CN220865168U

CN220865168U - Thermal management system for electric vehicle and vehicle

Info

Publication number: CN220865168U
Application number: CN202322119177.0U
Authority: CN
Inventors: 尤古塔纳·贝努利
Original assignee: Mind Electronics Appliance Co Ltd
Current assignee: Mind Electronics Appliance Co Ltd
Priority date: 2023-08-08
Filing date: 2023-08-08
Publication date: 2024-04-30
Anticipated expiration: 2033-08-08

Abstract

The utility model provides a thermal management system for an electric vehicle and the vehicle. The first heat exchanger, the double-fluid heat exchanger and the fourth heat exchanger can be in countercurrent direction and can be used as an evaporator or a condenser, the refrigerant in the fourth heat exchanger can directly exchange heat with the battery pack, and the refrigerant in the high-pressure side heat exchange channel and the refrigerant in the low-pressure side heat exchange channel in the internal heat exchanger can exchange heat. The heat management system can improve the heat exchange efficiency with the power battery, can realize various working modes, and is beneficial to popularization and application of the heat pump type management system.

Description

Thermal management system for electric vehicle and vehicle

Technical Field

The utility model relates to the technical field, in particular to a thermal management system for an electric vehicle. The utility model also relates to a vehicle provided with the thermal management system for an electric vehicle.

Background

At present, more and more electric vehicle types begin to apply heat pump air conditioning systems, and compared with the traditional PTC heating mode, the power consumption of the heat pump air conditioning systems in heating can be greatly reduced, and the driving mileage of the vehicle can be guaranteed. However, the existing heat pump air conditioning system still has the defects of complex structure, limited working mode and the like, and meanwhile, the existing heat pump air conditioning system also has the problems of low heat exchange efficiency with a power battery and the like, so that popularization and application of the heat pump air conditioning system are limited.

Disclosure of utility model

In view of the above, the present utility model aims to propose a thermal management system for an electric vehicle, so as to be capable of facilitating popularization and application of a heat pump air conditioning system.

In order to achieve the above purpose, the technical scheme of the utility model is realized as follows:

A thermal management system for an electric vehicle, a refrigerant circuit of the thermal management system comprising a compressor, a first heat exchanger, a two-fluid heat exchanger, a second heat exchanger, a third heat exchanger, a stock solution drying device, an internal heat exchanger, a fourth heat exchanger, a first control valve, a fourth control valve, and a first expansion valve;

One end of the first heat exchanger is connected with an outlet of the compressor through a third control valve, and the other end of the first heat exchanger is connected with an inlet of the liquid storage drying device through the double-fluid heat exchanger and a second control valve; one end of the second heat exchanger is connected with the outlet of the compressor through a fifth control valve, and the other end of the second heat exchanger is connected with the inlet of the liquid storage drying device through a sixth control valve;

An inlet of a high-pressure side heat exchange channel in the internal heat exchanger is connected with an outlet of the liquid storage drying device, an outlet of the high-pressure side heat exchange channel in the internal heat exchanger is connected with an inlet of the third heat exchanger through a third expansion valve, an outlet of the third heat exchanger is connected with an inlet of a low-pressure side heat exchange channel in the internal heat exchanger through a ninth control valve, and an outlet of the low-pressure side heat exchange channel in the internal heat exchanger is connected with an inlet of the compressor;

One end of the fourth heat exchanger is connected with the outlet of the compressor through a fourth two-way expansion valve and a second control valve, the other end of the fourth heat exchanger is divided into two paths which are connected in parallel, one path is connected with the outlet of a high-pressure side heat exchange channel in the internal heat exchanger through the second expansion valve, and the other path is connected with the inlet of the liquid storage drying device through an eighth control valve;

One end of the first control valve is connected in parallel between the fourth bidirectional expansion valve and the second control valve, the other end of the first control valve is connected with an inlet of a low-pressure side heat exchange channel in the internal heat exchanger, one end of the fourth control valve is connected in parallel between the third control valve and the first heat exchanger, the other end of the fourth control valve is connected with an inlet of a low-pressure side heat exchange channel in the internal heat exchanger, the inlet of the first expansion valve is connected with an outlet of a high-pressure side heat exchange channel in the internal heat exchanger, and the outlet of the first expansion valve is connected in parallel between the two-fluid heat exchanger and the second control valve;

the first heat exchanger, the two-fluid heat exchanger and the fourth heat exchanger can be in countercurrent, and can be used as an evaporator or a condenser, the refrigerant in the fourth heat exchanger can directly exchange heat with the battery pack, and the refrigerant in the high-pressure side heat exchange channel and the low-pressure side heat exchange channel in the internal heat exchanger can exchange heat.

Further, in the refrigerant circuit, positions of the first heat exchanger and the two-fluid heat exchanger are adjusted, one end of the two-fluid heat exchanger is connected with an outlet of the compressor through the third control valve, the other end of the two-fluid heat exchanger is connected with an inlet of the liquid storage drying device through the first heat exchanger and the second control valve, one end of the fourth control valve is connected between the third control valve and the two-fluid heat exchanger in parallel, and an outlet of the first expansion valve is connected between the first heat exchanger and the second control valve in parallel.

Further, the sixth control valve is eliminated from the refrigerant circuit;

The second heat exchanger is connected in series with the outlet of the compressor, and the fifth control valve is connected in parallel between the outlet of the second heat exchanger and the stock solution drying device.

Further, the first heat exchanger is eliminated from the refrigerant circuit;

The cooling fluid passage in the two-fluid heat exchanger can communicate with at least one of a cooling passage in the drive motor, and a low-temperature radiator.

Further, the thermal management system has a single air conditioning cooling mode;

When the thermal management system is in the single air-conditioning refrigeration mode, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor and then is at high pressure, the high-pressure refrigerant enters the liquid storage drying device through the third control valve, the first heat exchanger, the double-fluid heat exchanger and the second control valve, and the refrigerant transfers the enthalpy value to the outside air at the first heat exchanger and becomes liquid;

Then, the refrigerant passes through the high-pressure side heat exchange channel in the internal heat exchanger, enthalpy is transferred to the low-pressure refrigerant in the low-pressure side heat exchange channel, then the refrigerant passes through the third expansion valve, the high-pressure refrigerant undergoes isenthalpic pressure reduction and passes through a saturation curve to be changed into a low-pressure gas-liquid mixed state, then the low-pressure refrigerant enters the third heat exchanger, the cavity in the air conditioner box is cooled and obtains enthalpy, then the low-pressure refrigerant passes through the fourth control valve to enter the low-pressure side heat exchange channel in the internal heat exchanger, enthalpy is obtained from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, the refrigerant is changed into gas state, and finally the low-pressure refrigerant returns to the compressor.

Further, the thermal management system has a single cell cooling mode;

when the thermal management system is in the single-cell refrigeration mode, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor and then is at high pressure, the high-pressure refrigerant enters the liquid storage drying device through the third control valve, the first heat exchanger, the double-fluid heat exchanger and the second control valve, and the refrigerant transfers the enthalpy value to the outside air at the first heat exchanger and becomes liquid;

Then, the refrigerant passes through the high-pressure side heat exchange channel in the internal heat exchanger, and the enthalpy is transferred to the low-pressure refrigerant in the low-pressure side heat exchange channel, then, the refrigerant passes through the second expansion valve, the high-pressure refrigerant undergoes isenthalpic pressure reduction and changes into a low-pressure gas-liquid mixed state through a saturation curve, then, the low-pressure refrigerant enters the fourth heat exchanger, the battery is cooled and obtains the enthalpy, then, the refrigerant passes through the fourth bidirectional expansion valve and the first control valve and enters the low-pressure side heat exchange channel in the internal heat exchanger, the enthalpy is obtained from the refrigerant in the high-pressure side heat exchange channel and passes through the saturation curve, the refrigerant is changed into a gaseous state, and finally, the low-pressure refrigerant returns to the compressor.

Further, the thermal management system has a dual cooling mode;

When the thermal management system is in the dual-refrigeration mode, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor and then is at high pressure, the high-pressure refrigerant enters the liquid storage drying device through the third control valve, the first heat exchanger, the double-fluid heat exchanger and the second control valve, and the refrigerant transfers the enthalpy value to the outside air at the first heat exchanger and becomes liquid;

Then, the refrigerant passes through a high-pressure side heat exchange channel in the internal heat exchanger, enthalpy is transferred to low-pressure refrigerant in a low-pressure side heat exchange channel, the refrigerant is divided into two paths, one path passes through the third expansion valve and the third heat exchanger, the other path passes through the second expansion valve and the fourth heat exchanger, the high-pressure refrigerant is subjected to isenthalpic pressure reduction at the third expansion valve and the second expansion valve and passes through a saturation curve to be changed into a low-pressure gas-liquid mixed state, and the refrigerant cools an air conditioner inner cavity at the third heat exchanger and obtains enthalpy, and the refrigerant cools a battery at the fourth heat exchanger and obtains enthalpy;

Then, after the refrigerant passing through the fourth control valve merges with the refrigerant passing through the first control valve, the refrigerant enters a low-pressure side heat exchange passage in the internal heat exchanger, obtains enthalpy from the refrigerant in a high-pressure side heat exchange passage and passes through a saturation curve, causes the refrigerant to become gaseous, and finally the low-pressure refrigerant returns to the compressor.

Further, the thermal management system has a heat pump mode;

When the thermal management system is in the heat pump mode, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor and then is at high pressure, the high-pressure refrigerant enters the liquid storage drying device through the fifth control valve, the second heat exchanger and the first control valve, and the air conditioning box air is heated at the second heat exchanger to lose enthalpy;

Then, the refrigerant enters a high-pressure side heat exchange passage in the internal heat exchanger, enthalpy is transferred to a low-pressure refrigerant in a low-pressure side heat exchange passage, then the refrigerant passes through the first expansion valve, the refrigerant undergoes isenthalpic pressure drop and passes through a saturation curve and becomes a low-pressure gas-liquid mixed state, then the refrigerant passes through the two-fluid heat exchanger into the first heat exchanger, absorbs heat from the outside air at the first heat exchanger to obtain enthalpy, then the refrigerant passes through the fourth control valve to enter a low-pressure side heat exchange passage in the internal heat exchanger, the refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange passage and passes through the saturation curve and causes the refrigerant to become gaseous, and finally the low-pressure refrigerant returns to the compressor.

Further, when the thermal management system is in the heat pump mode, the first heat exchanger and the dual fluid heat exchanger can be positioned and the dual fluid heat exchanger can be connected to the fourth control valve, and the first heat exchanger can be connected to the first expansion valve.

Further, the thermal management system has a heat pump + heat recovery mode;

When the thermal management system is in the heat pump and heat recovery mode, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor and then is at high pressure, the high-pressure refrigerant enters the liquid storage drying device through the fifth control valve, the second heat exchanger and the first control valve, and the air conditioning box air is heated at the second heat exchanger to lose enthalpy;

Then, the refrigerant enters a high-pressure side heat exchange channel in the internal heat exchanger, enthalpy is transferred to low-pressure refrigerant in a low-pressure side heat exchange channel, the refrigerant passes through the first expansion valve, the refrigerant undergoes isenthalpic pressure reduction and passes through a saturation curve and becomes a low-pressure gas-liquid mixed state, then the refrigerant enters the first heat exchanger through the double-fluid heat exchanger, heat is absorbed from outside air through the first heat exchanger to obtain enthalpy, and heat of a motor is absorbed at the double-fluid heat exchanger to obtain enthalpy;

Then, the refrigerant enters the low pressure side heat exchange passage in the internal heat exchanger through the fourth control valve, the refrigerant acquires enthalpy from the refrigerant in the high pressure side heat exchange passage and passes through the saturation curve, and causes the refrigerant to become gaseous, and finally the low pressure refrigerant returns to the compressor.

Further, the thermal management system has a heat pump + battery heating mode;

When the thermal management system is in the heat pump and battery heating mode, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor and is at high pressure, and is divided into two paths, wherein one path of high-pressure refrigerant enters the liquid storage drying device through the second control valve, the fourth bidirectional expansion valve, the fourth heat exchanger and the third control valve, and enthalpy is lost when the battery is heated by the fourth heat exchanger; the other path of high-pressure refrigerant enters the liquid storage drying device through the fifth control valve, the second heat exchanger and the first control valve, and heats air of the air conditioning box at the second heat exchanger to lose enthalpy;

Then, the refrigerant flowing out of the liquid storage drying device enters a high-pressure side heat exchange channel in the internal heat exchanger, enthalpy is transferred to low-pressure refrigerant in a low-pressure side heat exchange channel, the refrigerant passes through the first expansion valve, the refrigerant undergoes isenthalpic pressure reduction and passes through a saturation curve and becomes a low-pressure gas-liquid mixed state, then the refrigerant enters the first heat exchanger through the double-fluid heat exchanger, absorbs heat from the external air through the first heat exchanger to obtain enthalpy, and absorbs heat of a motor through the double-fluid heat exchanger to obtain enthalpy;

Further, the fifth control valve adopts a stop valve, the sixth control valve adopts a one-way valve, or the fifth control valve adopts a stop valve, the sixth control valve adopts a two-way expansion valve, or the fifth control valve adopts a two-way expansion valve, and the sixth control valve adopts a one-way valve.

Further, the thermal management system has a first dehumidification mode;

When the thermal management system is in the first dehumidification mode, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor and then is at high pressure, and the high-pressure refrigerant enters the liquid storage drying device through the fifth control valve, the second heat exchanger and the first control valve and heats the gas in the air conditioning box through the second heat exchanger to lose enthalpy;

then, the refrigerant enters a high-pressure side heat exchange channel in the internal heat exchanger, enthalpy is transferred to low-pressure refrigerant in a low-pressure side heat exchange channel, the refrigerant passes through the third expansion valve, the refrigerant undergoes isenthalpic pressure reduction and passes through a saturation curve and becomes a low-pressure gas-liquid mixed state, and then the refrigerant enters the third heat exchanger, and the air inside the air conditioning box is cooled to dehumidify the interior of the vehicle and obtain the enthalpy;

Then, the refrigerant enters the low pressure side heat exchange passage in the internal heat exchanger through the fourth control valve, the refrigerant obtains enthalpy from the refrigerant in the high pressure side heat exchange passage and passes through the saturation curve, and causes the refrigerant to become gaseous, and finally the low pressure refrigerant returns to the compressor.

Further, the thermal management system has a second dehumidification mode;

When the thermal management system is in the second dehumidification mode, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor and then is at high pressure, and the high-pressure refrigerant enters the liquid storage drying device through the fifth control valve, the second heat exchanger and the first control valve and heats the gas in the air conditioning box through the second heat exchanger to lose enthalpy;

Then, the refrigerant enters a high-pressure side heat exchange channel in the internal heat exchanger, enthalpy is transferred to a low-pressure refrigerant in a low-pressure side heat exchange channel, the refrigerant is divided into two paths, one path of refrigerant passes through the third expansion valve, the refrigerant undergoes isenthalpic pressure reduction and passes through a saturation curve and becomes a low-pressure gas-liquid mixed state, then the refrigerant enters the third heat exchanger, and the air inside the air conditioning box is cooled to dehumidify the interior of the vehicle, so that the enthalpy is obtained; the other path of refrigerant passes through the first expansion valve, the refrigerant undergoes isenthalpic pressure drop and passes through a saturation curve and becomes a low-pressure gas-liquid mixed state, then the refrigerant enters the double-fluid heat exchanger and the first heat exchanger, and absorbs heat from the outside air through the first heat exchanger to obtain enthalpy, or absorbs heat of a motor through the double-fluid heat exchanger to obtain enthalpy;

Then, after passing through the fourth control valve and the fourth control valve, the two paths of refrigerant respectively enter the low-pressure side heat exchange channel in the internal heat exchanger, the refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange channel and passes through a saturation curve, the refrigerant is caused to be changed into a gas state, and finally the low-pressure refrigerant returns to the compressor.

Compared with the prior art, the utility model has the following advantages:

The heat management system for the electric vehicle can form a direct and reversible air conditioning system through the arrangement of the compressor, the first heat exchanger, the double-fluid heat exchanger, the second heat exchanger, the third heat exchanger, the liquid storage drying device, the internal heat exchanger and the fourth heat exchanger and the control connection of the plurality of control valves, is simpler in structure, can realize direct cooling and direct heating of batteries, improves the heat exchange efficiency with the batteries, can realize single refrigeration and double refrigeration on the basis of a heat pump mode, and can realize multiple working modes such as heat pump, heat recovery, heat pump, battery heating and dehumidification, and the like, thereby being beneficial to popularization and application of the heat pump type management system.

Another object of the present utility model is to propose a vehicle which is an electric vehicle and in which a thermal management system for electric vehicles as described above is provided.

The vehicle of the present utility model has the same beneficial effects as the above-mentioned thermal management system, and will not be described here again.

Drawings

The accompanying drawings, which are included to provide a further understanding of the utility model and are incorporated in and constitute a part of this specification, illustrate embodiments of the utility model and together with the description serve to explain the utility model. In the drawings:

FIG. 1 is a schematic diagram of a direct reversible air conditioning circuit according to an embodiment of the present utility model;

FIG. 2 is a schematic illustration of a dual fluid heat exchanger and a first heat exchanger in a direct reversible air conditioning circuit according to an embodiment of the present utility model after position adjustment;

FIG. 3 is a schematic diagram of a direct reversible air conditioning circuit with a second heat exchanger adjusted in position according to an embodiment of the present utility model;

FIG. 4 is a schematic illustration of a direct reversible air conditioning circuit according to an embodiment of the present utility model with a first heat exchanger removed;

FIG. 5 is a schematic diagram of a direct reversible air conditioning circuit in a single air conditioning cooling mode according to an embodiment of the present utility model;

Fig. 6 is a schematic diagram showing changes in pressure and enthalpy of a refrigerant in a single air conditioning refrigeration mode according to an embodiment of the present utility model;

FIG. 7 is a schematic diagram of a direct reversible air conditioning circuit in a single-cell cooling mode according to an embodiment of the present utility model;

fig. 8 is a schematic diagram showing changes in pressure and enthalpy of a refrigerant in a single-cell cooling mode according to an embodiment of the present utility model;

FIG. 9 is a schematic diagram of a direct reversible air conditioning circuit in a dual cooling mode according to an embodiment of the present utility model;

FIG. 10 is a schematic diagram showing changes in pressure and enthalpy of a refrigerant in a dual refrigeration mode according to an embodiment of the present utility model;

FIG. 11 is a schematic diagram of a direct reversible air conditioning circuit in a heat pump mode according to an embodiment of the present utility model;

FIG. 12 is a schematic diagram showing changes in pressure and enthalpy of a refrigerant in a heat pump mode according to an embodiment of the present utility model;

FIG. 13 is a schematic diagram of a direct reversible air conditioning circuit in heat pump+heat recovery mode according to an embodiment of the present utility model;

fig. 14 is a schematic diagram showing changes in pressure and enthalpy of a refrigerant in a heat pump+heat recovery mode according to an embodiment of the present utility model;

FIG. 15 is a schematic diagram of a direct reversible air conditioning circuit in a heat pump + battery heating mode according to an embodiment of the present utility model;

FIG. 16 is a graph showing changes in pressure and enthalpy of a refrigerant in a heat pump + battery heating mode according to an embodiment of the present utility model;

FIG. 17 is a schematic diagram of a direct reversible air conditioning circuit in a first dehumidification mode, according to an embodiment of the present disclosure;

FIG. 18 is a schematic diagram showing changes in pressure and enthalpy of a refrigerant in a first dehumidification mode according to an embodiment of the present disclosure;

FIG. 19 is a schematic diagram of a direct reversible air conditioning circuit in a second dehumidification mode, according to an embodiment of the present disclosure;

FIG. 20 is a schematic diagram showing changes in pressure and enthalpy of a refrigerant in a second dehumidification mode according to an embodiment of the present disclosure;

Reference numerals illustrate:

1. A compressor; 2. a first heat exchanger; 3. a two-fluid heat exchanger; 4. a second heat exchanger; 5. a third heat exchanger; 6. a liquid storage drying device; 7. an internal heat exchanger; 8. a fourth heat exchanger; 9. a first control valve; 10. a second control valve; 11. a third control valve; 12. a fourth control valve; 13. a fifth control valve; 14. a first expansion valve; 15. a second expansion valve; 16. a third expansion valve; 17. a fourth bi-directional expansion valve; 18. a sixth control valve; 19. a seventh control valve; 20. an eighth control valve; 21. a ninth control valve;

22-29, a communication point.

Detailed Description

It should be noted that, without conflict, the embodiments of the present utility model and features of the embodiments may be combined with each other.

In the description of the present utility model, it should be noted that, if terms indicating an orientation or positional relationship such as "upper", "lower", "inner", "outer", etc. are presented, they are based on the orientation or positional relationship shown in the drawings, only for convenience of describing the present utility model and simplifying the description, and do not indicate or imply that the apparatus or element to be referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present utility model. Furthermore, the terms "first," "second," and the like, if any, are also used for descriptive purposes only and are not to be construed as indicating or implying relative importance.

In addition, in the description of the present utility model, unless otherwise specifically defined, the mating components may be connected using conventional connection structures in the art. Moreover, the terms "mounted," "connected," and "connected" are to be construed broadly. For example, the connection can be fixed connection, detachable connection or integrated connection; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art in combination with specific cases.

The utility model will be described in detail below with reference to the drawings in connection with embodiments.

Example 1

The present embodiment relates to a thermal management system for an electric vehicle, which, in combination with the one shown in fig. 1, has a refrigerant circuit including a compressor 1, a first heat exchanger 2, a two-fluid heat exchanger 3, a second heat exchanger 4, a third heat exchanger 5, a stock solution drying device 6, an internal heat exchanger 7, a fourth heat exchanger 8, a first control valve 9, a fourth control valve 12, and a first expansion valve 14, as a whole.

Wherein one end of the first heat exchanger 2 is connected with the outlet of the compressor 1 through the third control valve 11, and the other end of the first heat exchanger 2 is connected with the inlet of the stock solution drying device 6 through the two-fluid heat exchanger 3 and the second control valve 19. One end of the second heat exchanger 4 is connected with the outlet of the compressor 1 through a fifth control valve 13, and the other end of the second heat exchanger 4 is connected with the inlet of the stock solution drying device 6 through a sixth control valve 18.

The inlet of the high-pressure side heat exchange channel in the internal heat exchanger 7 is connected with the outlet of the liquid storage drying device 6, and the outlet of the high-pressure side heat exchange channel in the internal heat exchanger 7 is connected with the inlet of the third heat exchanger 5 through the third expansion valve 16. The outlet of the third heat exchanger 5 is connected to the inlet of the low pressure side heat exchange passage in the internal heat exchanger 7 through a ninth control valve 21, and the outlet of the low pressure side heat exchange passage in the internal heat exchanger 7 is connected to the inlet of the compressor 1.

One end of the fourth heat exchanger 8 is connected with the outlet of the compressor 1 through a fourth two-way expansion valve 17 and a second control valve 10, the other end of the fourth heat exchanger 8 is divided into two paths which are connected in parallel, one path is connected with the outlet of a high-pressure side heat exchange channel in the internal heat exchanger 7 through a second expansion valve 15, and the other path is connected with the inlet of the liquid storage drying device 6 through an eighth control valve 20.

One end of the first control valve 9 is connected in parallel between the fourth two-way expansion valve 17 and the second control valve 10, and the other end of the first control valve 9 is connected to the inlet of the low-pressure side heat exchange passage in the interior heat exchanger 7. One end of the fourth control valve 12 is connected in parallel between the third control valve 11 and the first heat exchanger 2, and the other end of the fourth control valve 12 is connected to an inlet of a low-pressure side heat exchange passage in the internal heat exchanger 7. The inlet of the first expansion valve 14 is also connected to the outlet of the high-pressure side heat exchange channel in the internal heat exchanger 7, the outlet of the first expansion valve 14 being connected in parallel between the two-fluid heat exchanger 3 and the second control valve 19.

Still referring to fig. 1, in order to more clearly illustrate the connection between the components in the system, 8 connection points from the connection point 22 to the connection point 29 are also provided in the figure, and the components connected at the connection points are connected to each other, so as to achieve the connection relationship required by the thermal management system of the present embodiment. Of course, in practice, the connection points between the actual components may not be exactly connected to the same point as in fig. 1, but it is undeniable that the connection relationships that they can achieve are still the same as in fig. 1.

Further, based on the above-described integral constitution, in the thermal management system of the present embodiment, specifically, the above-described first heat exchanger 2, two-fluid heat exchanger 3, and fourth heat exchanger 8 are all reversible flow directions, and may be selected as an evaporator or a condenser depending on the flow directions. At the same time, the refrigerant in the fourth heat exchanger 8 is able to exchange heat directly with the battery pack, so that indirect heat exchange by means of the cooling liquid is not necessary. The refrigerant in the high-pressure side heat exchange passage and the low-pressure side heat exchange passage in the internal heat exchanger 7 is able to exchange heat to realize the internal heat exchange function of the internal heat exchanger 7.

The two-fluid heat exchanger 3 of the present embodiment has a refrigerant passage and a cooling liquid passage as a two-fluid heat exchange structure. In which a refrigerant flows in the refrigerant passage, and correspondingly, a coolant flows in the coolant passage, and in the two-fluid heat exchanger 3, the refrigerant in the refrigerant passage and the coolant in the coolant passage can exchange heat, thereby realizing a heat exchanger function.

With the above-described internal heat exchanger 7 of the present embodiment, the internal heat exchanger 7 has a high-pressure side heat exchange passage and a low-pressure side heat exchange passage therein, and it is to be noted that the high-pressure side and the low-pressure side refer to a state in which the refrigerant flowing through the passages is in a high-pressure state or a low-pressure state. Also, in the internal heat exchanger 7, the refrigerant in the high-pressure side heat exchange passage and the low-pressure side heat exchange passage can exchange heat to achieve the heat exchange action of the internal heat exchanger 7.

In particular, the internal heat exchanger 7 in this embodiment may be, for example, an existing coaxial tube.

The above-mentioned gas-liquid separation device 6 in the present embodiment is provided, and it can be understood that it can separate the gaseous refrigerant fluid from the liquid refrigerant fluid, so as to help to improve the heat exchange efficiency of the refrigerant. In practice, the gas-liquid separation device 6 may be a separator product for separating refrigerant gas from liquid.

In the present embodiment, in the specific implementation, it is preferable that the first control valve 9, the second control valve 10, the third control valve 11, the fourth control valve 12, and the fifth control valve 13 may be electrically controlled shut-off valves, and that the sixth control valve 18, the seventh control valve 19, the eighth control valve 20, and the ninth control valve 21 may be check valves. Of course, instead of using a stop valve and a check valve, respectively, the control valves of the present embodiment may have other valve structures that can meet the use requirements.

In specific implementation, the first expansion valve 14, the second expansion valve 15, the third expansion valve 16, and the fourth two-way expansion valve 17 of this embodiment may be all existing expansion valve products. And wherein the first expansion valve 14, the second expansion valve 15 and the third expansion valve 16 may be conventional one-way expansion valves, and as for the fourth two-way expansion valve 17, still referring to fig. 1, it may be specifically configured to be capable of being in a throttled or fully opened state along the direction from the connection point 24 to the fourth heat exchanger 8, and capable of being only in a fully opened state along the direction from the fourth heat exchanger 8 to the connection point 24.

In addition, on the basis of the integral structure of the thermal management system shown in fig. 1, the heat absorption distribution condition during heating of the system is considered, and based on different cost requirements, part of components in the loop can be adjusted during implementation to form an alternative mode matched with corresponding requirements.

Specifically, considering, for example, the case of heat absorption capacity distribution at the time of system heating, as a first alternative, continuing to be shown in fig. 2, in the refrigerant circuit of the present embodiment, the positions of the first heat exchanger 2 and the two-fluid heat exchanger 3 may be adjusted, and thereby one end of the two-fluid heat exchanger 3 is connected to the outlet of the compressor 1 through the third control valve 11, and the other end of the two-fluid heat exchanger 3 is connected to the inlet of the stock solution drying apparatus 6 through the first heat exchanger 2 and the second control valve 19. Meanwhile, one end of the fourth control valve 12 is connected in parallel between the third control valve 11 and the two-fluid heat exchanger 3, and the outlet of the first expansion valve 14 is connected in parallel between the first heat exchanger 2 and the second control valve 19.

In the present embodiment, however, as shown in fig. 3, the sixth control valve 18 may be omitted from the refrigerant circuit of the present embodiment, and the second heat exchanger 4 may be serially connected to the outlet of the compressor 1, and the fifth control valve 13 may be parallelly connected between the outlet of the second heat exchanger 4 and the stock solution drying device 6, based on different cost requirements, based on the first alternative described above.

Of course, in addition to the above second alternative, in the present embodiment, as still based on the above first alternative, the first heat exchanger 2 may be omitted in the refrigerant circuit as well, and at this time, in the specific implementation, the cooling liquid passage in the two-fluid heat exchanger 3 may be communicated with the cooling passage in the drive motor and the low-temperature radiator, or the cooling liquid passage in the two-fluid heat exchanger 3 may also be communicated with one of the cooling passage in the drive motor and the low-temperature radiator.

In this embodiment, based on the above description, taking the configuration of the indirect reversible air conditioning system shown in fig. 1 as an example, the operation mode of the indirect reversible air conditioning system according to this embodiment will be specifically described below by controlling the control valves.

1. Single air conditioner refrigerating mode

In conjunction with the illustration in fig. 5, the thermal management system of the present embodiment has a single air conditioning refrigeration mode, and the refrigerant circuit is mainly composed of the compressor 1, the third control valve 11, the first heat exchanger 2, the two-fluid heat exchanger 3, the seventh control valve 19, the stock solution drying device 6, the internal heat exchanger 7, the third expansion valve 16, the third heat exchanger 5, and the ninth control valve 21 when the thermal management system is in the single air conditioning refrigeration mode.

In specific operation, the gaseous refrigerant is compressed by the compressor 1 and then is at high pressure, the high-pressure refrigerant enters the liquid storage drying device 6 through the third control valve 11, the first heat exchanger 2, the double-fluid heat exchanger 3 and the second control valve 19, and the refrigerant transfers the enthalpy value to the outside air at the first heat exchanger 2 and becomes liquid.

Then, the refrigerant passes through the high-pressure side heat exchange passage in the internal heat exchanger 7, and the enthalpy is transferred to the low-pressure refrigerant in the low-pressure side heat exchange passage, and then, the refrigerant passes through the third expansion valve 16, and the high-pressure refrigerant undergoes an isenthalpic pressure drop, and changes to a low-pressure gas-liquid mixture state through a saturation curve. Then, the low-pressure refrigerant enters the third heat exchanger 5 to cool the air-conditioning tank inner cavity and obtain enthalpy, then, the low-pressure refrigerant passes through the fourth control valve 21 to enter the low-pressure side heat exchange passage in the inner heat exchanger 7, and obtains enthalpy from the refrigerant in the high-pressure side heat exchange passage and passes through the saturation curve, causing the refrigerant to become gaseous, and finally, the low-pressure refrigerant returns to the compressor 1.

Fig. 6 shows the changes in pressure and enthalpy experienced by a refrigerant in a single air conditioning refrigeration mode, and wherein curve X represents refrigerant fluid saturation.

Specifically, the refrigerant fluid entering the compressor 1 is in the vapor phase, and as the refrigerant fluid passes through the compressor 1, the refrigerant fluid undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at a high pressure. The refrigerant fluid at high pressure then enters the first heat exchanger 2 and transfers the enthalpy value into the external air stream, as indicated by arrow 600. The refrigerant flowing out of the first heat exchanger 2 is in a pure liquid state, and the refrigerant fluid then enters the internal heat exchanger 7 where it loses enthalpy, as indicated by arrow 10a, which is transferred to the low pressure refrigerant fluid, as indicated by arrow 10 b.

The high pressure refrigerant then passes through the third expansion valve 16, and the high pressure refrigerant fluid undergoes an isenthalpic pressure drop indicated by arrow 110 and passes through the saturation curve X, which causes it to switch to a mixture of gas and liquid state and at a low pressure. The low pressure refrigerant fluid then passes through the third heat exchanger 5 and obtains enthalpy there, as indicated by arrow 150, and then the low pressure refrigerant fluid passes through the inner heat exchanger 7 and obtains enthalpy there from the high pressure refrigerant fluid passing through the inner heat exchanger 7 as indicated by arrow 10b and passes through the saturation curve X, which causes it to switch to a gaseous state, and the low pressure refrigerant fluid is then returned to the compressor 1.

2. Single cell cooling mode

As shown in fig. 7, the thermal management system of the present embodiment has a single-cell cooling mode, and when the thermal management system is in the single-cell cooling mode, the refrigerant circuit is mainly composed of the compressor 1, the third refrigerant shut-off valve 11, the first heat exchanger 2, the two-fluid heat exchanger 3, the second refrigerant check valve 19, the stock solution drying device 6, the internal heat exchanger 7, the second expansion valve 15, the fourth heat exchanger 8, the fourth two-way expansion device 17, and the first refrigerant shut-off valve 9.

In specific operation, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and then is at high pressure, the high-pressure refrigerant enters the liquid storage and drying device 6 through the third control valve 11, the first heat exchanger 2, the two-fluid heat exchanger 3 and the second control valve 19, and the refrigerant transfers the enthalpy value to the outside air at the first heat exchanger 2 and becomes liquid.

The refrigerant then passes through the high-pressure side heat exchange channels in the internal heat exchanger 7 and transfers enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange channels. Next, the refrigerant passes through the second expansion valve 15, and the high-pressure refrigerant undergoes an isenthalpic pressure drop, and passes through a saturation curve to become a low-pressure gas-liquid mixed state. The low pressure refrigerant then enters the fourth heat exchanger 8, cooling the battery and obtaining enthalpy. The refrigerant then passes through the fourth two-way expansion valve 17, the first control valve 9, and enters the low-pressure side heat exchange passage in the internal heat exchanger 7, and obtains enthalpy from the refrigerant in the high-pressure side heat exchange passage and passes through the saturation curve, causing the refrigerant to change to a gaseous state, and finally the low-pressure refrigerant returns to the compressor 1.

Fig. 8 shows the changes in pressure and enthalpy experienced by a refrigerant in a single cell cooling mode, and wherein curve X represents the refrigerant fluid saturation.

The high pressure refrigerant then passes through the second expansion valve 15, and the high pressure refrigerant fluid undergoes an isenthalpic pressure drop indicated by arrow 110 and passes through the saturation curve X, which causes it to switch to a mixture of gas and liquid state and at a low pressure. Then, the low-pressure refrigerant fluid passes through the fourth heat exchanger 8 and obtains enthalpy therein as indicated by an arrow 150, and then the low-pressure refrigerant fluid passes through the internal heat exchanger 7 and obtains enthalpy therein as indicated by an arrow 10b from the high-pressure refrigerant fluid passing through the internal heat exchanger 7 and passes through the saturation curve X, which causes it to be switched to a gaseous state, and then the low-pressure refrigerant fluid returns to the compressor 1.

3. A dual cooling mode;

As shown in fig. 9, the thermal management system of the present embodiment has a dual cooling mode, and when the thermal management system is in the dual cooling mode, the refrigerant circuit is mainly composed of the compressor 1, the third refrigerant shut-off valve 11, the first heat exchanger 2, the two-fluid heat exchanger 3, the second refrigerant check valve 19, the stock solution drying device 6, the internal heat exchanger 7, the second expansion valve 15, the fourth heat exchanger 8, the fourth two-way expansion device 17, the first refrigerant shut-off valve 9, the third expansion valve 16, the third heat exchanger 5, and the fourth refrigerant check valve 21.

The refrigerant then passes through the high-pressure side heat exchange passage in the internal heat exchanger 7, transfers enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange passage, and the refrigerant is split into two paths. One path passes through the third expansion valve 16 and the third heat exchanger 5, the other path passes through the second expansion valve 15 and the fourth heat exchanger 8, the high-pressure refrigerant undergoes isenthalpic pressure drop at the third expansion valve 16 and the second expansion valve 15 and changes into a low-pressure gas-liquid mixed state through a saturation curve, the refrigerant cools the air conditioning tank cavity and obtains enthalpy at the third heat exchanger 5, and the refrigerant cools the battery and obtains enthalpy at the fourth heat exchanger 8.

Then, after the refrigerant passing through the fourth control valve 21 merges with the refrigerant passing through the first control valve 9, it enters the low pressure side heat exchange passage in the internal heat exchanger 7, and obtains enthalpy from the refrigerant in the high pressure side heat exchange passage and passes through the saturation curve, causing the refrigerant to become gaseous, and finally the low pressure refrigerant returns to the compressor 1.

Fig. 10 shows the pressure and enthalpy changes experienced by a refrigerant in a dual refrigeration mode, and wherein curve X represents refrigerant fluid saturation.

Then, the high-pressure refrigerant is divided into 2 branches, and passes through the third expansion valve 16 and the second expansion valve 15, respectively, and the high-pressure refrigerant fluid undergoes isenthalpic pressure drop indicated by an arrow 120 and passes through a saturation curve X, which causes it to switch to a mixture state of gas and liquid, and is at a low pressure. The low pressure refrigerant fluid then passes through the third heat exchanger 5 and the fourth heat exchanger 8, respectively, where enthalpy is obtained, as indicated by arrows 160 and 180, respectively, while cooling the internal air stream.

The low-pressure refrigerant fluid then passes through the internal heat exchanger 7, where enthalpy is obtained from the high-pressure refrigerant fluid passing through the internal heat exchanger 7 as indicated by arrow 10b and passes through the saturation curve X, which causes it to switch to the gaseous state, and the low-pressure refrigerant fluid is then returned to the compressor 1.

4. A heat pump mode;

As shown in fig. 11, the thermal management system of the present embodiment has a heat pump mode, and when the thermal management system is in the heat pump mode, the refrigerant circuit is mainly composed of the compressor 1, the fifth refrigerant shut-off valve 13, the second heat exchanger 4, the first refrigerant check valve 18, the stock solution drying device 6, the internal heat exchanger 7, the first expansion valve 14, the two-fluid heat exchanger 3, the first heat exchanger 2, and the fourth refrigerant shut-off valve 12.

In specific operation, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and then is at high pressure, the high-pressure refrigerant enters the liquid storage drying device 6 through the fifth control valve 13, the second heat exchanger 4 and the first control valve 18, and the air conditioning box air is heated at the second heat exchanger 4 to lose enthalpy.

Then, the refrigerant enters the high-pressure side heat exchange passage in the internal heat exchanger 7, transfers enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange passage, and then the refrigerant passes through the first expansion valve 14, undergoes isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixed state. Then, the refrigerant enters the first heat exchanger 2 through the two-fluid heat exchanger 3, absorbs heat from the outside air at the first heat exchanger 2 to obtain enthalpy, then enters the low-pressure side heat exchange passage in the internal heat exchanger 7 through the fourth control valve 12, obtains enthalpy from the refrigerant in the high-pressure side heat exchange passage and passes through the saturation curve, and causes the refrigerant to become gaseous, and finally the low-pressure refrigerant returns to the compressor 1.

Fig. 12 shows the changes in pressure and enthalpy experienced by the refrigerant in the heat pump mode, and wherein curve X represents the refrigerant fluid saturation.

Specifically, the refrigerant fluid entering the compressor 1 is in the vapor phase, and as the refrigerant fluid passes through the compressor 1, the refrigerant fluid undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at a high pressure. The refrigerant fluid at high pressure then enters the second heat exchanger 4, then enters the internal heat exchanger 7 and transfers the enthalpy value to the heat transfer fluid in the internal heat exchanger 7 as indicated by arrow 200, at which time the refrigerant fluid loses enthalpy while maintaining a constant pressure, the refrigerant fluid being in a liquid phase, high pressure state as indicated by arrow 4 a.

The refrigerant fluid then passes through the first expansion valve 14, and undergoes an isenthalpic pressure drop, indicated by arrow 500, which results in a mixture of gas and liquid, and passes through the saturation curve X, while the refrigerant fluid is still a mixture of gas and liquid, at a low pressure. The low pressure refrigerant then passes through the two-fluid heat exchanger 3, the first heat exchanger 2, to gain enthalpy by absorbing heat from the flow of air outside the flow, while the refrigerant is in a two-phase state, as indicated by arrow 600, then passes through the internal heat exchanger 7, as indicated by arrow 4b, and finally returns to the compressor 1.

5. A heat pump + heat recovery mode;

As shown in fig. 13, the thermal management system of the present embodiment has a heat pump+heat recovery mode, and the refrigerant circuit is mainly composed of the compressor 1, the fifth refrigerant shut-off valve 13, the second heat exchanger 4, the first refrigerant check valve 18, the stock solution drying device 6, the internal heat exchanger 7, the first expansion valve 14, the two-fluid heat exchanger 3, the first heat exchanger 2, and the fourth refrigerant shut-off valve 12 when the thermal management system is in the heat pump+heat recovery mode.

Then, the refrigerant enters the high-pressure side heat exchange passage in the internal heat exchanger 7, transfers the enthalpy to the low-pressure refrigerant in the low-pressure side heat exchange passage, and then passes through the first expansion valve 14, the refrigerant undergoes isenthalpic pressure drop and passes through the saturation curve and becomes a low-pressure gas-liquid mixed state, and then enters the first heat exchanger 2 through the two-fluid heat exchanger 3, absorbs heat from the outside air through the first heat exchanger 2 to obtain the enthalpy, and absorbs heat of the motor at the two-fluid heat exchanger 3 to obtain the enthalpy.

Then, the refrigerant enters the low-pressure side heat exchange passage in the internal heat exchanger 7 through the fourth control valve 12, the refrigerant acquires enthalpy from the refrigerant in the high-pressure side heat exchange passage and passes through the saturation curve, and causes the refrigerant to become gaseous, and finally the low-pressure refrigerant returns to the compressor 1.

Fig. 14 shows the changes in pressure and enthalpy experienced by the refrigerant in the heat pump + heat recovery mode, and wherein curve X represents the refrigerant fluid saturation.

Specifically, the refrigerant fluid entering the compressor 1 is in the vapor phase, and as the refrigerant fluid passes through the compressor 1, the refrigerant fluid undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at a high pressure. The refrigerant fluid at high pressure then enters the second heat exchanger 4, then enters the internal heat exchanger 7 and transfers the enthalpy value to the heat transfer fluid in the internal heat exchanger 7 as indicated by arrow 200, at which time the refrigerant fluid loses enthalpy while maintaining a constant pressure, the refrigerant fluid being in a liquid phase, high pressure state as indicated by arrow 10 a.

The refrigerant fluid then passes through the first expansion valve 14, and undergoes an isenthalpic pressure drop, indicated by arrow 110, which results in a mixture of gas and liquid, and passes through the saturation curve X, while the refrigerant fluid is still a mixture of gas and liquid, at a low pressure. The low pressure refrigerant then passes through the two-fluid heat exchanger 3 and the first heat exchanger 2 to gain enthalpy by absorbing heat from the flow of air outside the flow and from the drive motor, with the refrigerant in a two-phase state, as indicated by arrow 150. The refrigerant then passes through the internal heat exchanger 7 as indicated by arrow 10b and finally back to the compressor 1.

6. A heat pump + battery heating mode;

As shown in fig. 15, the thermal management system of the present embodiment has a heat pump+battery heating mode, and the refrigerant circuit is mainly composed of the compressor 1, the fifth refrigerant shut-off valve 13, the second heat exchanger 4, the first refrigerant check valve 18, the second refrigerant shut-off valve 10, the fourth bi-directional expansion device 17, the fourth heat exchanger 8, the third refrigerant check valve 20, the stock solution drying device 6, the internal heat exchanger 7, the first expansion valve 14, the two-fluid heat exchanger 3, the first heat exchanger 2, and the fourth refrigerant shut-off valve 12 when the thermal management system is in the heat pump+battery heating mode.

In the specific working process, in the refrigerant loop, the gaseous refrigerant is compressed by the compressor 1 and is at high pressure, and is divided into two paths, wherein one path of high-pressure refrigerant enters the liquid storage drying device 6 through the second control valve 10, the fourth bidirectional expansion valve 17, the fourth heat exchanger 8 and the third control valve 20, and the enthalpy of the battery is lost by heating through the fourth heat exchanger 8; the other high-pressure refrigerant enters the liquid storage drying device 6 through the fifth control valve 13, the second heat exchanger 4 and the first control valve 18, and heats the air of the air conditioning box at the second heat exchanger 4 to lose enthalpy.

Then, the refrigerant flowing out of the stock solution drying device 6 enters the high-pressure side heat exchange channel in the internal heat exchanger 7, enthalpy is transferred to the low-pressure refrigerant in the low-pressure side heat exchange channel, the refrigerant then passes through the first expansion valve 14, the refrigerant undergoes isenthalpic pressure drop and passes through a saturation curve and becomes a low-pressure gas-liquid mixed state, then the refrigerant enters the first heat exchanger 2 through the two-fluid heat exchanger 3, heat is absorbed from the outside air through the first heat exchanger 2, enthalpy is obtained, and heat of the motor is absorbed through the two-fluid heat exchanger 3.

Fig. 16 shows the changes in pressure and enthalpy experienced by the refrigerant in the heat pump + battery heating mode, and wherein curve X represents the refrigerant fluid saturation state.

Specifically, the refrigerant fluid entering the compressor 1 is in the vapor phase, and as the refrigerant fluid passes through the compressor 1, the refrigerant fluid undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at a high pressure. The refrigerant fluid at high pressure then enters the second heat exchanger 4 and the fourth heat exchanger 8 and transfers the enthalpy value to the heat transfer fluid in the internal heat exchanger 7 as indicated by arrows 200 and 300, at which time the refrigerant fluid loses enthalpy while maintaining a constant pressure, the refrigerant fluid being in a liquid phase, high pressure state as indicated by arrow 10 a.

Furthermore, it should be noted that, when the thermal management system of the present embodiment can implement the heat pump+battery heating mode, the fifth control valve 13 is made to use a shut-off valve and the sixth control valve 18 is made to use a check valve, except as mentioned above. In specific implementation, the fifth control valve 13 may be a stop valve, the sixth control valve 18 may be a bidirectional expansion valve, or the fifth control valve 13 may be a bidirectional expansion valve, and the sixth control valve 18 may be a one-way valve.

7. A first dehumidification mode;

As shown in fig. 17, the thermal management system of the present embodiment has a first dehumidification mode, and when the thermal management system is in the first dehumidification mode, the refrigerant circuit is mainly composed of the compressor 1, the fifth refrigerant shut-off valve 13, the second heat exchanger 4, the first refrigerant check valve 18, the stock solution drying device 6, the internal heat exchanger 7, the third expansion valve 16, the third heat exchanger 5, and the fourth refrigerant check valve 21.

In specific operation, in the refrigerant circuit, the gaseous refrigerant is compressed by the compressor 1 and then is at high pressure, the high-pressure refrigerant enters the liquid storage drying device 6 through the fifth control valve 13, the second heat exchanger 4 and the first control valve 18, and the gas in the air conditioning box is heated by the second heat exchanger 4 to lose enthalpy.

Then, the refrigerant enters the high-pressure side heat exchange passage in the internal heat exchanger 7, the enthalpy is transferred to the low-pressure refrigerant in the low-pressure side heat exchange passage, and then the refrigerant passes through the third expansion valve 16, undergoes isenthalpic pressure drop and passes through the saturation curve, and becomes a low-pressure gas-liquid mixed state, and then the refrigerant enters the third heat exchanger 5, cools the air-conditioning box interior gas, dehumidifies the interior of the vehicle, and obtains the enthalpy.

Then, the refrigerant enters the low-pressure side heat exchange passage in the internal heat exchanger 7 through the fourth control valve 21, the refrigerant acquires enthalpy from the refrigerant in the high-pressure side heat exchange passage and passes through the saturation curve, and causes the refrigerant to become gaseous, and finally the low-pressure refrigerant returns to the compressor 1.

Fig. 18 shows the changes in pressure and enthalpy experienced by the refrigerant in the first dehumidification mode, and wherein curve X represents the refrigerant fluid saturation state.

Specifically, the refrigerant fluid entering the compressor 1 is in the vapor phase, and as the refrigerant fluid passes through the compressor 1, the refrigerant fluid undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at a high pressure. The refrigerant fluid at high pressure then enters the second heat exchanger 4 and will pass into the cabin as indicated by arrow 200, at which time the refrigerant fluid loses enthalpy while maintaining a constant pressure, the reduced enthalpy refrigerant fluid enters the receiver drier 6, the refrigerant fluid exiting the receiver drier 6 is in the liquid phase, and the refrigerant fluid enters the internal heat exchanger 7 and loses enthalpy there, as indicated by arrow 10a, which is transferred to the low pressure refrigerant fluid as indicated by arrow 10 b.

The high pressure refrigerant then passes through the third expansion valve 16, the high pressure refrigerant fluid undergoes an isenthalpic pressure drop indicated by arrow 120 and passes through the saturation curve X, which causes it to switch to a mixture of gas and liquid state, now at low pressure. The low pressure refrigerant fluid then passes through the third heat exchanger 5 where it acquires enthalpy as indicated by arrow 160 while cooling the internal air stream. The low pressure refrigerant fluid then passes through the internal heat exchanger 7, where it acquires enthalpy as indicated by arrow 10b from the high pressure refrigerant fluid passing through the internal heat exchanger 7 and passes through the saturation curve X, which causes it to switch to the gaseous state, and the low pressure refrigerant fluid then returns to the compressor 1.

8. A second dehumidification mode;

As shown in fig. 19, the thermal management system of the present embodiment has a second dehumidification mode, and the refrigerant circuit is mainly composed of the compressor 1, the fifth refrigerant shut-off valve 13, the second heat exchanger 4, the first refrigerant check valve 18, the reservoir drying device 6, the internal heat exchanger 7, the third expansion valve 16, the third heat exchanger 5, the fourth refrigerant check valve 21, the first expansion valve 14, the two-fluid heat exchanger 3, the first heat exchanger 2, and the fourth refrigerant shut-off valve 12 when the thermal management system is in the heat pump+battery heating mode.

Then, the refrigerant enters a high-pressure side heat exchange channel in the internal heat exchanger 7, enthalpy is transferred to a low-pressure refrigerant in a low-pressure side heat exchange channel, the refrigerant is divided into two paths, one path of refrigerant passes through the third expansion valve 16, the refrigerant undergoes isenthalpic pressure reduction and passes through a saturation curve and becomes a low-pressure gas-liquid mixed state, and then the refrigerant enters the third heat exchanger 5, and the air inside the air conditioning box is cooled to dehumidify the interior of the vehicle and obtain enthalpy; the other path of refrigerant passes through the first expansion valve 14, undergoes isenthalpic pressure drop and passes through a saturation curve, and becomes a low-pressure gas-liquid mixed state, and then enters the two-fluid heat exchanger 3 and the first heat exchanger 2, absorbs heat from the outside air through the first heat exchanger 2 to obtain enthalpy, or absorbs heat of the motor through the two-fluid heat exchanger 3 to obtain enthalpy.

Then, after passing through the fourth control valve 21 and the fourth control valve 12, respectively, the two-way refrigerant enters the low-pressure side heat exchange passage in the internal heat exchanger 7, the refrigerant obtains enthalpy from the refrigerant in the high-pressure side heat exchange passage and passes through the saturation curve, and causes the refrigerant to become gaseous, and finally the low-pressure refrigerant returns to the compressor 1.

Fig. 20 shows the changes in pressure and enthalpy experienced by the refrigerant in the first dehumidification mode, and wherein curve X represents the refrigerant fluid saturation state.

Specifically, the refrigerant fluid entering the compressor 1 is in the vapor phase, and as the refrigerant fluid passes through the compressor 1, the refrigerant fluid undergoes compression, as indicated by arrow 100, at which point the refrigerant fluid is at a high pressure. The refrigerant fluid at high pressure then enters the second heat exchanger 4 and will pass into the cabin as indicated by arrow 200, where it loses enthalpy while maintaining a constant pressure, and the reduced enthalpy refrigerant fluid enters the receiver drier 6 as indicated by arrow 4 a.

The refrigerant then splits into 2 branches, the first refrigerant branch passing through the third expansion valve 16, the refrigerant fluid undergoing an isenthalpic pressure drop, indicated by arrow 500, which results in a mixture of gas and liquid and passing through the saturation curve X, while the refrigerant fluid is still a mixture of gas and liquid at a low pressure. The low pressure refrigerant then absorbs cabin heat through the third heat exchanger 5 to gain enthalpy, where it is in a two-phase state, as indicated by arrow 600, and then passes through the internal heat exchanger 7, as indicated by arrow 4 b.

The second refrigerant leg fluid passes through the first expansion valve 14 and undergoes an isenthalpic pressure drop, indicated by arrow 120, which results in a mixture of gas and liquid and passes through the saturation curve X, while the refrigerant fluid is still a mixture of gas and liquid at a low pressure. The low pressure refrigerant then passes through the two-fluid heat exchanger 3, the first heat exchanger 2 and absorbs heat from the outside air of the first heat exchanger 2 or the heat from the drive motor through the two-fluid heat exchanger 3 to obtain enthalpy, where the refrigerant is in a two-phase state as indicated by arrow 160, and then enters the internal heat exchanger 7 to obtain enthalpy, where the refrigerant fluid is in a gas phase as indicated by arrow 10 b.

The last two refrigerant branches merge back into the compressor 1 at the connection point 29.

The thermal management system for an electric vehicle of the present embodiment, with the above configuration, can form a direct and reversible air conditioning system by the arrangement of the compressor 1, the first heat exchanger 2, the two-fluid heat exchanger 3, the second heat exchanger 4, the third heat exchanger 5, the stock solution drying device 6, the internal heat exchanger 7, and the fourth heat exchanger 8, and by the control connection of the plurality of control valves.

At this time, the thermal management system of the embodiment is simpler in structure constitution, can realize direct cooling and direct heating of the battery, improves heat exchange efficiency with the power battery, and can realize single refrigeration and double refrigeration and multiple working modes such as heat pump, heat recovery, heat pump, battery heating and dehumidification on the basis of a heat pump mode, thereby being beneficial to popularization and application of the heat pump type management system.

Example two

The present embodiment relates to a vehicle that is an electric vehicle, and in which the thermal management system for an electric vehicle of the first embodiment is provided.

The vehicle of the embodiment is provided with the thermal management system of the first embodiment, so that the heat exchange efficiency with the power battery can be improved, and various working modes such as heat pump, single refrigeration, double refrigeration, heat pump+heat recovery, heat pump+battery heating and dehumidification can be realized, thereby being beneficial to improving the thermal management effect of the vehicle and the driving quality of the vehicle.

The foregoing description of the preferred embodiments of the utility model is not intended to be limiting, but rather is intended to cover all modifications, equivalents, alternatives, and improvements that fall within the spirit and scope of the utility model.

Claims

1. A thermal management system for an electric vehicle, characterized by:

The refrigerant loop of the thermal management system comprises a compressor (1), a first heat exchanger (2), a two-fluid heat exchanger (3), a second heat exchanger (4), a third heat exchanger (5), a stock solution drying device (6), an internal heat exchanger (7), a fourth heat exchanger (8), a first control valve (9), a fourth control valve (12) and a first expansion valve (14);

One end of the first heat exchanger (2) is connected with an outlet of the compressor (1) through a third control valve (11), and the other end of the first heat exchanger (2) is connected with an inlet of the liquid storage drying device (6) through the double-fluid heat exchanger (3) and a second control valve (19); one end of the second heat exchanger (4) is connected with an outlet of the compressor (1) through a fifth control valve (13), and the other end of the second heat exchanger (4) is connected with an inlet of the liquid storage drying device (6) through a sixth control valve (18);

An inlet of a high-pressure side heat exchange channel in the internal heat exchanger (7) is connected with an outlet of the liquid storage drying device (6), an outlet of the high-pressure side heat exchange channel in the internal heat exchanger (7) is connected with an inlet of the third heat exchanger (5) through a third expansion valve (16), an outlet of the third heat exchanger (5) is connected with an inlet of a low-pressure side heat exchange channel in the internal heat exchanger (7) through a ninth control valve (21), and an outlet of the low-pressure side heat exchange channel in the internal heat exchanger (7) is connected with an inlet of the compressor (1);

One end of the fourth heat exchanger (8) is connected with the outlet of the compressor (1) through a fourth two-way expansion valve (17) and a second control valve (10), the other end of the fourth heat exchanger (8) is divided into two paths which are connected in parallel, one path is connected with the outlet of a high-pressure side heat exchange channel in the internal heat exchanger (7) through a second expansion valve (15), and the other path is connected with the inlet of the liquid storage drying device (6) through an eighth control valve (20);

One end of the first control valve (9) is connected in parallel between the fourth bidirectional expansion valve (17) and the second control valve (10), the other end of the first control valve (9) is connected to an inlet of a low-pressure side heat exchange channel in the internal heat exchanger (7), one end of the fourth control valve (12) is connected in parallel between the third control valve (11) and the first heat exchanger (2), the other end of the fourth control valve (12) is connected to an inlet of a low-pressure side heat exchange channel in the internal heat exchanger (7), an inlet of the first expansion valve (14) is connected to an outlet of a high-pressure side heat exchange channel in the internal heat exchanger (7), and an outlet of the first expansion valve (14) is connected in parallel between the dual-fluid heat exchanger (3) and the second control valve (19);

The first heat exchanger (2), the double-fluid heat exchanger (3) and the fourth heat exchanger (8) are all reversible flow directions and can be selected as an evaporator or a condenser, the refrigerant in the fourth heat exchanger (8) can directly exchange heat with a battery pack, and the refrigerant in a high-pressure side heat exchange channel and a low-pressure side heat exchange channel in the internal heat exchanger (7) can exchange heat.

2. The thermal management system for an electric vehicle of claim 1, wherein:

In the refrigerant loop, the positions of the first heat exchanger (2) and the double-fluid heat exchanger (3) are adjusted, one end of the double-fluid heat exchanger (3) is connected with the outlet of the compressor (1) through the third control valve (11), the other end of the double-fluid heat exchanger (3) is connected with the inlet of the liquid storage drying device (6) through the first heat exchanger (2) and the second control valve (19), one end of the fourth control valve (12) is connected between the third control valve (11) and the double-fluid heat exchanger (3) in parallel, and the outlet of the first expansion valve (14) is connected between the first heat exchanger (2) and the second control valve (19) in parallel.

3. The thermal management system for an electric vehicle of claim 2, wherein:

-removing said sixth control valve (18) from said refrigerant circuit;

The second heat exchanger (4) is connected in series with the outlet of the compressor (1), and the fifth control valve (13) is connected in parallel between the outlet of the second heat exchanger (4) and the stock solution drying device (6).

4. The thermal management system for an electric vehicle of claim 2, wherein:

-removing said first heat exchanger (2) from said refrigerant circuit;

The cooling fluid channel in the two-fluid heat exchanger (3) can be in communication with at least one of a cooling channel in the drive motor and a low temperature radiator.

5. The thermal management system for an electric vehicle of claim 1, wherein:

The fifth control valve (13) adopts a stop valve, and the sixth control valve (18) adopts a one-way valve; or the fifth control valve (13) adopts a stop valve, and the sixth control valve (18) adopts a two-way expansion valve; or the fifth control valve (13) adopts a two-way expansion valve, and the sixth control valve (18) adopts a one-way valve.

6. A vehicle, characterized in that:

The vehicle is an electric vehicle, and the vehicle is provided therein with the thermal management system for an electric vehicle according to any one of claims 1 to 5.