EP3982059B1

EP3982059B1 - Heat management system

Info

Publication number: EP3982059B1
Application number: EP20871421.2A
Authority: EP
Inventors: Junqi DONG; Shiwei JIA; Yibiao WANG
Original assignee: Hangzhou Sanhua Research Institute Co Ltd
Current assignee: Hangzhou Sanhua Research Institute Co Ltd
Priority date: 2019-09-30
Filing date: 2020-09-25
Publication date: 2024-05-15
Anticipated expiration: 2040-09-25
Also published as: CN112577213A; EP3982059A1; US20220243961A1; EP3982059A4; WO2021063272A1

Description

TECHNICAL FIELD

The present invention relates to a field of air conditioning, and in particular to a thermal management system.

BACKGROUND

A thermal management system can realize cooling, heating, ventilation and air purification of indoor air, and provide a comfortable environment for indoor personnel. How to optimize the thermal management system to improve the performance thereof is a current focus.
In the related thermal management system, in a cooling mode, a high-temperature and high-pressure refrigerant flows out of an outlet of the compressor and directly enters an outdoor heat exchanger. The temperature of the refrigerant flowing out of the outlet of the compressor is relatively high. When the outdoor environment temperature is high, after the refrigerant exchanges heat with the external environment in the outdoor heat exchanger, the temperature of the refrigerant flowing out of the outdoor heat exchanger is still high, which results in poor cooling effect of the thermal management system.
US 2004/0134217 A1 discloses an air conditioning system. When a dehumidifying and heating operation is set in an air conditioner, refrigerant is circulated from a compressor to the compressor through a first exterior heat exchanger, a decompression device, an interior heat exchanger, an another decompression device, an inner heat exchanger and a second exterior heat exchanger, in this order. Further, by controlling a throttle opening degree of the another decompression device, a refrigerant temperature in the interior heat exchanger can be set higher than that in the second exterior heat exchanger. Thus, even when the interior heat exchanger is controlled to a temperature to be not frosted, heat can be absorbed from outside air in the second exterior heat exchanger. Accordingly, when an outside air temperature is low, by setting the dehumidifying and heating operation, air to be blown into a compartment can be dehumidified while sufficiently increasing heating capacity.
US 2002/007943 A1 discloses a heat pump. In a heat pump cycle, a first high-pressure side heat exchanger is disposed to perform a heat exchange between refrigerant discharged from a compressor and a first fluid, and a second high-pressure side heat exchanger is disposed to perform a heat exchanger between refrigerant from the first high-pressure side heat exchanger and a second fluid having a temperature lower than that of the first fluid. Accordingly, a heat quantity obtained from the heat pump cycle is the sum of a heat amount obtained from the first high-pressure side heat exchanger and a heat amount obtained from the second high-pressure side heat exchanger.
US 2014/069123 A1 discloses a heat pump system for a vehicle. The heat pump system may include a cooling apparatus that supplies and circulates coolant to a motor and an electrical equipment through a cooling line, wherein the cooling apparatus includes a radiator, a cooling fan that ventilates wind to the radiator, and a water pump connected to the cooling line, and an air conditioner apparatus connected through a refrigerant line, wherein the air conditioner apparatus includes a water-cooled condenser connected to the cooling line to change a temperature of the coolant using a waste heat that has occurred in the motor and the electrical equipment according to each mode of the vehicle and that is connected to the refrigerant line to enable an injected refrigerant in the refrigerant line to exchange a heat with the coolant at the inside thereof, and an air-cooled condenser connected in series to the water-cooled condenser through the refrigerant line.

SUMMARY

The present invention provides a thermal management system, as defined by appended independent claim 1, to improve the cooling effect of the thermal management system in a high-temperature environment.
It can be seen from the technical solution as defined by appended independent claim 1 that by providing the third heat exchanger at the outlet of the compressor, in the cooling mode, the refrigerant flowing out of the outlet of the compressor will firstly pass through the third heat exchanger. After cooling by the third heat exchanger, the refrigerant flows into the first heat exchanger (that is, the outdoor heat exchanger), the heat of the refrigerant loop is brought to the outside environment through the coolant loop, thereby bearing part of the heat exchange pressure of the outdoor heat exchanger. This effectively solves the problem of insufficient heat exchange capacity of the outdoor heat exchanger in a high temperature environment, and improves the cooling effect of the thermal management system.

BRIEF DESCRIPTION OF DRAWINGS

Drawings here are incorporated into the specification and constitute a part of the specification, show embodiments that comply with the present invention, and are used together with the specification to explain the principle of the present invention.

FIG. 1 is a schematic structural view of a thermal management system provided by an embodiment of the present invention;
FIG. 2 is a schematic view of flow paths of a refrigerant and a coolant in a cooling mode of the thermal management system of FIG. 1, wherein bold lines represent the flow paths;
FIG. 3 is a schematic view of a refrigerant flow path of the heat management system of FIG. 1 in a heating mode, wherein bold lines represent the flow path;
FIG. 4 is a schematic view of a refrigerant flow path of the heat management system of FIG. 1 in a heating and dehumidifying mode, wherein bold lines represent the flow path; and
FIG. 5 is a schematic view of a partial cut-away structure of a third heat exchanger in accordance with an embodiment of the present invention.

Reference signs:

1: compressor; 2: first heat exchanger; 21: first connection port; 22: second connection port; 3: first throttling device; 4: second heat exchanger; 41: third connection port; 42: fourth connection port; 5: coolant loop; 51: motor; 52: pump device; 6: third heat exchanger; 61: first heat exchange portion; 611: first inlet; 612: first outlet; 62: second heat exchange portion; 7: fourth heat exchanger; 8: gas-liquid separator; 9: first fan; 10: fifth heat exchanger; 11: third heat exchange portion; 111: seventh connection port; 112: eighth connection port; 12: fourth heat exchange portion; 13 air-conditioning box; 14: damper; 15: first collecting member; 16: second collecting member; 17: heat exchange tube; 18: heat sink; 19: casing 190: heat exchange cavity; 20: second throttling device; 30: sixth heat exchanger; 301: fifth connection port; 302: sixth connection port; 40: four-way valve; 401: first port; 402: second port; 403: third port; 404: fourth port; 50: shut-off valve; 60: check valve; 70: second fan; 80: control valve.

DETAILED DESCRIPTION

The exemplary embodiments will be described in detail here, and examples thereof are shown in the drawings. The present invention is solely defined by the appended independent claim. When the following description refers to the drawings, unless otherwise indicated, the same numbers in different drawings indicate the same or similar elements. The implementation embodiments described in the following exemplary embodiments do not represent all implementation embodiments consistent with the present invention. On the contrary, they are merely examples of devices and methods consistent with some aspects of the present invention as detailed in the appended claims.
The singular forms of "a", "said" and "the" used in the present invention and appended claims are also intended to include plural forms, unless the context clearly indicates otherwise. It should also be understood that the term "and/or" as used herein refers to and includes any or all possible combinations of one or more associated listed items.
It should be understood that although the terms "first", "second", "third", etc., may be used in the present invention to describe various information, the information should not be limited to these terms. These terms are only used to distinguish the same type of information from each other. For example, without departing from the scope of the present invention, a first information may also be referred to as a second information. Similarly, the second information may also be referred to as the first information. Depending on the context, the word "if' as used herein can be interpreted as "when" or "during" or "depending on".
The term "communicated" used in the present invention is intended to indicate that a certain medium can circulate from one element to another element. The term "connected" used in the present invention is intended to indicate a physical relationship, and does not necessarily mean that the components are communicated.
The thermal management system of the present invention will be described in detail below with reference to the accompanying drawings.
Referring to FIGS. 1 to 4, a thermal management system provided by an embodiment of the present invention is disclosed. The thermal management system may include a compressor 1, a first heat exchanger 2, a first throttling device 3, a second heat exchanger 4, a third heat exchanger 6, a fourth heat exchanger 7, and an air-conditioning box 13. Among them, the third heat exchanger 6 includes a first heat exchange portion 61 and a second heat exchange portion 62. The first heat exchange portion 61 and the second heat exchange portion 62 can exchange heat with each other. The first heat exchanger 2 and the fourth heat exchanger 7 in this embodiment are located outside the air-conditioning box 13. The second heat exchanger 4 is located in an indoor air inlet passage. The indoor air inlet passage is a passage of the air-conditioning box 13, that is, the second heat exchanger 4 is located in the air-conditioning box 13.
The thermal management system of this embodiment includes a cooling mode. Referring to FIG. 2, in the cooling mode, the thermal management system includes two loops, namely a first refrigerant loop and a coolant loop. Among them, an outlet of the compressor 1, the first heat exchange portion 61, the first heat exchanger 2, the first throttling device 3, the second heat exchanger 4, and an inlet of the compressor 1 are in communication to form the first refrigerant loop. Optionally, the outlet of the compressor 1, the first heat exchange portion 61, the first heat exchanger 2, the first throttling device 3, the second heat exchanger 4, and the inlet of the compressor 1 are in communication in sequence to form the first refrigerant loop.
The second heat exchange portion 62 and the fourth heat exchanger 7 are in communication to form a coolant loop 5. Optionally, the second heat exchange portion 62 and the fourth heat exchanger 7 are sequentially communicated to form the coolant loop 5. Of course, the above-mentioned structures in the coolant loop 5 can also be communicated in other arrangement sequences.
It should be noted that, in the embodiment of the present invention, the sequential communication only describes the sequence relationship between the various components, and the various components may also include other components, such as a shut-off valve. In addition, the type of the coolant disclosed in the present invention can be selected according to needs. For example, the coolant can be a heat exchange substance such as water and oil, or a mixture of water and ethylene glycol or other mixtures that can exchange heat.
In this embodiment, the coolant in the second heat exchange portion 62 can cool down the temperature of the refrigerant in the first heat exchange portion 61.
Specifically, in the cooling mode, the first heat exchanger 2 is used as a condenser, and the second heat exchanger 4 is used as an evaporator. Referring to FIG. 2, the compressor 1 compresses a low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant flows out of the outlet of the compressor 1 and enters the first heat exchange portion 61. The refrigerant in the first heat exchange portion 61 exchanges heat with the coolant in the second heat exchange portion 62, and the refrigerant releases heat. The released heat is carried by the coolant loop 5 to the fourth heat exchanger 7. The heated coolant exchanges heat with the outdoor air flow in the fourth heat exchanger 7. The coolant releases heat, and the released heat is carried by the air flow to the outdoor ambient air. The low-temperature coolant continues to be recycled in the coolant loop 5. After the refrigerant in the first heat exchange portion 61 releases heat, the cooled refrigerant enters the first heat exchanger 2 and exchanges heat with the outdoor air flow in the first heat exchanger 2, and the refrigerant further releases heat. The released heat is carried by the air flow to the outdoor ambient air, and the refrigerant undergoes a phase change and condenses into a liquid or gas-liquid two-phase refrigerant. The refrigerant flows out of the first heat exchanger 2, and is throttled and depressurized by the first throttling device 3 to become a low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant enters the second heat exchanger 4. The low-temperature and low-pressure refrigerant absorbs the heat of the air around the second heat exchanger 4, so that the temperature of the air around the second heat exchanger 4 is lowered. Under the action of the air flow, the cold air enters the passage of the air-conditioning box 13 and is sent into the cabin, thereby reducing the indoor temperature. The refrigerant undergoes a phase change and partially or completely evaporates into a low-temperature and low-pressure gaseous refrigerant, which flows back into the compressor 1 to realize the recycling of the refrigerant.
A third heat exchanger 6 is provided at the outlet of the compressor 1. In the cooling mode, the refrigerant in the first heat exchange portion 61 is cooled down by the coolant in the second heat exchange portion 62, which can reduce the temperature of the refrigerant in the outlet pipe of the compressor 1, for example, the temperature of the refrigerant decreases from 150°C to 80°C. This reduces the temperature of the refrigerant flowing into the first heat exchanger 2 and reduces the heat exchange pressure of the first heat exchanger 2. The cooled refrigerant then passes through the first heat exchanger 2 to exchange heat with the external environment so as to further reduce the temperature of the refrigerant, for example, the temperature of the refrigerant decreases from 80°C to 47°C. The refrigerant flowing out of the first heat exchanger 2 sequentially flows through the first throttling device 3 to reduce pressure, flows through the second heat exchanger 4 to absorb heat and evaporate, and then flows back into the compressor 1 to realize the recycling of the refrigerant.
In the thermal management system of the present invention, the third heat exchanger 6 is provided at the outlet of the compressor 1. In the cooling mode, the refrigerant flowing out of the outlet of the compressor 1 will firstly pass through the third heat exchanger 6. After the temperature is lowered by the third heat exchanger 6, the refrigerant flows into the first heat exchanger 2 (i.e., the outdoor heat exchanger), takes the heat to the outside environment through the coolant loop 5, and undertakes part of the heat exchange of the outdoor heat exchanger pressure. This effectively solves the problem of insufficient outdoor heat exchanger capacity in high temperature environments (for example, between 35°C and 50°C), and improves the cooling capacity of the system.
Those of ordinary skill in the art can select the types of the first heat exchanger 2, the second heat exchanger 4, the third heat exchanger 6, and the fourth heat exchanger 7 according to specific scenarios. For example, the first heat exchanger 2, the second heat exchanger 4, and the fourth heat exchanger 7 may be air-cooled heat exchangers. The third heat exchanger 6 is a water-cooled heat exchanger. Referring to FIG. 5, the third heat exchanger 6 includes a first collecting member 15, a second collecting member 16 and a casing 19. The casing 19 has two ends. The two ends of the casing 19 are sealed and connected to the first collecting member 15 and the second collecting member 16, respectively so as to enclose a heat exchange cavity 190. A heat exchange tube 17 and a heat sink 18 are disposed in the third heat exchanger 6. The heat exchange tube 17 and the heat sink 18 are alternately stacked in the heat exchange cavity 190 one by one. The heat exchange tube 17 and the heat sink 18 are fixedly connected. Two ends of the heat exchange tube 17 are fixedly connected to the first collecting member 15 and the second collecting member 16, respectively. Each of the first collecting member 15 and the second collecting member 16 defines a collecting cavity. The collecting cavity is in communication with a tube cavity of the heat exchange tube 17, so that the refrigerant can circulate between the first collecting member 15 and the second collecting member 16. The two opposite sides of the casing 19 are also provided with an inlet pipe and an outlet pipe, so that the coolant can enter and exit the heat exchange cavity 190. The coolant enters the heat exchange cavity 190 and exchanges heat with the refrigerant through the heat exchange tube 17. The heat sink 18 may be corrugated fins for improving heat exchange efficiency. The heat exchange tube 17 may be a microchannel flat tube. Two connecting members are provided on the second current collecting member 16. The two connecting members are respectively used to connect the refrigerant pipeline, so that the refrigerant can enter and exit the second collecting member 16. It is understandable that those of ordinary skill in the art can select other types of heat exchangers as the first heat exchanger 2, the second heat exchanger 4, the third heat exchanger 6 and the fourth heat exchanger 7 according to specific scenarios, which is not limited here. According to the present invention, the corresponding type of refrigerant can also be selected and a suitable heat exchanger can be used according to the actual application. For example, the third heat exchanger 6 may adopt the structure shown in FIG. 5, which has the characteristics of high pressure resistance and is suitable for using a medium with high pressure resistance requirements, such as carbon dioxide, as the refrigerant.
In this embodiment, the thermal management system also includes a functional component. The functional component can generate heat and needs to dissipate heat when the temperature exceeds a set value. The coolant loop includes the above-mentioned functional component. The coolant loop is used to dissipate heat from the functional component. Therefore, the coolant loop 5 in this embodiment can also undertake the heat dissipation of the functional component in the thermal management system to ensure the normal operation of the functional component, thereby effectively ensuring the stable operation of the thermal management system in the cooling mode. Referring to FIG. 1, the functional component may include a motor 51. The coolant loop 5 can also undertake the heat dissipation of the motor 51 in the thermal management system to ensure the normal operation of the motor 51, thereby effectively ensuring the stable operation of the thermal management system in the cooling mode. It is understandable that the functional components may also include other components capable of generating heat, such as a battery and so on. The thermal management system can recycle the waste heat generated by the functional component. For example, in a heating mode in winter, the waste heat of functional component is used to improve the heating capacity of the thermal management system. In addition, referring to FIG. 1 again, the coolant loop may also include a power device (for example, a pump device 52) for flowing the coolant. By providing the pump device 52, the circulating flow of the coolant in the coolant loop 5 can be driven. Optionally, in an embodiment, the coolant flow path of the coolant loop 5 includes: the pump device 52 -> the motor 51 (or other functional component) -> the second heat exchange portion 62 -> the fourth heat exchanger 7.
Referring to FIG. 1, the thermal management system may further include a first fan 9 located outside the air-conditioning box 13. In this embodiment, the first heat exchanger 2 and the fourth heat exchanger 7 are disposed along the air flow direction of the first fan 9. That is, the first heat exchanger 2 is located on an upwind side of the fourth heat exchanger 7. With this arrangement, on one hand, the first heat exchanger 2 and the second heat exchanger 4 share the fan to dissipate heat from the first heat exchanger 2 and the second heat exchanger 4, and save installation space; on the other hand, in the cooling mode, since the temperature of the first heat exchanger 2 is usually higher than the temperature of the fourth heat exchanger 7, this arrangement allows the air to pass through the first heat exchanger 2 with a higher temperature first, and then pass through the fourth heat exchanger 7 with a lower temperature, thereby helping to improve the heat exchange effect and avoid affecting he heat dissipation of the first heat exchanger 2. Optionally, the first fan 9, the first heat exchanger 2 and the fourth heat exchanger 7 are disposed in a row or a column at intervals. Optionally, the fourth heat exchanger 7 is located between the first fan 9 and the first heat exchanger 2. The air flow generated by the first fan 9 can more quickly take away the heat of the coolant in the fourth heat exchanger 7, speed up the cooling effect of the coolant loop 5, and reduce the temperature of the refrigerant in the second heat exchange portion 62 more quickly .
In addition, referring to FIG. 1 again, the inlet of the compressor 1 can also be connected with a gas-liquid separator 8 to perform gas-liquid separation of the refluxed refrigerant. The liquid part of the refrigerant is stored in the gas-liquid separator 8, and the low-temperature and low-pressure gaseous refrigerant part enters the compressor 1 to be compressed again, so as to realize the recycling of the refrigerant. Of course, for some new compressors, such as compressors with a function of storing liquid or a function of gas-liquid separation, the gas-liquid separator 8 may not be provided.
In the following, taking the gas-liquid separator 8 provided at the inlet of the compressor 1 as an example, the structure of the thermal management system is further explained.
Referring to FIGS. 1 and 2, the thermal management system includes a fifth heat exchanger 10. The fifth heat exchanger 10 includes a third heat exchange portion 11 and a fourth heat exchange portion 12. Referring to FIG. 2, in the cooling mode, the outlet of the compressor 1, the first heat exchange portion 61, the first heat exchanger 2, the third heat exchange portion 11, the first throttling device 3, the second heat exchanger 4, the gas-liquid separator 8, the fourth heat exchange portion 12, and the inlet of the compressor 1 are communicated to form the first refrigerant loop. Specifically, in the cooling mode, the refrigerant flowing out of the first heat exchanger 2 passes through the third heat exchange portion 11 again. The refrigerant in the third heat exchange portion 11 exchanges heat with the refrigerant in the fourth heat exchange portion 12 (a low-pressure side pipeline) to further reduce the refrigerant temperature in the third heat exchange portion 11 and further improve the cooling effect of the thermal management system. The refrigerant flowing out of the third heat exchange portion 11 is throttled and depressurized by the first throttling device 3 to become a low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant enters the second heat exchanger 4. The low-temperature and low-pressure refrigerant absorbs the heat of the air around the second heat exchanger 4, so that the temperature of the air around the second heat exchanger 4 is lowered. Under the action of the air flow, the cold air enters the passage of the air-conditioning box 13 and is sent into the cabin, thereby reducing the indoor temperature. The refrigerant undergoes a phase change and most of it evaporates into a low-temperature and low-pressure gas refrigerant, which flows into the gas-liquid separator 8. The gas-liquid separator 8 separates the refluxed refrigerant, and stores the liquid part of it in the gas-liquid separator 8, while the low-temperature and low-pressure gaseous refrigerant part enters the compressor 1 through the fourth heat exchange portion 12 to be compressed again so as to realize the recycling of refrigerant.
Referring to FIG. 1 again, the thermal management system includes a second throttling device 20 and a sixth heat exchanger 30. The sixth heat exchanger 30 is located in the passage of the air-conditioning box 13. Referring to FIG. 3, the thermal management system of this embodiment also includes a heating mode. In the heating mode, the outlet of the compressor 1, the first heat exchange portion 61, the sixth heat exchanger 30, the second throttling device 20, the third heat exchange portion 11, the first heat exchanger 2, the gas-liquid separator 8, the fourth heat exchange portion 12, and the inlet of the compressor 1 are communicated to form a second refrigerant loop. It is understandable to those skilled in the art that only one of the first refrigerant loop in the cooling mode and the second refrigerant loop in the heating mode can be selected in the same working mode.
The thermal management system also includes a damper 14 located in the air-conditioning box 13. The damper 14 is located between the second heat exchanger 4 and the sixth heat exchanger 30. The damper 14 is used to control whether the air passes through the sixth heat exchanger 30 or not. For example, in the cooling mode, the damper 14 is closed so that the air does not pass through the sixth heat exchanger 30. In the heating mode, the damper 14 is opened to allow air to pass through the sixth heat exchanger 30.
Specifically, in the heating mode, the first heat exchanger 2 is used as an evaporator, and the sixth heat exchanger 30 is used as a condenser or an air cooler. In the heating mode, the damper 14 is opened so that air can flow through the sixth heat exchanger 30. It should be noted that in the cooling mode, the damper 14 at the sixth heat exchanger 30 is closed, which reduces the influence of the sixth heat exchanger 30. Referring to FIG. 3, the compressor 1 compresses a low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant flows out of the outlet of the compressor 1 and enters the sixth heat exchanger 30 through the first heat exchange portion 61. The high-temperature and high-pressure refrigerant exchanges heat with the air flow in the sixth heat exchanger 30, and the refrigerant releases heat. The hot air enters the passage of the air-conditioning box 13 and is sent into the cabin to increase the indoor temperature. The refrigerant undergoes a phase change and condenses into a liquid or gas-liquid two-phase refrigerant. The refrigerant flows out of the sixth heat exchanger 30 and enters the second throttling device 20, where it is throttled and depressurized to become a low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant enters the first heat exchanger 2 through a third channel, absorbs the heat in the external air flow, and changes phase into a low-pressure gaseous refrigerant. The low-pressure gas refrigerant enters the gas-liquid separator 8 after flowing out of the first heat exchanger 2. The gas-liquid separator 8 separates the refluxed refrigerant, and stores the liquid part of it in the gas-liquid separator 8, while the low-temperature and low-pressure gaseous refrigerant part enters the compressor 1 through the fourth heat exchange portion 12 and is compressed again so as to realize the recycling of refrigerant.
The thermal management system of the present invention also includes a first branch. The first branch is disposed in parallel with the third heat exchanger 6. A control valve 80 is provided on the first branch. The control valve 80 may be a water valve or other types of valves. Referring to FIG. 3, the control valve 80 is connected to the first branch. The control valve 80 is disposed in parallel with the third heat exchanger 6. Optionally, the control valve 80 may also be a three-way valve. A first port of the three-way valve is connected to the motor 51 through a pipeline. A second port of the three-way valve is connected to the second heat exchange portion 62 of the third heat exchanger 6 through a pipeline. A third port of the three-way valve is connected to the first branch.
In the heating mode, when the motor generates excess heat, the control valve 80 is opened, and the pump device 52 is turned on. Since the flow resistance of the coolant at the third heat exchanger 6 is greater than the flow resistance at the control valve 80, only a small amount of coolant flows to the third heat exchanger 6. The coolant flow path of the coolant loop 5 includes: the pump device 52 -> the motor 51 (or other functional component) -> the control valve 80 -> the fourth heat exchanger 7. The waste heat generated by the motor is released to the external environment through the fourth heat exchanger 7. When the fourth heat exchanger 7 is located between the first fan 9 and the first heat exchanger 2 (positions of the fourth heat exchanger 7, the first fan 9 and the first heat exchanger 2 are not limited, which is disposed roughly along the air flow direction), the air flow generated by the first fan 9 can take away the heat of the coolant of the fourth heat exchanger 7 more quickly, and the air temperature rises at the same time. Correspondingly, the temperature of the surrounding environment of the first heat exchanger 2 rises, and the low-temperature refrigerant in the first heat exchanger 2 can absorb this part of the heat. As a result, when the external environment temperature is low in winter, the excess heat generated by the motor will be absorbed by the refrigerant in the first heat exchanger 2, which can increase the heating capacity of the thermal management system. Besides, in the heating mode in winter, the first heat exchanger 2 is prone to frost in a low temperature environment, and the control valve 80 can be opened to defrost the first heat exchanger 2.
Referring to FIG. 4, the thermal management system also includes a heating and dehumidifying mode which can be executed when dehumidification is required in winter. In the heating and dehumidifying mode, the outlet of the compressor 1, the first heat exchange portion 61, the sixth heat exchanger 30, the second throttling device 20, the third heat exchange portion 11, the first heat exchanger 2, the gas-liquid separator 8, the fourth heat exchange portion 12, and the inlet of the compressor 1 are communicated to form the second refrigerant loop. And, the outlet of the compressor 1, the first heat exchange portion 61, the sixth heat exchanger 30, the first throttling device 3, the second heat exchanger 4, the gas-liquid separator 8, the fourth heat exchange portion 12, and the inlet of the compressor 1 are communicated to form a third refrigerant loop.
Among them, the second refrigerant loop is the second refrigerant loop in the heating mode in the above embodiment. The third refrigerant loop is used to cool down the cabin. The working process of the third refrigerant loop is as follows: the compressor 1 compresses a low-temperature and low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant; the high-temperature and high-pressure gaseous refrigerant flows out of the outlet of the compressor 1, enters the sixth heat exchanger 30 through the first heat exchange portion 61, and exchanges heat in the sixth heat exchanger 30; the refrigerant releases heat, the released heat is carried into the cabin by the air flow, and the refrigerant undergoes a phase change and condenses into a liquid or gas-liquid two-phase refrigerant. One path of the refrigerant flows out of the sixth heat exchanger 30 and enters the second throttling device 20 to realize the heating function of the second refrigerant loop. The other path of the refrigerant enters the first throttling device 3 for expansion. The refrigerant is throttled and depressurized to become a low-temperature and low-pressure refrigerant. The low-temperature and low-pressure refrigerant enters the second heat exchanger 4. At this time, the air circulation mode is an inner circulation, and the air with higher humidity flows through the second heat exchanger 4 with relatively lower temperature. The moisture in the air flow condenses into water droplets to reduce the humidity of the air around the second heat exchanger 4. The dehumidified air then flows through the sixth heat exchanger 30 for heating, so as to achieve the purpose of heating and dehumidifying. The refrigerant undergoes a phase change and most of it evaporates into a low-temperature and low-pressure gas refrigerant, which flows into the gas-liquid separator 8. The gas-liquid separator 8 separates the refluxed refrigerant, and stores the liquid part of it in the gas-liquid separator 8, while the low-temperature and low-pressure gaseous refrigerant enters the compressor 1 to be compressed again so as to realize the recycling of the refrigerant.
Referring to FIG. 1 again, the thermal management system further includes a four-way valve 40. The four-way valve 40 includes a first port 401, a second port 402, a third port 403 and a fourth port 404. The first heat exchange portion 61 includes a first inlet 611 and a first outlet 612. The first heat exchanger 2 includes a first connection port 21 and a second connection port 22. The second heat exchanger 4 includes a third connection port 41 and a fourth connection port 42. The sixth heat exchanger 30 includes a fifth connection port 301 and a sixth connection port 302. The third heat exchange portion 11 includes a seventh connection port 111 and an eighth connection port 112. The first inlet 611 is in communication with the outlet of the compressor 1. The first outlet 612 is in communication with the fifth connection port 301. The first port 401 is in communication with the sixth connection port 302. The second port 402 is in communication with the first connection port 21. The second connection port 22 is in communication with the seventh connection port 111. The eighth connection port 112 is in communication with one end of the second throttling device 20. The third port 403 is in communication with the other end of the second throttling device 20. In addition, the third port 403 is also in communication with one end of the first throttling device 3. The third connection port 41 is in communication with the other end of the first throttling device 3. The fourth connection port 42 and the fourth port 404 are in communication with the inlet of the gas-liquid separator 8. For the thermal management system without the gas-liquid separator 8, the fourth connection port 42 and the fourth port 404 are in communication with the inlet of the compressor 1 via the fourth heat exchange portion 12. In the cooling mode, the first port 401 and the second port 402 are in communication, and the third port 403 and the fourth port 404 are not in communication. In the heating mode and the heating and dehumidifying mode, the first port 401 is in communication with the third port 403, and the second port 402 is in communication with the fourth port 404. By controlling the communication state of the four-way valve 40, the flow direction of the refrigerant can be switched, thereby realizing the switching of different modes. Of course, a three-way valve or a shut-off valve can also be used to replace the four-way valve 40 to control the switching of the refrigerant flow direction and realize the switching of different modes.
Referring to FIGS. 1 to 4, the thermal management system may further include a shut-off valve 50. One end of the shut-off valve 50 is in communication with the first outlet 612 and the fifth connection port 301, and the other end of the shut-off valve 50 is in communication with the first port 401 and the sixth connection port 302. In this embodiment, in the cooling mode, the shut-off valve 50 is opened. Due to the flow resistance, the sixth heat exchanger 30 can be bypassed through the branch where the shut-off valve 50 is located. Only a small amount or no refrigerant flows through the sixth heat exchanger 30, which reduces the influence of the sixth heat exchanger 30 on the refrigeration effect. In the heating mode or the heating and dehumidifying mode, the shut-off valve 50 is closed. By controlling the shut-off valve 50, the on-off of the branch is realized. Applied to different modes, the shut-off valve 50 has a simple structure and reliable on-off control.
Referring to FIGS. 1 to 4 again, the thermal management system also includes a check valve 60. The check valve 60 is disposed in parallel with the second throttling device 20. Among them, in the cooling mode, the check valve 60 is opened, and the second throttling device 20 is closed. In the heating mode or the heating and dehumidifying mode, the check valve 60 is closed, and the second throttling device 20 throttles. By controlling the check valve 60 and the second throttling device 20, the on-off of the branch is realized, which can be applied to different modes.
It should be noted that in the embodiment of the present invention, the first throttling device 3 and the second throttling device 20 can play the role of throttling and depressurizing, and blocking in the thermal management system, and may include a throttling valve, an ordinary thermal expansion valve or an electronic expansion valve etc.
In addition, referring to FIG. 1 again, the thermal management system may further include a second fan 70 located in the passage of the air-conditioning box 13. The second heat exchanger 4 and the sixth heat exchanger 30 are disposed along the air flow direction of the second fan 70. With this arrangement, the second heat exchanger 4 and the sixth heat exchanger 30 share the fan, which saves installation space. Optionally, the second fan 70, the second heat exchanger 4 and the sixth heat exchanger 30 are disposed in a line or a row at intervals.
It is noted that the thermal management system of the present embodiments can be applied to houses, vehicles or other equipment.
The above descriptions are only preferred embodiments of the present invention, and are not intended to limit the present invention, which is solely defined by the claims.

Claims

A thermal management system, comprising: a compressor (1), a first heat exchanger (2), a first throttling device (3), a second heat exchanger (4), a third heat exchanger (6), a fourth heat exchanger (7) and an air-conditioning box (13), the third heat exchanger (6) comprising a first heat exchange portion (61) for circulating a refrigerant and a second heat exchange portion (62) for circulating a coolant, the second heat exchanger (4) being located in the air-conditioning box (13);
wherein the thermal management system is configured such that it comprises a cooling mode; in the cooling mode, an outlet of the compressor (1), the first heat exchange portion (61), the first heat exchanger (2), the first throttling device (3), the second heat exchanger (4) and an inlet of the compressor (1) are in communication to form a first refrigerant loop; the second heat exchange portion (62) and the fourth heat exchanger (7) are in communication to form a coolant loop (5); and the coolant in the second heat exchange portion (62) is capable of absorbing heat of the refrigerant in the first heat exchange portion (61); and

wherein the fourth heat exchanger (7) is located outside the air-conditioning box (13);

the thermal management system further comprises a fifth heat exchanger (10), a second throttling device (20) and a sixth heat exchanger (30), the fifth heat exchanger (10) comprises a third heat exchange portion (11) and a fourth heat exchange portion (12) capable of exchanging heat with the third heat exchange portion (11), the sixth heat exchanger (30) is located in the air-conditioning box (13);

wherein the thermal management system is configured such that it further comprises a heating and dehumidifying mode; and

wherein in the heating and dehumidifying mode, the outlet of the compressor (1), the first heat exchange portion (61), the sixth heat exchanger (30), the second throttling device (20), the third heat exchange portion (11), the first heat exchanger (2), the fourth heat exchange portion (12) and the inlet of the compressor (1) are in communication to form the second refrigerant loop; and the outlet of the compressor (1), the first heat exchange portion (61), the sixth heat exchanger (30), the first throttling device (3), the second heat exchanger (4), the fourth heat exchange portion (12) and the inlet of the compressor (1) are in communication to form a third refrigerant loop;

characterized in that the thermal management system further comprises a four-way valve (40), the four-way valve (40) having a first port (401), a second port (402), a third port (403) and a fourth port (404);

wherein the first heat exchange portion (61) comprises a first inlet (611) and a first outlet (612); the first heat exchanger (2) comprises a first connection port (21) and a second connection port (22); the second heat exchanger (4) comprises a third connection port (41) and a fourth connection port (42); the sixth heat exchanger (30) comprises a fifth connection port (301) and a sixth connection port (302); the third heat exchange portion (11) comprises a seventh connection port (111) and an eighth connection port (112); and

wherein the first inlet (611) is in communication with the outlet of the compressor (1); the first outlet (612) is in communication with the fifth connection port (301); the first port (401) is in communication with the sixth connection port (302); the second port (402) is in communication with the first connection port (21); the second connection port (22) is in communication with the seventh connection port (111); the eighth connection port (112) is in communication with one end of the second throttling device (20); the third port (403) is in communication with the other end of the second throttling device (20) and in communication with one end of the first throttling device (3); the third connection port (41) is in communication with the other end of the first throttling device (3); and the fourth connection port (42) and the fourth port (404) are in communication with the inlet of the compressor (1) through the fourth heat exchange portion (12).
The thermal management system according to claim 1, further comprising a first fan (9) located outside the air-conditioning box (13), the first heat exchanger (2) and the fourth heat exchanger (7) sharing the first fan (9) for heat dissipation.
The thermal management system according to claim 1, further comprising a fifth heat exchanger (10), the fifth heat exchanger (10) comprising a third heat exchange portion (11) and a fourth heat exchange portion (12) capable of exchanging heat with the third heat exchange portion (11); wherein
wherein the system is configured such that, in the cooling mode, the outlet of the compressor (1), the first heat exchange portion (61), the first heat exchanger (2), the third heat exchange portion (11), the first throttling device (3), the second heat exchanger (4), the fourth heat exchange portion (12) and the inlet of the compressor (1) are in communication to form the first refrigerant loop.
The thermal management system according to claim 1, further comprising a second throttling device (20) and a sixth heat exchanger (30), the sixth heat exchanger (30) being located in the air-conditioning box (13);
wherein the thermal management system is configured such that it further comprises a heating mode; in the heating mode, the outlet of the compressor (1), the first heat exchange portion (61), the sixth heat exchanger (30), the second throttling device (20), the first heat exchanger (2) and the inlet of the compressor (1) are in communication to form a second refrigerant loop.
The thermal management system according to claim 1, further comprising a shut-off valve (50), one end of the shut-off valve (50) being in communication with the first outlet (612) and being in communication with the fifth connection port (301), the other end of the shut-off valve (50) being in communication with the first port (401) and being in communication with the sixth connection port (302).
The thermal management system according to claim 5, wherein the system is configured such that in the cooling mode, the shut-off valve (50) is opened; and in the heating and dehumidifying mode, the shut-off valve (50) is closed.
The thermal management system according to claim 1, further comprising a gas-liquid separator (8), the fourth connection port (42) and the fourth port (404) being in communication with an inlet of the gas-liquid separator (8), an outlet of the gas-liquid separator (8) being in communication with the fourth heat exchange portion (12).
The thermal management system according to claim 4, further comprising a check valve (60), the check valve (60) being disposed in parallel with the second throttling device (20).
The thermal management system according to claim 8, wherein the system is configured such that, in the cooling mode, the check valve (60) is opened and the second throttling device (20) is closed; and in the heating mode, the check valve (60) is closed and the second throttling device (20) is opened.
The thermal management system according to any one of claims 1 to 9, further comprising a first branch which is disposed in parallel with the third heat exchanger (6), the first branch being connected to the coolant loop (5), the first branch being provided with a control valve (80); wherein in the cooling mode, the control valve (80) is closed.
The thermal management system according to any one of claims 1 to 9, further comprising a pump device (52) and a functional component that requires heat dissipation, the pump device (52) and the functional component being disposed in the coolant loop (5).
The thermal management system according to claim 1, further comprising a power device in communication with the coolant loop (5) for driving the coolant to flow; the first heat exchanger (2) being located outside the air-conditioning box (13).
The thermal management system according to claim 1, wherein the coolant loop (5) comprises a functional component that requires heat dissipation, and the functional component comprises a motor (51) and/or a battery.