warm air core 10 to maintain the temperature in the passenger compartment, and the low-temperature heat transfer fluid flowing out of the outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature and high-pressure gaseous refrigerant; the other part of the high-temperature heat transfer fluid flows into the heat transfer fluid-low pressure refrigerant heat exchanger 22 to release heat, and the low-temperature heat transfer fluid flowing out of the heat transfer fluid-low pressure refrigerant heat exchanger 22 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant discharged from the refrigerant outlet of the first heat exchanger 2 releases heat to the heat transfer fluid, the refrigerant is subjected to gas-liquid separation in the high-pressure liquid drying tank 25, the liquid refrigerant is discharged from the outlet of the high-pressure liquid drying tank 25, the liquid refrigerant is divided into two streams, one stream flows into the internal heat exchanger 23 through the third flow path 9 and releases heat in the internal heat exchanger 23, the liquid refrigerant discharged from the first refrigerant outlet of the internal heat exchanger 23 is throttled and depressurized by the first expansion valve 4, the low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of the outlet of the first expansion valve 4, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the passenger compartment in the indoor heat exchanger 5, so that the humid air in the passenger compartment can be condensed into water beads on the surface of the indoor heat exchanger 5, thereby reducing the humidity of the air in the passenger compartment, the other stream of liquid enthalpy refrigerant passes through the second flow path 8 and is subjected to the expansion switch valve 33 under the equal pressure, the gas-liquid two-phase mixed refrigerant flows out of the outlet of the expansion switch valve 33, and absorbs heat of the outside atmosphere in the outdoor heat exchanger 3. The refrigerant flowing out of the outlet of the indoor heat exchanger 5 enters the internal heat exchanger 23, and obtains the heat lost by the internal heat exchanger 23 from the liquid refrigerant flowing out of the outlet of the high pressure liquid drying tank 25 in the internal heat exchanger 23, the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 3 absorbs the heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22, and the gas refrigerant flows out of the heat transfer fluid-low pressure refrigerant heat exchanger 22, and the gas refrigerant is merged with the gas refrigerant flowing out of the second refrigerant outlet of the internal heat exchanger 23 at the fifth connection point 43 and then returns to the compressor 1.
The third dehumidification mode can be applied to dehumidifying the passenger compartment at an ambient temperature of 5-10 ℃.
In some possible implementations, in the fourth dehumidification mode, referring to fig. 3, the first stop valve 26 is closed, the second stop valve 27 is opened, the expansion switch valve 33 is in the throttling state (i.e., the throttling flow passage inside the expansion switch valve 33 is on, the through flow passage is off), the third stop valve 29 is closed, the fourth stop valve 30 is opened, the first expansion valve 4 is opened, the second expansion valve 17 is closed, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is closed.
In a fourth dehumidification mode, as shown in fig. 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, a part of the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6 and dissipates heat to the passenger compartment in the indoor warm air core 10 to maintain the temperature of the passenger compartment, and the low-temperature heat transfer fluid flowing out of the outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature and high-pressure gaseous refrigerant; the other part of the high-temperature heat transfer fluid flows into the heat transfer fluid-low pressure refrigerant heat exchanger 22 to release heat, and the low-temperature heat transfer fluid flowing out of the heat transfer fluid-low pressure refrigerant heat exchanger 22 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant discharged from the refrigerant outlet of the first heat exchanger 2 releases heat to the heat transfer fluid, the refrigerant undergoes gas-liquid separation in the high pressure liquid drying tank 25, the liquid refrigerant flows out from the outlet of the high pressure liquid drying tank 25, the liquid refrigerant flows into the internal heat exchanger 23 through the third flow path 9, the liquid refrigerant neither releases heat nor absorbs heat in the internal heat exchanger 23 (see fig. 4, the liquid refrigerant discharged from the high pressure liquid drying tank 25 can directly flow into the first expansion valve 4 through the third flow path 9), that is, at this time, the internal heat exchanger 23 serves as a through flow path, the liquid refrigerant discharged from the first refrigerant outlet of the internal heat exchanger 23 is depressurized in the first expansion valve 4, a gas-liquid two-phase refrigerant flows out from the outlet of the first expansion valve 4, and the gas-liquid two-phase refrigerant absorbs heat of the passenger compartment in the indoor heat exchanger 5, so that the humid air in the passenger compartment is condensed into water drops on the surface of the indoor heat exchanger 5, the air humidity in the passenger compartment is reduced, the gaseous refrigerant flowing out of the outlet of the indoor heat exchanger 5 enters the expansion switch valve 33 through the second flow path 8, the isenthalpic pressure is reduced in the expansion switch valve 33, the gas-liquid two-phase mixed refrigerant flows out of the outlet of the expansion switch valve 33, the gas-liquid two-phase mixed refrigerant absorbs the heat of the outside atmosphere in the outdoor heat exchanger 3, the low-pressure gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 3 enters the heat transfer fluid-low-pressure refrigerant heat exchanger 22 through the fourth flow path 14, the heat is absorbed in the heat transfer fluid-low-pressure refrigerant heat exchanger 22, the gaseous refrigerant flows out of the heat transfer fluid-low-pressure refrigerant heat exchanger 22, and the gaseous refrigerant returns to the compressor 1.
The fourth dehumidification mode described above may be applied to dehumidify the passenger compartment when the ambient temperature is less than 5 ℃.
Optionally, the suction superheat degree of the compressor 1 can be controlled to be 3-7K in a heat pump heating mode and a dehumidification mode, and the control is easier.
In some embodiments, when the vehicle thermal management system is in the battery pack cooling mode, the cooling medium flows through the ninth cooling medium fluid circuit or the tenth cooling medium fluid circuit, and the heat transfer fluid flows through the fourth heat transfer fluid circuit;
in the ninth refrigerant fluid circuit, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25, the second flow path 8, the ninth connection point 38 and the first through flow path 12 to enter the outdoor heat exchanger 3, after releasing heat to the outside air in the outdoor heat exchanger 3, the refrigerant enters the second expansion valve 17 through the first connection point 44 and the second connection point 41, after being decompressed by the second expansion valve 17, the refrigerant enters the second heat exchanger 16, and after absorbing heat of the heat transfer fluid in the second heat exchanger 16, the refrigerant returns to the compressor 1 through the fourth connection point 42 and the fifth connection point 43;
in the tenth refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25, the third flow path 9 and the second connection point 41 and enters the second expansion valve 17, the refrigerant enters the second heat exchanger 16 after being subjected to pressure reduction by the second expansion valve 17, and the refrigerant returns to the compressor 1 through the fourth connection point 42 and the fifth connection point 43 after absorbing heat of heat transfer fluid in the second heat exchanger 16;
in the fourth heat transfer fluid circuit, the heat transfer fluid flowing out of the first heat exchanger 2 enters the outdoor radiator 7 through the first water pump 6, and the heat transfer fluid returns to the first heat exchanger 2 through the sixth connection point 45 after radiating heat to the outside air in the outdoor radiator 7; the heat transfer fluid flowing out of the second heat exchanger 16 enters the battery pack 18 through the second water pump 19, and the heat transfer fluid absorbs heat of the battery pack 18 and then returns to the second heat exchanger 16;
when the vehicle thermal management system is in a battery pack cooling mode, in the first heat exchanger 2, the refrigerant releases heat to the heat transfer fluid, and the heat transfer fluid absorbs heat; in the second heat exchanger 16, the refrigerant absorbs heat of the heat transfer fluid, and the heat transfer fluid releases heat.
In this embodiment, the working mode in which the refrigerant of the vehicle thermal management system flows through the ninth refrigerant fluid circuit and the heat transfer fluid flows through the fourth heat transfer fluid circuit is referred to as a first battery pack cooling mode, and the working mode in which the refrigerant of the vehicle thermal management system flows through the tenth refrigerant fluid circuit and the heat transfer fluid flows through the fourth heat transfer fluid circuit is referred to as a second battery pack cooling mode.
In some possible implementations, in the first battery pack cooling mode, referring to fig. 3, the first stop valve 26 is opened, the second stop valve 27 is closed, the expansion switch valve 33 is in a flow state (i.e., the flow passage inside the expansion switch valve 33 is open and the throttle passage is closed), the third stop valve 29 is closed, the fourth stop valve 30 is closed, the first expansion valve 4 is closed, the second expansion valve 17 is opened, the first water pump 6 is opened, the first two-way valve 35 is opened, the second two-way valve 36 is closed, the second water pump 19 is opened, and the third water pump 21 is closed.
As shown in fig. 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature high-pressure gaseous refrigerant from an outlet of the compressor 1, the high-temperature high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the outdoor heat sink 7 under the pumping of the first water pump 6 and radiates heat to the outside atmosphere in the outdoor heat sink 7, and the low-temperature heat transfer fluid flowing out of an outlet of the outdoor heat sink 7 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant which radiates heat to the heat transfer fluid flows out from the refrigerant outlet of the first heat exchanger 2, the refrigerant is subjected to gas-liquid separation through the high-pressure liquid drying tank 25, the liquid refrigerant flows out from the outlet of the high-pressure liquid drying tank 25, the liquid refrigerant passes through the second flow path 8 and is directly conducted in the expansion switch valve 33 without being throttled and depressurized, the liquid refrigerant still flows out from the outlet of the expansion switch valve 33, the liquid refrigerant releases heat to the outside atmosphere in the outdoor heat exchanger 3, the liquid refrigerant which flows out from the outlet of the outdoor heat exchanger 3 and releases heat enters the internal heat exchanger 23 and continues releasing heat in the internal heat exchanger 23, the liquid refrigerant which flows out from the first refrigerant outlet of the internal heat exchanger 23 is throttled and depressurized by the second expansion valve 17, the enthalpy pressure of the liquid refrigerant in the second expansion valve 17 is reduced, and the low-temperature and low-pressure gas-liquid two-phase refrigerant which flows out from the outlet of the second expansion valve 17 absorbs the heat of the high-temperature heat transfer fluid which absorbs heat from the battery pack 18 in the second heat exchanger 16, the low-temperature heat transfer fluid flows out of the first heat transfer fluid outlet of the second heat exchanger 16, the low-temperature heat transfer fluid can cool the battery pack 18, the refrigerant flowing out of the refrigerant outlet of the second heat exchanger 16 obtains heat lost by the liquid refrigerant flowing out of the outlet of the outdoor heat exchanger 3 in the internal heat exchanger 23, and the gaseous refrigerant flows out of the second refrigerant outlet of the internal heat exchanger 23 and finally returns to the compressor 1.
In the first battery pack cooling mode, the refrigerant first passes through the first heat exchanger 2 and loses heat by the outdoor heat radiator 7, and then passes through the outdoor heat exchanger 3 to lose heat again. This first battery pack cooling mode enables rapid cooling of the battery pack 18 in a high-temperature environment.
In some possible implementations, in the second pack cooling mode, referring to fig. 3, the first cut-off valve 26 is closed, the second cut-off valve 27 is opened, the expansion switch valve 33 is closed, the third cut-off valve 29 is closed, the fourth cut-off valve 30 is closed, the first expansion valve 4 is closed, the second expansion valve 17 is opened, the first water pump 6 is opened, the first two-way valve 35 is opened, the second two-way valve 36 is closed, the second water pump 19 is opened, and the third water pump 21 is closed.
As shown in fig. 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature high-pressure gaseous refrigerant from an outlet of the compressor 1, the high-temperature high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the outdoor heat sink 7 under the pumping of the first water pump 6 and dissipates heat to the outside atmosphere in the outdoor heat sink 7, and the low-temperature heat transfer fluid flowing out of an outlet of the outdoor heat sink 7 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant discharged from the refrigerant outlet of the first heat exchanger 2 releases heat to the heat transfer fluid, the refrigerant is subjected to gas-liquid separation in the high-pressure liquid drying tank 25, the liquid refrigerant flows out from the outlet of the high-pressure liquid drying tank 25, the liquid refrigerant flows into the internal heat exchanger 23 through the third flow path 9 and loses heat in the internal heat exchanger 23, the liquid refrigerant flowing out from the first refrigerant outlet of the internal heat exchanger 23 is throttled and depressurized by the second expansion valve 17, the enthalpy pressure of the liquid refrigerant in the second expansion valve 17 is reduced, the low-temperature and low-pressure gas-liquid two-phase refrigerant flows out from the outlet of the second expansion valve 17, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the high-temperature heat transfer fluid absorbed at the battery pack 18 in the second heat exchanger 16, the low-temperature heat transfer fluid flows out from the first heat transfer fluid outlet of the second heat exchanger 16, and the low-temperature heat transfer fluid can cool the battery pack 18, the refrigerant flowing out of the refrigerant outlet of the second heat exchanger 16 obtains heat lost from the liquid refrigerant flowing out of the outlet of the high pressure liquid desiccant tank 25 in the interior heat exchanger 23 by the interior heat exchanger 23, and the gaseous refrigerant flows out of the second refrigerant outlet of the interior heat exchanger 23 and finally returns to the compressor 1.
In some embodiments, when the vehicle thermal management system is in a passenger compartment cooling and battery pack cooling mode, the cooling medium flows through the eleventh cooling medium fluid circuit or the twelfth cooling medium fluid circuit, and the heat transfer fluid flows through the fourth heat transfer fluid circuit;
in the eleventh refrigerant fluid circuit, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25, the second flow path 8, the ninth connection point 38 and the first through-flow path 12 to enter the outdoor heat exchanger 3, the refrigerant releases heat to the outside air in the outdoor heat exchanger 3, and the refrigerant flowing out of the outdoor heat exchanger 3 passes through the first connection point 44 and the second connection point 41 and then is divided into two paths: one path of refrigerant is depressurized by the first expansion valve 4, enters the indoor heat exchanger 5, absorbs heat of the passenger compartment in the indoor heat exchanger 5, and returns to the compressor 1 through the third connection point 39, the first flow path 13, the fourth connection point 42 and the fifth connection point 43; the other path of refrigerant enters the second heat exchanger 16 after being subjected to pressure reduction by the second expansion valve 17, absorbs heat of the heat transfer fluid in the second heat exchanger 16, and then returns to the compressor 1 through the fourth connection point 42 and the fifth connection point 43;
in the twelfth refrigerant fluid loop, the refrigerant passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25 and the third flow path 9 in sequence, and the refrigerant flowing out of the third flow path 9 is divided into two paths: one path of refrigerant is depressurized by the first expansion valve 4, enters the indoor heat exchanger 5, absorbs heat of the passenger compartment in the indoor heat exchanger 5, and returns to the compressor 1 through the third connection point 39, the first flow path 13, the fourth connection point 42 and the fifth connection point 43; the other path of refrigerant enters the second heat exchanger 16 after being subjected to pressure reduction by the second expansion valve 17, and after absorbing heat of heat transfer fluid in the second heat exchanger 16, the refrigerant returns to the compressor 1 through the fourth connection point 42 and the fifth connection point 43;
when the vehicle thermal management system is in a passenger compartment refrigeration mode and a battery pack cooling mode, in the first heat exchanger 2, the refrigerant releases heat to the heat transfer fluid, and the heat transfer fluid absorbs heat; in the second heat exchanger 16, the refrigerant absorbs heat of the heat transfer fluid, and the heat transfer fluid releases heat.
In this embodiment, the operation mode in which the refrigerant of the vehicle thermal management system flows through the eleventh refrigerant fluid circuit and the heat transfer fluid flows through the fourth heat transfer fluid circuit is referred to as the first passenger compartment cooling and battery pack cooling mode, and the operation mode in which the refrigerant of the vehicle thermal management system flows through the twelfth refrigerant fluid circuit and the heat transfer fluid flows through the fourth heat transfer fluid circuit is referred to as the second passenger compartment cooling and battery pack cooling mode.
In some possible implementations, in the first passenger compartment cooling and battery pack cooling mode, referring to fig. 3, the first stop valve 26 is opened, the second stop valve 27 is closed, the expansion switch valve 33 is in the flow state (i.e., the flow passage inside the expansion switch valve 33 is on, the throttle flow passage is off), the third stop valve 29 is opened, the fourth stop valve 30 is closed, the first expansion valve 4 is opened, the second expansion valve 17 is opened, the first water pump 6 is opened, the first two-way valve 35 is opened, the second two-way valve 36 is closed, the second water pump 19 is opened, and the third water pump 21 is closed.
As shown in fig. 3, in the first passenger compartment refrigeration and battery pack cooling mode, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant, so that the outlet of the compressor 1 discharges the high-temperature and high-pressure gaseous refrigerant, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of the heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the outdoor heat sink 7 under the pumping of the first water pump 6 and dissipates heat to the outside atmosphere in the outdoor heat sink 7, and the low-temperature heat transfer fluid flowing out of the outlet of the outdoor heat sink 7 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 and continues to absorb heat of the high-temperature and high-pressure gaseous refrigerant. The refrigerant which releases heat to the heat transfer fluid flows out of the refrigerant outlet of the first heat exchanger 2, the refrigerant is subjected to gas-liquid separation through the high-pressure liquid drying tank 25, the liquid refrigerant flows out of the outlet of the high-pressure liquid drying tank 25, the liquid refrigerant enters the outdoor heat exchanger 3 through the second flow path 8 and the first through flow path 12, the liquid refrigerant is discharged to the outside atmosphere in the outdoor heat exchanger 3, the liquid refrigerant flowing out of the outlet of the outdoor heat exchanger 3 enters the internal heat exchanger 23 and loses heat in the internal heat exchanger 23, the liquid refrigerant flowing out of the first refrigerant outlet of the internal heat exchanger 23 is divided into two streams, one stream is throttled and decompressed by the first expansion valve 4, the enthalpy pressure of the liquid refrigerant in the first expansion valve 4 is reduced, the gas-liquid two-phase refrigerant flows out of the outlet of the first expansion valve 4, the gas-liquid two-phase refrigerant absorbs heat of the passenger compartment in the indoor heat exchanger 5 to reduce the temperature of the passenger compartment, the other branch is throttled and depressurized in the second expansion valve 17, the enthalpy pressure of the liquid refrigerant in the second expansion valve 17 is reduced, the low-temperature and low-pressure gas-liquid two-phase refrigerant flows out of the outlet of the second expansion valve 17, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs the heat of the high-temperature heat transfer fluid absorbed at the battery pack 18 in the second heat exchanger 16, the low-temperature heat transfer fluid flows out from the first heat transfer fluid outlet of the second heat exchanger 16, the low-temperature heat transfer fluid can cool the battery pack 18, the refrigerant flowing out of the refrigerant outlet of the second heat exchanger 16 and the refrigerant flowing out of the outlet of the indoor heat exchanger 5 are converged and then enter the internal heat exchanger 23, and obtains the heat lost in the interior heat exchanger 23 from the liquid refrigerant flowing out of the outlet of the exterior heat exchanger 3 in the interior heat exchanger 23, and the gaseous refrigerant flows out of the second refrigerant outlet of the interior heat exchanger 23 and returns to the compressor 1.
In some possible implementations, in the second passenger compartment cooling and battery pack cooling mode, referring to fig. 3, the first stop valve 26 is closed, the second stop valve 27 is opened, the expansion switch valve 33 is closed, the third stop valve 29 is opened, the fourth stop valve 30 is closed, the first expansion valve 4 is opened, the second expansion valve 17 is opened, the first water pump 6 is opened, the first two-way valve 35 is opened, the second two-way valve 36 is closed, the second water pump 19 is opened, and the third water pump 21 is closed.
As shown in fig. 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature high-pressure gaseous refrigerant from an outlet of the compressor 1, the high-temperature high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the outdoor heat sink 7 under the pumping of the first water pump 6 and dissipates heat to the outside atmosphere in the outdoor heat sink 7, and the low-temperature heat transfer fluid flowing out of an outlet of the outdoor heat sink 7 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant which releases heat to the heat transfer fluid flows out of the refrigerant outlet of the first heat exchanger 2, the refrigerant is subjected to gas-liquid separation through the high-pressure liquid drying tank 25, the liquid refrigerant flows out of the outlet of the high-pressure liquid drying tank 25, the liquid refrigerant enters the internal heat exchanger 23 through the third flow path 9 and loses heat in the internal heat exchanger 23, the liquid refrigerant flowing out of the first refrigerant outlet of the internal heat exchanger 23 is divided into two parts, one part of the liquid refrigerant is throttled and depressurized by the first expansion valve 4, the enthalpy pressure of the liquid refrigerant in the first expansion valve 4 is reduced, the gas-liquid two-phase refrigerant flows out of the outlet of the first expansion valve 4, the gas-liquid two-phase refrigerant absorbs the heat of the passenger compartment in the indoor heat exchanger 5 to reduce the temperature of the passenger compartment, the other part of the liquid refrigerant is throttled and depressurized in the second expansion valve 17, the enthalpy pressure of the liquid refrigerant in the second expansion valve 17 is reduced, and the low-temperature and low-pressure gas-liquid two-liquid-phase refrigerant flows out of the outlet of the second expansion valve 17, the low-temperature and low-pressure gas-liquid two-phase refrigerant absorbs heat of the high-temperature heat transfer fluid absorbed at the battery pack 18 in the second heat exchanger 16, the low-temperature heat transfer fluid flows out of the first heat transfer fluid outlet of the second heat exchanger 16, the low-temperature heat transfer fluid can cool the battery pack 18, the refrigerant flowing out of the refrigerant outlet of the second heat exchanger 16 and the refrigerant flowing out of the outlet of the indoor heat exchanger 5 converge and then enter the internal heat exchanger 23, heat lost by the liquid refrigerant flowing out of the outlet of the high-pressure liquid drying tank 25 in the internal heat exchanger 23 is obtained in the internal heat exchanger 23, the gaseous refrigerant flows out of the second refrigerant outlet of the internal heat exchanger 23, and the gaseous refrigerant returns to the compressor 1.
In some embodiments, when the vehicle thermal management system is in the heat recovery mode, the refrigerant flows through the tenth refrigerant fluid circuit and the heat transfer fluid flows through the fifth heat transfer fluid circuit;
in the tenth refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25, the third flow path 9 and the second connection point 41 and enters the second expansion valve 17, the refrigerant enters the second heat exchanger 16 after being subjected to pressure reduction by the second expansion valve 17, and the refrigerant returns to the compressor 1 through the fourth connection point 42 and the fifth connection point 43 after absorbing heat of heat transfer fluid in the second heat exchanger 16;
in the fifth heat transfer fluid loop, the heat transfer fluid flowing out of the first heat exchanger 2 enters the indoor warm air core 10 through the first water pump 6 and the seventh connection point 46, and after the heat transfer fluid is radiated to the passenger compartment in the indoor warm air core 10, the heat transfer fluid returns to the first heat exchanger 2 through the eighth connection point 47 and the sixth connection point 45; the heat transfer fluid flowing out of the second heat exchanger 16 enters the electronic device 20 through the third water pump 21, and the heat transfer fluid absorbs the heat of the electronic device 20 and then returns to the second heat exchanger 16;
when the vehicle thermal management system is in a heat recovery mode, in the first heat exchanger 2, the refrigerant releases heat to the heat transfer fluid, and the heat transfer fluid absorbs heat; in the second heat exchanger 16, the refrigerant absorbs heat of the heat transfer fluid, and the heat transfer fluid releases heat.
In some possible implementations, in the heat recovery mode, referring to fig. 3, the first cut-off valve 26 is closed, the second cut-off valve 27 is opened, the expansion switch valve 33 is closed, the third cut-off valve 29 is closed, the fourth cut-off valve 30 is closed, the first expansion valve 4 is closed, the second expansion valve 17 is opened, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is opened.
As shown in fig. 3, in the heat recovery mode, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature high-pressure gaseous refrigerant from an outlet of the compressor 1, the high-temperature high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6 and dissipates heat to the passenger compartment in the indoor warm air core 10 to increase the temperature of the passenger compartment, and the low-temperature heat transfer fluid flowing out of the outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant which releases heat to the heat transfer fluid flows out of the refrigerant outlet of the first heat exchanger 2, the refrigerant is subjected to gas-liquid separation through the high-pressure liquid drying tank 25, the liquid refrigerant flows out of the outlet of the high-pressure liquid drying tank 25, the liquid refrigerant flows into the internal heat exchanger 23 through the third flow path 9 and loses heat in the internal heat exchanger 23, the enthalpy pressure of the liquid refrigerant flowing out of the first refrigerant outlet of the internal heat exchanger 23 in the second expansion valve 17 is reduced, the low-temperature low-pressure gas-liquid two-phase refrigerant flows out of the outlet of the second expansion valve 17, the low-temperature low-pressure gas-liquid two-phase refrigerant absorbs the heat of the high-temperature heat transfer fluid absorbed at the electronic device 20 in the second heat exchanger 16 to recover the waste heat of the electronic device 20 into the refrigerant loop, the air and enthalpy of the refrigerant are supplemented, and the refrigerant is obtained in the internal heat exchanger 23, the liquid refrigerant flowing out of the refrigerant outlet of the second heat exchanger 16 from the high-pressure liquid drying tank 25 loses the heat exchanger 23 Heat, the second refrigerant outlet of the interior heat exchanger 23 flows out the gaseous refrigerant, which is returned to the compressor 1.
In some embodiments, when the vehicle thermal management system is in the heat pump and heat recovery mode, the refrigerant flows through the thirteenth refrigerant fluid circuit or the fourteenth refrigerant fluid circuit, and the heat transfer fluid flows through the sixth heat transfer fluid circuit; or when the vehicle thermal management system is in a heat pump and heat recovery mode, the refrigerant flows through the fifteenth refrigerant fluid loop, and the heat transfer fluid flows through the fifth heat transfer fluid loop;
in the thirteenth refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2 and the high-pressure liquid drying tank 25 to enter the third flow path 9, and the refrigerant flowing out of the third flow path 9 is divided into two paths: one path of refrigerant is depressurized by the first expansion valve 4 and then enters the indoor heat exchanger 5, after releasing heat to the passenger compartment in the indoor heat exchanger 5, the refrigerant enters the outdoor heat exchanger 3 through the third connection point 39, the first check valve 15, the ninth connection point 38 and the first throttle flow path 11, after absorbing heat of outside air in the outdoor heat exchanger 3, the refrigerant enters the heat transfer fluid-low pressure refrigerant heat exchanger 22 through the first connection point 44 and the fourth flow path 14, and after absorbing heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22, the refrigerant returns to the compressor 1 through the fifth connection point 43; the other path of refrigerant enters the second heat exchanger 16 after being subjected to pressure reduction by the second expansion valve 17, and after absorbing heat of heat transfer fluid in the second heat exchanger 16, the refrigerant returns to the compressor 1 through the fourth connection point 42 and the fifth connection point 43;
in the fourteenth refrigerant fluid loop, the refrigerant sequentially passes through the compressor 1 and the first heat exchanger 2 to enter the high-pressure liquid drying tank 25, and the refrigerant flowing out of the high-pressure liquid drying tank 25 is divided into two paths: one path of refrigerant enters the second expansion valve 17 through the third flow path 9, enters the second heat exchanger 16 after being subjected to pressure reduction through the second expansion valve 17, and returns to the compressor 1 through the fourth connection point 42 and the fifth connection point 43 after absorbing heat of heat transfer fluid in the second heat exchanger 16; the other path of refrigerant enters the outdoor heat exchanger 3 through the second flow path 8, the ninth connection point 38 and the first throttling flow path 11, the refrigerant enters the heat transfer fluid-low pressure refrigerant heat exchanger 22 through the first connection point 44 and the fourth flow path 14 after absorbing heat of outside air in the outdoor heat exchanger 3, and the refrigerant returns to the compressor 1 through the fifth connection point 43 after absorbing heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22;
in the sixth heat transfer fluid circuit, the heat transfer fluid flowing out of the first heat exchanger 2 is divided into two paths after passing through the first water pump 6 and the seventh connection point 46: one path of heat transfer fluid enters the indoor warm air core 10, and returns to the first heat exchanger 2 through the eighth connection point 47 and the sixth connection point 45 after radiating heat to the passenger compartment in the indoor warm air core 10; the other path of heat transfer fluid enters the heat transfer fluid-low pressure refrigerant heat exchanger 22, releases heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22, and returns to the first heat exchanger 2 through the eighth connection point 47 and the sixth connection point 45; the heat transfer fluid flowing out of the second heat exchanger 16 enters the electronic device 20 through the third water pump 21, and the heat transfer fluid returns to the second heat exchanger 16 after absorbing heat of the electronic device 20;
in the fifteenth refrigerant fluid circuit, the refrigerant sequentially passes through the compressor 1, the first heat exchanger 2, the high-pressure liquid drying tank 25, the second flow path 8, the ninth connection point 38 and the first throttle flow path 11 to enter the outdoor heat exchanger 3, the refrigerant absorbs heat of outside air in the outdoor heat exchanger 3, then enters the second expansion valve 17 through the first connection point 44 and the second connection point 41, is subjected to pressure reduction by the second expansion valve 17 and then enters the second heat exchanger 16, and the refrigerant absorbs heat of heat transfer fluid in the second heat exchanger 16 and then returns to the compressor 1 through the fourth connection point 42 and the fifth connection point 43;
when the vehicle thermal management system is in a heat pump and heat recovery mode, in the first heat exchanger 2, the refrigerant releases heat to the heat transfer fluid, and the heat transfer fluid absorbs heat; in the second heat exchanger 16, the refrigerant absorbs heat of the heat transfer fluid, and the heat transfer fluid releases heat; in the heat transfer fluid-low pressure refrigerant heat exchanger 22, the refrigerant flowing out of the exterior heat exchanger 3 and entering the heat transfer fluid-low pressure refrigerant heat exchanger 22 absorbs heat, and the heat transfer fluid flowing out of the first heat exchanger 2 and entering the heat transfer fluid-low pressure refrigerant heat exchanger 22 releases heat.
In this embodiment, the working mode that the refrigerant of the vehicle thermal management system flows through the thirteenth refrigerant fluid circuit and the heat transfer fluid flows through the sixth heat transfer fluid circuit is referred to as the first heat pump and heat recovery mode, the working mode that the refrigerant of the vehicle thermal management system flows through the fourteenth refrigerant fluid circuit and the heat transfer fluid flows through the sixth heat transfer fluid circuit is referred to as the second heat pump and heat recovery mode, the working mode that the refrigerant of the vehicle thermal management system flows through the fifteenth refrigerant fluid circuit and the working mode that the heat transfer fluid flows through the fifth heat transfer fluid circuit is referred to as the third heat pump and heat recovery mode.
In some possible implementations, in the first heat pump and heat recovery mode, referring to fig. 3, the first stop valve 26 is closed, the second stop valve 27 is opened, the expansion switch valve 33 is in a throttling state (i.e., the throttling flow passage inside the expansion switch valve 33 is on and the through flow passage is off), the third stop valve 29 is closed, the fourth stop valve 30 is opened, the first expansion valve 4 is opened, the second expansion valve 17 is opened, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is opened.
In the first heat pump and heat recovery mode, as shown in fig. 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, a part of the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6 and dissipates heat in the indoor warm air core 10 to the passenger compartment, the temperature of the passenger compartment is increased, and the low-temperature heat transfer fluid flowing out of the outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb heat of the high-temperature and high-pressure gaseous refrigerant; the other part of the high-temperature heat transfer fluid flows into the heat transfer fluid-low pressure refrigerant heat exchanger 22 to release heat, and the low-temperature heat transfer fluid flowing out of the heat transfer fluid-low pressure refrigerant heat exchanger 22 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant discharged from the refrigerant outlet of the first heat exchanger 2 releases heat to the heat transfer fluid, the refrigerant undergoes gas-liquid separation in the high pressure liquid drying tank 25, the liquid refrigerant flows out from the outlet of the high pressure liquid drying tank 25, the liquid refrigerant flows into the internal heat exchanger 23 through the third flow path 9, the liquid refrigerant loses heat in the internal heat exchanger 23, the liquid refrigerant discharged from the first refrigerant outlet of the internal heat exchanger 23 is divided into two streams, one stream has reduced enthalpy pressure in the first expansion valve 4, the liquid refrigerant discharged from the outlet of the first expansion valve 4 has reduced pressure, the liquid refrigerant releases heat in the indoor heat exchanger 5 to the passenger compartment to preheat the air flowing through the indoor warm air core 10, the liquid refrigerant discharged from the outlet of the indoor heat exchanger 5 throttles the pressure reduction by the expansion switch valve 33 and flows into the outdoor heat exchanger 3, and absorbs the heat of the outside air in the outdoor heat exchanger 3, the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 3 absorbs heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22, and the gas refrigerant flows out of the heat transfer fluid-low pressure refrigerant heat exchanger 22; the enthalpy pressure of the other liquid refrigerant flowing out of the first refrigerant outlet of the internal heat exchanger 23 is reduced in the second expansion valve 17, a gas-liquid two-phase mixed refrigerant flows out of the outlet of the second expansion valve 17, the gas-liquid two-phase refrigerant absorbs the heat of the high-temperature heat transfer fluid absorbed by the electronic device 20 in the second heat exchanger 16 to recover the waste heat of the electronic device 20 to the refrigerant loop, the gas is supplemented and the enthalpy of the refrigerant is increased, the refrigerant flowing out of the refrigerant outlet of the second heat exchanger 16 obtains the heat lost by the liquid refrigerant flowing out of the outlet of the high-pressure liquid drying tank 25 in the internal heat exchanger 23, and the gaseous refrigerant flowing out of the second refrigerant outlet of the internal heat exchanger 23 is mixed with the gaseous refrigerant flowing out of the heat transfer fluid-low-pressure refrigerant heat exchanger 22 and then returns to the compressor 1.
In some possible implementations, in the second heat pump and heat recovery mode, referring to fig. 3, the first stop valve 26 is opened, the second stop valve 27 is opened, the expansion switch valve 33 is in a throttling state (i.e., the throttling flow passage inside the expansion switch valve 33 is on, and the through flow passage is off), the third stop valve 29 is closed, the fourth stop valve 30 is opened, the first expansion valve 4 is closed, the second expansion valve 17 is opened, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is opened.
In the second heat pump and heat recovery mode, as shown in fig. 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant from an outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of a heat transfer fluid outlet of the first heat exchanger 2, a part of the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6 and dissipates heat to the passenger compartment in the indoor warm air core 10 to increase the temperature in the passenger compartment, and the low-temperature heat transfer fluid flowing out of the outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through a heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature and high-pressure gaseous refrigerant; the other part of the high-temperature heat transfer fluid flows into the heat transfer fluid-low pressure refrigerant heat exchanger 22 to release heat, and the low-temperature heat transfer fluid flowing out of the heat transfer fluid-low pressure refrigerant heat exchanger 22 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature high-pressure gaseous refrigerant. The refrigerant which releases heat to the heat transfer fluid flows out of the refrigerant outlet of the first heat exchanger 2, the refrigerant is subjected to gas-liquid separation through the high-pressure liquid drying tank 25, the liquid refrigerant flows out of the liquid outlet of the high-pressure liquid drying tank 25, the liquid refrigerant is divided into two parts, one part flows into the internal heat exchanger 23 through the third flow path 9 and loses heat in the internal heat exchanger 23, the liquid refrigerant flowing out of the first refrigerant outlet of the internal heat exchanger 23 is throttled and depressurized by the second expansion valve 17, the enthalpy pressure of the liquid refrigerant in the second expansion valve 17 is reduced, the gas-liquid two-phase mixed refrigerant flows out of the outlet of the second expansion valve 17, the gas-liquid two-phase refrigerant absorbs the heat of the high-temperature heat transfer fluid absorbed at the electronic device 20 in the second heat exchanger 16, so that the waste heat of the electronic device 20 is recovered into the refrigerant loop, the gas and enthalpy are added to the refrigerant, and the refrigerant flowing out of the refrigerant outlet of the second heat exchanger 16 obtains the heat from the liquid outlet of the high-pressure liquid drying tank 25 in the internal heat exchanger 23 The heat lost from the liquid refrigerant in the internal heat exchanger 23 and the gaseous refrigerant flowing out of the second refrigerant outlet of the internal heat exchanger 23; the enthalpy pressure of the other liquid refrigerant is reduced in the expansion switch valve 33, a gas-liquid two-phase mixed refrigerant flows out of the outlet of the expansion switch valve 33, the gas-liquid two-phase mixed refrigerant absorbs the heat of the outside atmosphere in the outdoor heat exchanger 3, the gas-liquid two-phase mixed refrigerant flowing out of the outlet of the outdoor heat exchanger 3 absorbs the heat in the heat transfer fluid-low pressure refrigerant heat exchanger 22, a gaseous refrigerant flows out of the heat transfer fluid-low pressure refrigerant heat exchanger 22, and the gaseous refrigerant flowing out of the second refrigerant outlet of the internal heat exchanger 23 converge and then return to the compressor 1.
In some possible implementations, in the third heat pump and heat recovery mode, referring to fig. 3, the first stop valve 26 is opened, the second stop valve 27 is closed, the expansion switch valve 33 is in a throttling state (i.e., the throttling flow passage inside the expansion switch valve 33 is on, and the through flow passage is off), the third stop valve 29 is closed, the fourth stop valve 30 is closed, the first expansion valve 4 is closed, the second expansion valve 17 is opened, the first water pump 6 is opened, the first two-way valve 35 is closed, the second two-way valve 36 is opened, the second water pump 19 is closed, and the third water pump 21 is opened.
In the third heat pump and heat recovery mode, as shown in fig. 3, the refrigerant entering the compressor 1 is a gaseous refrigerant, the compressor 1 compresses the gaseous refrigerant to discharge a high-temperature and high-pressure gaseous refrigerant from the outlet of the compressor 1, the high-temperature and high-pressure gaseous refrigerant flows into the first heat exchanger 2 and releases heat to the low-temperature heat transfer fluid in the first heat exchanger 2, the high-temperature heat transfer fluid flows out of the heat transfer fluid outlet of the first heat exchanger 2, the high-temperature heat transfer fluid flows into the indoor warm air core 10 under the pumping of the first water pump 6 and radiates heat to the passenger compartment in the indoor warm air core 10 to increase the temperature in the passenger compartment, and the low-temperature heat transfer fluid flowing out of the outlet of the indoor warm air core 10 returns to the first heat exchanger 2 through the heat transfer fluid inlet of the first heat exchanger 2 to continuously absorb the heat of the high-temperature and high-pressure gaseous refrigerant. The refrigerant discharged from the heat transfer fluid flows into the refrigerant outlet of the first heat exchanger 2, the refrigerant undergoes gas-liquid separation in the high-pressure liquid drying tank 25, the liquid refrigerant flows out from the liquid outlet of the high-pressure liquid drying tank 25, the enthalpy pressure of the liquid refrigerant in the expansion switch valve 33 is reduced, a gas-liquid two-phase mixed refrigerant flows out from the outlet of the expansion switch valve 33, the gas-liquid two-phase mixed refrigerant absorbs the heat of the outside atmosphere in the exterior heat exchanger 3, the gas-liquid two-phase mixed refrigerant flowing out from the outlet of the exterior heat exchanger 3 flows into the interior heat exchanger 23 and loses the heat in the interior heat exchanger 23, the liquid refrigerant flowing out from the first refrigerant outlet of the interior heat exchanger 23 is throttled and reduced in pressure by the second expansion valve 17, the enthalpy pressure of the liquid refrigerant in the second expansion valve 17 is reduced, the refrigerant flowing out from the outlet of the second expansion valve 17 and reduced in pressure absorbs the heat of the high-temperature heat transfer fluid absorbed by the electronic device 20 in the second heat exchanger 16, the waste heat of the electronic device 20 is recovered to the refrigerant loop to supplement air and enthalpy to the refrigerant, the refrigerant flowing out of the refrigerant outlet of the second heat exchanger 16 obtains the heat lost by the liquid refrigerant flowing out of the outlet of the outdoor heat exchanger 3 in the internal heat exchanger 23, the gaseous refrigerant flows out of the outlet of the internal heat exchanger 23, and the gaseous refrigerant returns to the compressor 1.
It should be noted that the above modes provide the main operation modes of the vehicle thermal management system for the present application, and the operation modes that are not mentioned in the present application, but the operation modes that can be realized by the vehicle thermal management system provided in the present application also belong to the protection scope of the present application.
Corresponding to above-mentioned vehicle thermal management system, the embodiment of the utility model provides a vehicle is still provided, including the vehicle thermal management system that any embodiment provided as above to have the beneficial effect of any kind of above-mentioned vehicle thermal management system.
The above embodiments are only used to illustrate the technical solution of the present invention, and not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it should be understood by those skilled in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; such modifications and substitutions do not depart from the spirit and scope of the present invention in its corresponding aspects.

Claims (13)

1. A vehicle thermal management system, comprising:
the refrigerant fluid loop is used for enabling refrigerant fluid to flow in and comprises a compressor (1), a first heat exchanger (2), a high-pressure liquid drying tank (25), a heat transfer fluid-low-pressure refrigerant heat exchanger (22), an outdoor heat exchanger (3), a first expansion valve (4), an indoor heat exchanger (5) and a first flow path (13) which is selectively communicated or cut off;
a heat transfer fluid circuit in which a heat transfer fluid flows, the heat transfer fluid circuit comprising the first heat exchanger (2), a first water pump (6), the heat transfer fluid-low pressure refrigerant heat exchanger (22), and an outdoor heat sink (7);
the outlet of the compressor (1) is connected with the refrigerant inlet of the first heat exchanger (2), the refrigerant outlet of the first heat exchanger (2) is connected with the inlet of the high-pressure liquid drying tank (25), the liquid outlet of the high-pressure liquid drying tank (25) is connected with the inlet of the outdoor heat exchanger (3), an outlet of the outdoor heat exchanger (3) is connected to an inlet of the first expansion valve (4) through a first connection point (44) and a second connection point (41), the outlet of the first expansion valve (4) is connected with the inlet of the indoor heat exchanger (5), an outlet of the indoor heat exchanger (5) is connected to an inlet of the first flow path (13) via a third connection point (39), the outlet of the first flow path (13) is connected to the inlet of the compressor (1) via a fourth connection point (42) and a fifth connection point (43);
the outlet of the outdoor heat exchanger (3) is also connected with the refrigerant inlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) through the first connection point (44), and the refrigerant outlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) is connected with the inlet of the compressor (1) through the fifth connection point (43);
the heat transfer fluid outlet of the first heat exchanger (2) is connected with the inlet of the outdoor radiator (7), and the outlet of the outdoor radiator (7) is connected with the heat transfer fluid inlet of the first heat exchanger (2) through a sixth connecting point (45); the first water pump (6) is arranged on a flow path between the outlet of the heat transfer fluid of the first heat exchanger (2) and the inlet of the outdoor radiator (7), or the first water pump (6) is arranged on a flow path between the outlet of the outdoor radiator (7) and the heat transfer fluid inlet of the first heat exchanger (2);
the heat transfer fluid outlet of the first heat exchanger (2) is further connected with the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) through a seventh connection point (46), and the heat transfer fluid outlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) is connected with the heat transfer fluid inlet of the first heat exchanger (2) through an eighth connection point (47) and the sixth connection point (45).
2. The vehicle thermal management system according to claim 1, wherein the coolant fluid circuit further comprises a second selectively open or closed flow path (8), a third selectively open or closed flow path (9), a first throttle flow path (11), a first flow path (12), a fourth selectively open or closed flow path (14), and a first check valve (15);
the liquid outlet of the high-pressure liquid drying tank (25) is connected with the inlet of the second flow path (8), the outlet of the indoor heat exchanger (5) is connected with the inlet of the first check valve (15) through the third connection point (39), and the outlet of the second flow path (8) and the outlet of the first check valve (15) are both selectively connected with the inlet of the outdoor heat exchanger (3) through the first throttling flow path (11) or the first through flow path (12) through a ninth connection point (38);
a liquid outlet of the high-pressure liquid drying tank (25) is connected to an inlet of the first expansion valve (4) via the third flow path (9);
the outlet of the outdoor heat exchanger (3) is also connected to the refrigerant inlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) via the first connection point (44) and the fourth flow path (14).
3. The vehicle thermal management system of claim 2, wherein the heat transfer fluid circuit further comprises an indoor warm air core (10);
the heat transfer fluid outlet of the first heat exchanger (2) is connected with the inlet of the outdoor radiator (7) through the first water pump (6), the heat transfer fluid outlet of the first heat exchanger (2) is also respectively connected with the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) and the inlet of the indoor warm air core body (10) through the first water pump (6) and the seventh connecting point (46), and the heat transfer fluid outlet of the first heat exchanger (2) is selectively communicated with the inlet of the outdoor radiator (7), the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) and the inlet of the indoor warm air core (10), the outlet of the indoor warm air core (10) is connected with the heat transfer fluid inlet of the first heat exchanger (2) through the eighth connecting point (47) and the sixth connecting point (45).
4. The vehicle thermal management system of claim 3, wherein the refrigerant fluid circuit further comprises a second heat exchanger (16) and a second expansion valve (17);
the heat transfer fluid circuit further comprising the second heat exchanger (16), a battery pack (18) and a second water pump (19);
an outlet of the outdoor heat exchanger (3) and an outlet of the third flow path (9) are both connected with a refrigerant inlet of the second heat exchanger (16) through the second connection point (41) and the second expansion valve (17), and a refrigerant outlet of the second heat exchanger (16) is connected with an inlet of the compressor (1) through the fourth connection point (42) and the fifth connection point (43);
the first heat transfer fluid outlet of the second heat exchanger (16) is connected with the inlet of the battery pack (18), and the outlet of the battery pack (18) is connected with the first heat transfer fluid inlet of the second heat exchanger (16);
the second water pump (19) is provided on a flow path between the first heat transfer fluid outlet of the second heat exchanger (16) and the inlet of the battery pack (18), or the second water pump (19) is provided on a flow path between the outlet of the battery pack (18) and the first heat transfer fluid inlet of the second heat exchanger (16).
5. The vehicle thermal management system of claim 4, wherein the heat transfer fluid circuit further comprises electronics (20) and a third water pump (21);
the second heat transfer fluid outlet of the second heat exchanger (16) is connected to the inlet of the electronics (20), the outlet of the electronics (20) is connected to the second heat transfer fluid inlet of the second heat exchanger (16);
the third water pump (21) is provided on a flow path between the second heat transfer fluid outlet of the second heat exchanger (16) and the inlet of the electronic device (20), or the third water pump (21) is provided on a flow path between the outlet of the electronic device (20) and the second heat transfer fluid inlet of the second heat exchanger (16);
wherein the electronic device (20) comprises at least one of a motor, a charger, a motor controller and a DC-DC converter.
6. The vehicle thermal management system of claim 2 or 3, wherein the coolant fluid circuit further comprises an internal heat exchanger (23);
an outlet of the third flow path (9) and an outlet of the outdoor heat exchanger (3) are both connected with a first refrigerant inlet of the internal heat exchanger (23) through a tenth connection point (40), a first refrigerant outlet of the internal heat exchanger (23) is connected with an inlet of the indoor heat exchanger (5) through the second connection point (41) and the first expansion valve (4), an outlet of the first flow path (13) is connected with a second refrigerant inlet of the internal heat exchanger (23) through the fourth connection point (42), and a second refrigerant outlet of the internal heat exchanger (23) is connected with an inlet of the compressor (1) through the fifth connection point (43); or,
an outlet of the outdoor heat exchanger (3) is connected with a first refrigerant inlet of the internal heat exchanger (23) through the first connection point (44), an inlet of the first expansion valve (4) is connected with a first refrigerant outlet of the internal heat exchanger (23) and an outlet of the third flow path (9) through an eleventh connection point (49), an outlet of the first flow path (13) is connected with a second refrigerant inlet of the internal heat exchanger (23) through the fourth connection point (42), and a second refrigerant outlet of the internal heat exchanger (23) is connected with an inlet of the compressor (1) through the fifth connection point (43).
7. The vehicle thermal management system of claim 4 or 5, characterized in that the coolant fluid circuit further comprises an internal heat exchanger (23);
the outlet of the third flow path (9) and the outlet of the outdoor heat exchanger (3) are both connected with the first refrigerant inlet of the internal heat exchanger (23) through a tenth connection point (40), a first refrigerant outlet of the interior heat exchanger (23) is connected to an inlet of the indoor heat exchanger (5) through the second connection point (41) and the first expansion valve (4), and the first refrigerant outlet of the interior heat exchanger (23) is further connected to the refrigerant inlet of the second heat exchanger (16) through the second connection point (41) and the second expansion valve (17), an outlet of the first flow path (13) and a refrigerant outlet of the second heat exchanger (16) are connected to a second refrigerant inlet of the interior heat exchanger (23) via a fourth connection point (42), a second refrigerant outlet of the internal heat exchanger (23) is connected to an inlet of the compressor (1) through the fifth connection point (43); or,
an outlet of the outdoor heat exchanger (3) is connected with a first refrigerant inlet of the internal heat exchanger (23) through the first connecting point (44), an inlet of the first expansion valve (4) and an inlet of the second expansion valve (17) are both connected with a first refrigerant outlet of the internal heat exchanger (23) and an outlet of the third flow path (9), an outlet of the first flow path (13) and a refrigerant outlet of the second heat exchanger (16) are both connected with a second refrigerant inlet of the internal heat exchanger (23) through a fourth connecting point (42), and a second refrigerant outlet of the internal heat exchanger (23) is connected with an inlet of the compressor (1) through the fifth connecting point (43).
8. The vehicle thermal management system of claim 6, wherein the coolant fluid circuit further comprises a second check valve (24);
an outlet of the outdoor heat exchanger (3) is connected with a first refrigerant inlet of the internal heat exchanger (23) through the first connecting point (44) and the second check valve (24); or,
the second check valve (24) is disposed at a first refrigerant outlet of the interior heat exchanger (23).
9. The vehicle thermal management system according to any of the claims 2 to 5, characterized in that a first shut-off valve (26) is arranged on the second flow path (8), a second shut-off valve (27) is arranged on the third flow path (9), and the outlet of the high-pressure liquid dryer tank (25) is connected with the inlet of the second flow path (8) and the inlet of the third flow path (9) through a twelfth connection point (37), respectively; or,
the refrigerant fluid loop further comprises a first three-way valve (28), the first three-way valve (28) is located on the second flow path (8) and the third flow path (9) at the same time, a port A of the first three-way valve (28) is connected with a liquid outlet of the high-pressure liquid drying tank (25), a port B of the first three-way valve (28) is connected with an inlet of the outdoor heat exchanger (3), and a port C of the first three-way valve (28) is connected with an inlet of the first expansion valve (4).
10. The vehicle thermal management system according to any of claims 2 to 5, characterized in that a third shut-off valve (29) is provided on the first flow path (13) and a fourth shut-off valve (30) is provided on the fourth flow path (14).
11. The vehicle thermal management system according to any one of claims 2 to 5, characterized in that a third expansion valve (31) is arranged on the first throttle flow path (11), a fifth stop valve (32) is arranged on the first through flow path (12), an outlet of the second flow path (8) and an outlet of the first check valve (15) are connected with an inlet of the third expansion valve (31) and an inlet of the fifth stop valve (32) through the ninth connection point (38) and the thirteenth connection point (50), respectively, and an outlet of the third expansion valve (31) and an outlet of the fifth stop valve (32) are connected with an inlet of the outdoor heat exchanger (3) through the fourteenth connection point (51); or,
the refrigerant fluid loop further comprises an expansion switch valve (33), the outlet of the second flow path (8) and the outlet of the first one-way valve (15) are both connected with the inlet of the expansion switch valve (33), the outlet of the expansion switch valve (33) is connected with the inlet of the outdoor heat exchanger (3), the first throttling flow path (11) is a throttling flow path of the expansion switch valve (33), and the first through flow path (12) is a through flow path of the expansion switch valve (33).
12. The vehicle thermal management system according to any one of claims 3 to 5, characterized in that the heat transfer fluid circuit further comprises a second three-way valve (34), wherein a port A of the second three-way valve (34) is connected with an outlet of the first water pump (6), a port B of the second three-way valve (34) is connected with an inlet of the outdoor radiator (7), and a port C of the second three-way valve (34) is respectively connected with the inlet of the indoor warm air core (10) and the heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) through the seventh connection point (46); or,
the heat transfer fluid loop further comprises a first two-way valve (35) and a second two-way valve (36), an outlet of the first water pump (6) is connected with an inlet of the outdoor radiator (7) through a fifteenth connection point (48) and the first two-way valve (35), and an outlet of the first water pump (6) is further connected with an inlet of the indoor warm air core (10) and a heat transfer fluid inlet of the heat transfer fluid-low pressure refrigerant heat exchanger (22) through the fifteenth connection point (48), the second two-way valve (36) and the seventh connection point (46).
13. A vehicle comprising a vehicle thermal management system according to any of claims 1 to 12.
CN202220973600.6U 2022-04-25 2022-04-25 Vehicle thermal management system and vehicle Active CN217294196U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202220973600.6U CN217294196U (en) 2022-04-25 2022-04-25 Vehicle thermal management system and vehicle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202220973600.6U CN217294196U (en) 2022-04-25 2022-04-25 Vehicle thermal management system and vehicle

Publications (1)

Publication Number Publication Date
CN217294196U true CN217294196U (en) 2022-08-26

Family

ID=82915154

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202220973600.6U Active CN217294196U (en) 2022-04-25 2022-04-25 Vehicle thermal management system and vehicle

Country Status (1)

Country Link
CN (1) CN217294196U (en)

Similar Documents

Publication Publication Date Title
US11760162B2 (en) Thermal management system
WO2018161907A1 (en) Thermal management system
US20160059666A1 (en) Air conditioning system and heat exchanger
CN109140815B (en) Thermal management system and flow control device
US20160238290A1 (en) Air conditioner
CN113454407B (en) Device for thermal management of an electric or hybrid motor vehicle
CN113173050B (en) Thermal management system
CN110678340B (en) Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method
CN113173049B (en) Thermal management system
CN112428771B (en) Thermal management system
CN112428769B (en) Thermal management system
US11358438B2 (en) Automotive air conditioning system
CN109386989B (en) Two-pipe jet enthalpy-increasing outdoor unit and multi-split system
EP4049869A1 (en) Vehicle thermal management system, and vehicle
CN217294196U (en) Vehicle thermal management system and vehicle
CN106766332B (en) Air conditioning system unit and air conditioning system
CN112140829B (en) Vehicle thermal management system and vehicle
CN114771199A (en) Vehicle thermal management system, vehicle and operation method of vehicle thermal management system
CN113424000B (en) Thermal management device for an electric or hybrid motor vehicle
CN111854215B (en) heat pump system
WO2021063272A1 (en) Heat management system
CN214215422U (en) Vehicle thermal management system and vehicle
CN219055912U (en) Automobile CO 2 Heat pump air conditioning system and automobile
CN218287372U (en) Heat pump air conditioning system and vehicle
CN210792731U (en) Heat pump air conditioning system and vehicle

Legal Events

Date Code Title Description
GR01 Patent grant
GR01 Patent grant