CN218777385U - Coolant distribution assembly, thermal management module and vehicle thermal management system - Google Patents

Abstract

The utility model relates to a coolant distribution assembly, thermal management module and vehicle thermal management system. The utility model provides a coolant distribution subassembly, because its distributing plate main part has installation cavity, passageway chamber and through-hole, and through-hole intercommunication installation cavity and passageway chamber for the lid need not to have the function of intercommunication installation cavity and passageway chamber, therefore the structure of lid can design fairly simplely. This also simplifies the structure of the coolant distribution assembly and makes it easy to manufacture.

Description

Coolant distribution assembly, thermal management module and vehicle thermal management system

Technical Field

The utility model relates to a coolant distribution assembly, thermal management module and vehicle thermal management system.

Background

As vehicles move toward electrification, thermal management systems for vehicles have become increasingly important. The thermal management system of the vehicle not only needs to thermally manage the cabin environment, but also needs to thermally manage modules such as a battery, a motor and the like, so that the thermal management system of the vehicle needs to comprise a large number of refrigerant pipelines and coolant pipelines to communicate each component, which results in a complex structure and a large volume of the thermal management system.

There exists a need in the art for a thermal management module that reduces the size of the thermal management system by using highly customized components to reduce the number of refrigerant and coolant lines. The thermal management module includes a coolant distribution assembly including a coolant distribution unit including a coolant pump and a distribution plate body. The prior art coolant distribution assembly has a disadvantage of a complicated structure.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a coolant distribution subassembly has simple structure, the advantage of easily making.

It is also an object of the present invention to provide a thermal management module, including the above-mentioned coolant distribution assembly.

An object of the present invention is to provide a vehicle thermal management system, including foretell thermal management module.

The coolant distribution assembly comprises a distribution plate main body, a cover body and a coolant distribution unit; the distribution plate main body is provided with a mounting cavity, a channel cavity and a through hole; the through hole is communicated with the installation cavity and the channel cavity; the mounting cavity has a mounting opening, and the passage cavity has a passage opening; the coolant distribution unit is mounted to the mounting cavity through the mounting opening; the cover covers the passage opening.

To achieve the object, a thermal management module includes a first heat exchanger, a second heat exchanger, and a coolant distribution assembly;

the first heat exchanger having a first coolant opening and a second coolant opening;

the second heat exchanger having a third coolant opening and a fourth coolant opening;

the coolant distribution assembly having a first distribution port, a second distribution port, a third distribution port, a first intermediate through-hole, an upstream channel cavity, and a first downstream channel cavity;

the first coolant opening is in communication with the first distribution port; the second coolant opening communicates with the second distribution port and with the upstream channel chamber through the second distribution port and the first intermediate through hole;

the third coolant opening communicates with the third distribution port and with the first downstream passage cavity through the third distribution port.

The vehicle thermal management system comprises a heater core and a thermal management module; the thermal management module includes a coolant distribution assembly; the outlet of the heater core communicates with the first interface portion of the coolant distribution assembly and with the upstream channel cavity of the coolant distribution assembly through the first interface portion.

The utility model discloses an actively advance the effect and lie in: the utility model provides a coolant distribution subassembly, because its distributing plate main part has installation cavity, passageway chamber and through-hole, and through-hole intercommunication installation cavity and passageway chamber for the lid need not to have the function of intercommunication installation cavity and passageway chamber, therefore the structure of lid can design fairly simplely. This also simplifies the structure of the coolant distribution assembly and makes it easy to manufacture.

Drawings

The above and other features, properties and advantages of the present invention will become more apparent from the following description of the embodiments with reference to the accompanying drawings, in which:

FIG. 1 is a schematic view of a thermal management module;

FIG. 2 is a schematic view of the thermal management module with the bracket removed;

FIG. 3 is an exploded view of the thermal management module without the bracket;

FIG. 4 is a schematic view of a thermal management module showing a different bracket;

FIGS. 5A and 5B are schematic views of a rack and coolant distribution assembly;

FIGS. 6A and 6B are schematic views of a rack, a coolant distribution assembly, a first heat exchanger, a second heat exchanger, and a receiver-drier;

FIG. 7 is a top view of the rack, the coolant distribution assembly, the first heat exchanger, and the receiver-drier;

FIG. 8A is a schematic view of a coolant distribution assembly;

FIG. 8B is a top view of the distribution plate body;

FIG. 9A is a schematic view of the main body of the distribution plate showing the side where the channel cavities are located;

FIG. 9B is a schematic view of the main body of the distribution plate showing the side of the mounting cavity;

FIG. 10A isbase:Sub>A schematic view of the distributor plate body taken along the line A-A in FIG. 8B;

FIG. 10B is a partial enlarged view of FIG. 10A;

FIG. 11 is a schematic view of a portion of the body of the distribution plate showing a first edge of the through hole;

FIG. 12 is a schematic view of a portion of the body of the distributor plate showing the third and fourth edges of the through holes;

FIG. 13 is a top view of a portion of the body of the distribution plate showing a third edge of the through hole;

FIG. 14 is a cross-sectional view of a portion of the distribution plate body showing the upstream channel chamber;

FIG. 15A is a schematic view of a refrigerant valve assembly;

FIG. 15B is a schematic view of a valve body;

FIG. 16A is a schematic view of the valve body taken along the line B-B in FIG. 15B;

FIG. 16B is a top view of the valve body taken along the line B-B in FIG. 15B;

FIG. 17A is a schematic view of the valve body showing the second valve body opening and the fourth valve body opening;

FIG. 17B is a schematic view of the refrigerant valve assembly showing the second valve body opening and the fourth valve body opening;

FIG. 18 is a schematic diagram of a vehicle thermal management system;

FIG. 19 is a schematic illustration of a first mode of operation of the thermal management system of the vehicle;

FIG. 20 is a schematic illustration of a second mode of operation of the thermal management system of the vehicle;

FIG. 21 is a schematic illustration of a third mode of operation of the thermal management system of the vehicle;

FIG. 22 is a schematic illustration of a fourth mode of operation of the thermal management system for a vehicle;

FIG. 23 is a schematic illustration of a fifth mode of operation of the thermal management system of the vehicle;

FIG. 24 is a schematic illustration of a sixth mode of operation of the thermal management system of the vehicle;

FIG. 25 is a schematic illustration of a seventh mode of operation of the thermal management system of the vehicle;

FIG. 26 is a schematic illustration of an eighth mode of operation of the thermal management system of the vehicle.

Detailed Description

The following discloses embodiments or examples of various implementations of the subject technology. Specific examples of components and arrangements are described below to simplify the present disclosure, but these are merely examples and are not intended to limit the scope of the present invention. For example, a first feature described later in the specification may be distributed over a second feature and may include embodiments in which the first and second features are distributed in direct association, or may include embodiments in which additional features may be formed between the first and second features, such that the first and second features may not be directly associated with each other. Additionally, reference numerals and/or letters may be repeated among the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed. Further, when a first element is described as being coupled or coupled to a second element, the description includes embodiments in which the first and second elements are directly coupled or coupled to each other, as well as embodiments in which one or more additional intervening elements are added to indirectly couple or couple the first and second elements to each other.

It should be noted that fig. 1-26 are exemplary only, not drawn to scale, and should not be construed as limiting the scope of the invention.

The vehicle thermal management system not only needs to thermally manage the cabin environment, but also needs to thermally manage modules such as a battery and a motor. To accomplish these thermal management, a vehicle thermal management system includes a refrigerant circuit and a coolant circuit. The refrigerant in the refrigerant circuit is driven by a compressor and flows through an object requiring thermal management, such as an air conditioning module for a cabin environment. The coolant in the coolant circuit is driven by a coolant pump and flows through an object, such as a battery, an electric machine, etc., which needs to be thermally managed. The refrigerant in the refrigerant circuit is in heat exchange with the coolant in the coolant circuit to bring the coolant to a desired temperature. These heat exchanges are effected by means of heat exchangers. To meet the need for modularity, vehicle thermal management systems integrate at least some of the components that make up the refrigerant circuit and/or the coolant circuit to form a thermal management module.

Fig. 18 illustrates a vehicle thermal management system 900 in one embodiment of the invention, including a battery 92, a motor 93, an evaporator 94, a coolant heating device 95, a compressor 96, a radiator 97, an external heat exchanger 98, an external intermediate heat exchanger 99, an external electronic expansion valve 991, an external shutoff valve 992, and a thermal management module 90. "exterior" is with respect to thermal management module 90 and refers to the exterior of thermal management module 90.

Fig. 1-4 illustrate one thermal management module 90 in an embodiment of the invention, including a first heat exchanger 1, a coolant distribution assembly 2, and a bracket 3. The first heat exchanger 1 has a first coolant opening 1a, a second coolant opening 1b, a first refrigerant opening 1c, and a second refrigerant opening 1d. The first coolant opening 1a and the second coolant opening 1b define a coolant passage that extends through the first heat exchanger 1, and the first refrigerant opening 1c and the second refrigerant opening 1d define a refrigerant passage that extends through the first heat exchanger 1, wherein, inside the first heat exchanger 1, the coolant in the coolant passage exchanges heat with the refrigerant in the refrigerant passage. In one mode of operation of the vehicle thermal management system 900, the first heat exchanger 1 is an evaporator, i.e. the refrigerant evaporates in the first heat exchanger 1 to absorb heat from the coolant, so that the temperature of the coolant leaving the first heat exchanger 1 is reduced. The coolant distribution assembly 2 includes a distribution plate body 20; the distribution plate main body 20 has a first distribution port 2a and a second distribution port 2b; the first coolant opening 1a is connected to and communicates with the first distribution port 2a, and the second coolant opening 1b is connected to and communicates with the second distribution port 2 b.

More specifically, referring to fig. 3, the thermal management module 90 further includes a first hose 41 and a second hose 42, the first coolant opening 1a and the first distribution port 2a being connected and communicated through the first hose 41; the second coolant opening 1b and the second distribution port 2b are connected to and communicate with each other through a second hose 42. The use of the hose connection can attenuate the transmission of vibrations from the distributor plate body 20 to the first heat exchanger 1.

In one operating mode of the vehicle thermal management system, coolant exits the first heat exchanger 1 from the first coolant opening 1a and enters the distributor plate body 20 from the first distribution port 2a, and coolant exits the distributor plate body 20 from the second distribution port 2b and enters the first heat exchanger 1 from the second coolant opening 1 b.

The first heat exchanger 1 and the distribution plate body 20 are respectively mounted on the bracket 3 such that the first heat exchanger 1 and the refrigerant distribution assembly 2 are relatively independent, thereby allowing high compatibility and low maintenance costs of the thermal management module 90.

As shown in fig. 1, 4, 5A, 5B, 6A, 6B, 7, the bracket 3 includes a back plate 30 and a connecting plate 31; the distribution plate main body 20 is disposed opposite to the back plate 30; the connection plate 31 is connected to the back plate 30 and the distribution plate body 20, respectively. This design enables a space to be formed between the distribution plate body 20 and the backing plate 30 that can be used to mount other components of the thermal management module 90, such as the coolant distribution unit 22, including the coolant pump 221 and/or the coolant valve 222. This helps to make the thermal management module 90 compact. More specifically, the coolant pump 221 and the coolant valve 222 are installed on the distribution plate main body 20, and are located at a side of the distribution plate main body 20 facing the back plate 30.

As shown in fig. 1, 5A, 5B, the connecting plate 31 has a first plate portion 311; the first plate portion 311 is connected to the back plate 30 and the distribution plate main body 20, respectively; wherein the distribution plate main body 20 is located inside the first plate portion 311. The connecting plate 31 also has a second plate portion 312; the second plate portion 312 forms an angle with the first plate portion 311; the second plate portion 312 is connected to the distribution plate main body 20; wherein the distribution plate main body 20 is located inside the second plate portion 312. Where the inner side is the side relatively closer to the center of the thermal management module 90 and the outer side is the side relatively further from the center of the thermal management module 90. Such a design enables the distribution plate body 20 to be located inside the connection plate 31, contributing to the compactness of the thermal management module 90; further, the distribution plate main body 20 is connected to the first plate portion 311 and the second plate portion 312, respectively, so that the connection of the distribution plate main body 20 to the bracket 3 is relatively firm.

As shown in fig. 6A and 6B, the first heat exchanger 1 is mounted on the second plate portion 312, and is located inside the side plate portions 312 and inside the top plate portion 311. Where the inner side is the side relatively closer to the center of the thermal management module 90 and the outer side is the side relatively further from the center of the thermal management module 90. Such a design helps to make the thermal management module 90 compact.

As can be seen with reference to fig. 1, 2, 3, 4, at least a portion of the first heat exchanger 1 coincides with the distribution plate main body 20 in the thickness direction T of the distribution plate main body 20. Such a design makes the thermal management module 90 compact in the thickness direction T. More specifically, the distribution plate main body 20 has a notch 20c extending in the thickness direction T; the first heat exchanger 1 protrudes into the notch 20c to coincide with the distribution plate main body 20 in the thickness direction T.

The distribution plate main body 20 has a first portion 20a and a second portion 20b distributed in the width direction W thereof; the first portion 20a protrudes from the second portion 20b along the length direction L of the distributor plate body 20 to form a notch 20c.

As can be seen from fig. 3 and 4, the second portion 20b has a first dispensing port 2a and a second dispensing port 2b; the first coolant opening 1a and the second coolant opening 1b are provided in the notch 20c; the first and second coolant openings 1a and 1b are aligned with the first and second distribution ports 2a and 2b, respectively; the first hose 41 and the second hose 42 extend within the notch 20c. Such a design helps to make the thermal management module 90 compact and to reduce the transmission of vibrations from the distribution plate body 20 to the first heat exchanger 1. In a particular embodiment, the first heat exchanger 1 is perpendicular to the distributor plate body 20.

Referring to fig. 6A, 6B, the thermal management module 90 further includes a second heat exchanger 5 and a third hose 43; the second heat exchanger 5 has a third coolant opening 5a, a fourth coolant opening 5b, a third refrigerant opening 5c, and a fourth refrigerant opening 5d; wherein the third and fourth coolant openings 5a and 5b define the coolant passages of the second heat exchanger 5, and the third and fourth refrigerant openings 5c and 5d define the refrigerant passages of the second heat exchanger 5. The coolant in the coolant passage of the second heat exchanger 5 exchanges heat with the refrigerant in the refrigerant passage of the second heat exchanger 5. In one mode of operation of the vehicle thermal management system 900, the second heat exchanger 5 is a condenser, i.e., the refrigerant condenses in the second heat exchanger 5 to give up heat to the coolant, thereby increasing the temperature of the coolant exiting the second heat exchanger 5.

The distribution plate body 20 also has a third distribution port 2c; the third coolant opening 5a and the third distribution port 2c are connected and communicated through a third hose 43; wherein the distribution plate main body 20 is disposed opposite to the back plate 30, and the second heat exchanger 5 is mounted on the back plate 30 and is located outside the back plate 30. In one mode of operation of the vehicle thermal management system, coolant exits the distributor plate body 20 from the third distribution port 2c of the distributor plate body 20 and enters the second heat exchanger 5 from the third coolant opening 5a.

Referring to fig. 4, 6A, 6B, thermal management module 90 further includes a receiver drier 6; the bracket 3 further includes a mounting portion 32; the mounting portion 32 is connected to the second plate portion 312; the receiver-drier 6 is attached to the attachment portion 32 and connected to the first plate portion 311; the inlet 6a of the receiver drier 6 communicates with the fourth refrigerant opening 5 d. The receiver-drier 6 has an inlet 6a and an outlet 6b, wherein the inlet 6a of the receiver-drier 6 communicates with the fourth refrigerant opening 5d of the second heat exchanger 5.

Fig. 8A to 14 show a coolant distribution assembly 2 in an embodiment of the invention. As shown in fig. 8A, 8B, 9A, 9B, 10A, 10B, the coolant distribution assembly 2 includes a distribution plate main body 20, a cover body 21, and a coolant distribution unit 22; the distribution plate main body 20 has a mounting cavity 20d, a passage cavity 20e, and a through hole 20f; the through hole 20f communicates the mounting cavity 20d and the passage cavity 20e; mounting cavity 20d has mounting opening 205 and passage cavity 20e has passage opening 206; the mounting opening 205 and the passage opening 206 face the two sides in the thickness direction T of the distribution plate main body 20, respectively; the coolant distribution unit 22 is mounted to the mounting cavity 20d through the mounting opening 205; the cover 21 covers the passage opening 206. Such a design makes the coolant distribution assembly 2 easy to assemble. In one embodiment, the cover 21 is integrally coupled to the distribution plate main body 20 by thermal welding.

Referring to fig. 8A, the cover 21 has an interface portion 21a; the interface portion 21a communicates with the passage chamber 20 e. The interface portion 21a can communicate with a coolant line other than the thermal management module 90.

With continued reference to fig. 10A and 10B, the mounting cavity 20d has a first bottom wall 201 and a first side wall 202; one end of the first side wall 202 is connected to the first bottom wall 201 in the thickness direction T of the distribution plate main body 20, and the other end of the first side wall 202 defines a mounting opening 205; the passage cavity 20e has a second bottom wall 203 and a second side wall 204; one end of the second side wall 204 is connected to the second bottom wall 203 in the thickness direction T of the distribution plate main body 20, and the other end of the second side wall 204 defines a passage opening 206; in the mounting cavity 20d, the edge of the through hole 20f is formed on the first side wall 202 and/or the first bottom wall 201; in the passage chamber 20e, the edge of the through hole 20f is formed on the second side wall 204 and/or the second bottom wall 203. This design allows the mounting cavity 20d and the passage cavity 20e to be relatively closely distributed over the distribution plate body 20.

As shown in fig. 10B, the mounting cavity 20D has a first depth D1 in the thickness direction T defined by the mounting opening 205 and the first bottom wall 201; the passage cavity 20e has a second depth D2 in the thickness direction T defined by the mounting opening 206 and the second bottom wall 203; the first depth D1 and the second depth D2 at least partially coincide in the thickness direction T to define a coincidence region D3; at least a part of the edge of the through hole 20f is located in the overlap region 20g. Such a design makes the distribution plate main body 20 compact in the thickness direction T.

10B, 11, 12, the edges of the through-hole 20f include a first edge 2031 and a second edge 2041 within the channel cavity 20e; a first edge 2031 is formed on the second bottom wall 203 and a second edge 2041 is formed on the second side wall 204. The edges of the through hole 20f further include a third edge 2011 and a fourth edge 2021 located inside the mounting cavity 20d; the third edge 2011 is formed on the first bottom wall 201, and the fourth edge 2021 is formed on the first side wall 202. Such a design makes the area of the through-hole 20f large, thereby allowing a larger flow of coolant to pass therethrough.

Referring to fig. 1, 2, 3, 9B, 10A, 10B, the coolant distribution unit 22 includes a coolant pump 221, and the installation cavity 20d includes a pump installation cavity 20d'; the coolant pump 221 is mounted to the pump mounting cavity 20d'; the coolant pump 221 is used to suck and discharge the coolant into and out of the pump installation chamber 20 d'. The coolant distribution unit 22 also includes a coolant valve 222; the mounting cavity 20d also includes a valve mounting cavity 20d "and a coolant valve 222 is used to control the flow of coolant within the valve mounting cavity 20 d".

As shown in fig. 8B, the through-hole 20f includes an upstream through-hole 20f 'and a downstream through-hole 20f ", and the passage chamber 20e includes an upstream passage chamber 20e' and a downstream passage chamber 20e"; the pump installation chamber 20d ' communicates with the upstream passage chamber 20e ' through the upstream through hole 20f '; the pump mounting cavity 20d' communicates with the downstream channel cavity 20e "through the downstream through hole 20 f"; the pump mounting cavity 20d ' is configured to suck the coolant from the upstream passage cavity 20e ' through the upstream through hole 20f ' and to discharge the coolant to the downstream passage cavity 20e "through the downstream through hole 20 f".

As shown in fig. 10B, 12, and 13, the first bottom wall 201 of the pump mounting cavity 20d' is recessed to form a scroll flow passage 201a; wherein the scroll flow passage 201a gradually widens in a direction toward the downstream through hole 20f ″.

Referring to FIGS. 3, 9B, 10A, 14, and 18, pump mounting cavity 20d ' includes first pump mounting cavity 20d '1 and second pump mounting cavity 20d '2; the coolant pump 221 includes a first coolant pump 2211 mounted to the first pump mounting cavity 20d '1 and a second coolant pump 2212 mounted to the second pump mounting cavity 20d'2, and further includes a third coolant pump 2213; the upstream through holes 20f ' include first upstream through hole 20f '1 and second upstream through hole 20f '2; the downstream through-holes 20f ″ include a first downstream through-hole 20f '1 and a second downstream through-hole 20f'2; the downstream channel chamber 20e ″ includes a first downstream channel chamber 20e '1 and a second downstream channel chamber 20e' 2;

the first pump mounting chamber 20d '1 is provided to suck the coolant from the upstream channel chamber 20e ' through the first upstream through-hole 20f '1, and to discharge the coolant to the first downstream channel chamber 20e '1 through the first downstream through-hole 20f ' 1; the second pump mounting chamber 20d '2 is provided to suck the coolant from the upstream channel chamber 20e ' through the second upstream through-hole 20f '2, and to discharge the coolant to the second downstream channel chamber 20e '2 through the second downstream through-hole 20f '2. This design makes the first and second pump mounting cavities 20d '1 and 20d '2 share the same upstream channel cavity 20e ', thereby making the structure of the distribution plate body 20 compact.

With continued reference to fig. 9A, the first upstream through holes 20f '1 and the second upstream through holes 20f '2 are distributed at a distance in the extending direction of the upstream channel chamber 20e '.

Referring to fig. 14, the interface portion 21a of the cover 21 includes a first interface portion 21a1, a second interface portion 21a2, a third interface portion 21a3, a fourth interface portion 21a4, a fifth interface portion 21a5 and a sixth interface portion 21a6; wherein the first interface part 21a1 and the second interface part 21a2 are respectively communicated with the upstream channel chamber 20e ', wherein the first interface part 21a1 is arranged concentrically with the first upstream through hole 20f '1, and the second interface part 21a2 is arranged concentrically with the second upstream through hole 20f '2. Such a design enables the coolant entering the upstream channel cavity 20e 'from the first interface part 21a1 to pass through the first upstream through hole 20f'1 through the shortest route and enter the first pump mounting cavity 20d '1, and enables the coolant entering the upstream channel cavity 20e' from the second interface part 21a2 to pass through the second upstream through hole 20f '2 through the shortest route and enter the second pump mounting cavity 20d'2. This can effectively reduce the possibility that the coolant entering the upstream passage chamber 20e 'from the first interface portion 21a1 enters the second pump mounting chamber 20d'2, and can also effectively reduce the possibility that the coolant entering the upstream passage chamber 20e 'from the second interface portion 21a2 enters the first pump mounting chamber 20d'1. The third, fourth, fifth and sixth interface ports 21a3, 21a4, 21a5 and 21a6 each communicate with a corresponding channel chamber 20 e.

With continued reference to fig. 3, 9A, 9B, 14, and 18, the coolant distribution unit 22 further includes a coolant valve 222; mounting cavity 20d further includes a valve mounting cavity 20d "; the coolant valve 222 is mounted to the valve mounting cavity 20d "; wherein the coolant valves 222 include a first coolant valve 2221, a second coolant valve 2222, and a third coolant valve 2223; the valve installation chamber 20d ″ includes a first valve installation chamber 20d '1, a second valve installation chamber 20d '2, and a third valve installation chamber 20d ' 3; the first coolant valve 2221 is mounted to the first valve mounting chamber 20d '1, the second coolant valve 2222 is mounted to the second valve mounting chamber 20d '2, and the third coolant valve 2223 is mounted to the third valve mounting chamber 20d ' 3; the through-holes 20f include a first intermediate through-hole 20f-1; the upstream passage chamber 20e 'is communicated with the first valve mounting chamber 20d'1 through a first intermediate through-hole 20f-1; the first intermediate through hole 20f-1, the first upstream through hole 20f '1 and the second upstream through hole 20f '2 are distributed in the extending direction of the upstream channel chamber 20e '; wherein the second upstream through hole 20f '2 is located between the first intermediate through hole 20f-1 and the first upstream through hole 20f' 1. Such a design enables the coolant that enters the upstream channel cavity 20e ' from the first intermediate through hole 20f-1 to enter the second pump mount cavity 20d '2 through the second upstream through hole 20f '2 as far as possible, thereby reducing the possibility that the coolant enters the first pump mount cavity 20d '1 through the first upstream through hole 20f '1.

Referring to fig. 1, 2, 3, 4, 6A, 6B, 9A, 9B and 18, the thermal management module 90 includes a first heat exchanger 1, a second heat exchanger 5 and a coolant distribution assembly 2; the first heat exchanger 1 has a first coolant opening 1a and a second coolant opening 1b; the second heat exchanger 5 has a third coolant opening 5a and a fourth coolant opening 5b; the coolant distribution assembly 2 has a first distribution port 2a, a second distribution port 2b, a third distribution port 2c, a first intermediate through-hole 20f-1, an upstream channel chamber 20e', and a first downstream channel chamber 20e ″ -1; the first coolant opening 1a is connected to and communicates with the first distribution port 2 a; the second coolant openings 1b are connected to and communicate with the second distribution port 2b, and communicate with the upstream passage chamber 20e' through the second distribution port 2b and the first intermediate through-hole 20f-1; the third coolant opening 5a is connected to and communicates with the third distribution port 2c, and communicates with the first downstream channel chamber 20e ″ -1 through the third distribution port 2 c.

With continued reference to FIG. 18, the vehicle thermal management system 900 includes a heater core 91 and a thermal management module 90; the thermal management module 90 includes a coolant distribution assembly 2; the outlet 91a of the heater core 91 communicates with the first port portion 21a1 of the coolant distribution assembly 2, and communicates with the upstream passage chamber 20e' of the coolant distribution assembly 2 through the first port portion 21a 1.

In one operation mode of the vehicle thermal management system 900, the coolant cooled by the first heat exchanger 1 exits the first heat exchanger 1 from the second coolant opening 1b, enters the distributor plate main body 20 from the second distribution port 2b, and enters the upstream passage chamber 20e' through the first valve mounting chamber 20d "1 and the first intermediate through-hole 20f-1 under the control of the first coolant valve 2221; the coolant heated by the heater core 91 exits the heater core 91 from the outlet 91a, and enters the upstream passage chamber 20e' through the first interface portion 21a 1. Since the first interface portion 21a1 is provided concentrically with the first upstream through hole 20f '1, the coolant heated by the heater core 91 can enter the first pump mounting cavity 20d '1 through the first upstream through hole 20f '1 as much as possible. Since the second upstream through hole 20f '2 is closer to the first intermediate through hole 20f-1 than to the first upstream through hole 20f'1, the coolant cooled by the first heat exchanger 1 can pass through the second upstream through hole 20f '2 and enter the second pump mounting chamber 20d'2 as much as possible. In this mode of operation of the vehicle thermal management system 900, therefore, mixing of the coolant heated by the heater core 91 and the coolant cooled by the first heat exchanger 1 in the upstream passage chamber 20e' can be avoided as much as possible, which is advantageous in improving the efficiency of the vehicle thermal management system 900.

Fig. 15A to 17B show a refrigerant valve assembly 2 in an embodiment of the present invention. The refrigerant valve assembly 2 includes a valve body 70; the valve body 70 has a first valve body opening 70a, a second valve body opening 70b, a third valve body opening 70c, a first intermediate chamber 70g, a fourth valve body opening 70d, a fifth valve body opening 70e, a sixth valve body opening 70f, and a second intermediate chamber 70h; wherein the first intermediate chamber 70g and the first, second and third valve body openings 70a, 70b, 70c define a first internal passage 701, a second internal passage 702, 703, respectively; second intermediate chamber 70h and fourth, fifth and sixth valve body openings 70d, 70e and 70f define fourth, fifth and sixth internal passages 704, 705 and 706, respectively. Such a design helps to reduce the number of openings of the valve body 70, thereby making the valve body 70 compact.

In one particular embodiment, the first valve body opening 70a is an inlet and the second valve body opening 70b and the third valve body opening 70c are outlets. The refrigerant enters the valve body 70 from the first valve body opening 70a, and flows into the first intermediate chamber 70g through the first internal passage 701, and then is divided into two paths in the first intermediate chamber 70g, one path flowing to the second valve body opening 70b through the second internal passage 702, and the other path flowing to the third valve body opening 70c through the third internal passage 703. The refrigerant exits the valve body 70 from the second valve body opening 70b and the third valve body opening 70c, respectively. It can be seen that the second valve body opening 70b and the third valve body opening 70c, which are outlets, share the first valve body opening 70a, which is an inlet. Such a design helps to reduce the number of openings of the valve body 70, thereby making the valve body 70 compact.

The valve body 70 also has a seventh valve body opening 70L, and the seventh valve body opening 70L communicates with the first internal passage 701. A part of the refrigerant entering the valve body 70 from the first valve body opening 70a flows toward the seventh valve body opening 70L, and the other part flows toward the first intermediate chamber 70g. This design improves the flexibility of the valve body 70.

Further, the fourth and fifth valve body openings 70d and 70e are inlets, and the sixth valve body opening 70f is an outlet. The two refrigerant flows into the valve body 70 from the fourth valve body opening 70d and the fifth valve body opening 70e, respectively, flows to the second intermediate chamber 70h along the fourth internal passage 704 and the fifth internal passage 705, respectively, and converges in one path in the second intermediate chamber 70h, then flows to the sixth valve body opening 70f along the sixth internal passage 706, and exits the valve body 70 from the sixth valve body opening 70f. It can be seen that the fourth and fifth valve body openings 70d and 70e, which are inlets, share the sixth valve body opening 70f, which is an outlet. Such a design helps to reduce the number of openings of the valve body 70, thereby making the valve body 70 compact.

The valve body 70 also has an eighth valve body opening 70M, the eighth valve body opening 70M in communication with the fifth internal passage 705. The refrigerant entering the valve body 70 from the eighth valve body opening 70M and the refrigerant entering the valve body 70 from the fifth valve body opening 70e join and flow to the second intermediate chamber 70h. This design improves the flexibility of the valve body 70.

As shown in fig. 17A, the valve body 70 also has a sensor opening 70n, and the first expansion valve 71 includes a sensor (not shown in the drawing). A sensor is mounted to the sensor opening 70n and at least partially positioned within the fourth interior passage 704 to sense refrigerant within the fourth interior passage 704.

In a particular embodiment, the refrigerant entering the valve body 70 from the first valve body opening 70a is high pressure, un-throttled refrigerant, and the refrigerant exiting the valve body 70 from the second valve body opening 70b and the third valve body opening 70c is low pressure, throttled refrigerant. The refrigerant that enters the valve body 70 from the fourth valve body opening 70d and the fifth valve body opening 70e is low-pressure refrigerant after being evaporated, and the refrigerant that exits the valve body 70 from the sixth valve body opening 70f is low-pressure refrigerant after being evaporated.

Referring to fig. 15A, 15B, 17A, 17B, the refrigerant valve assembly 7 further includes a first expansion valve 71 and a second expansion valve 72; valve body 70 also has a first valve chamber 70i and a second valve chamber 70j; first valve chamber 70i communicates with second internal passage 702, and second valve chamber 70j communicates with third internal passage 703; a first expansion valve 71 is provided in first valve chamber 70i for throttling the refrigerant passing through second internal passage 702; a second expansion valve 72 is disposed in second valve chamber 70j for throttling the refrigerant in third internal passage 703. Such a design enables the refrigerant valve assembly 7 to have at least two passages for throttling the refrigerant, improving the integration and compactness of the refrigerant valve assembly 7.

With continued reference to fig. 15A, 15B, 17A, 17B, the refrigerant valve assembly 7 further includes a shutoff valve 73; the valve body 70 also has a third valve chamber 70k, the third valve chamber 70k being in communication with a fifth mounting passage 705; a shut-off valve 73 is installed in the third installation chamber 70k for controlling the flow of the refrigerant in the fifth installation passage 705. Such a design enables the refrigerant valve assembly 7 to control the flow of coolant within the fifth mounting channel 705, thereby enabling the refrigerant valve assembly 7 to adapt to a variety of different operating modes of the vehicle thermal management system 900.

Referring to fig. 16A, 16B, first valve body opening 70a, first internal passage 701, first intermediate chamber 70g, sixth valve body opening 70f, sixth internal passage 706, and second intermediate chamber 70h are located on the same cross-section B-B. Such a design enables the first valve body opening 70a, the first internal passage 701, the first intermediate chamber 70g, the sixth valve body opening 70f, the sixth internal passage 706 and the second intermediate chamber 70h all to be located on the same section B-B, thereby making the valve body 70 compact in a direction perpendicular to the section B-B.

With continued reference to fig. 16A, 16B, the second internal passage 702 has a first segment 7021 that connects with the first intermediate chamber 70 g; third internal passage 703 has a second segment 7031 connected to first intermediate chamber 70 g; first segment 7021 and second segment 7031 lie on section B-B. Such a design allows at least a portion of the second internal passage 702 and the third internal passage 703 to also lie in the section B-B, thereby allowing the valve body 70 to be compact in a direction perpendicular to the section B-B.

With continued reference to fig. 16A, 16B, the fifth mounting channel 705 has a third segment 7051 that connects with the second intermediate chamber 70h; the third segment 7051 is located on section B-B; the fourth internal passage 704 is connected to and communicates with the third segment 7051; the fourth internal passage 704 extends perpendicular to the section B-B.

As shown in fig. 1, 2, 3, and 18, the thermal management module 90 further includes an intermediate heat exchanger 8, the intermediate heat exchanger 8 being connected to the valve body 70; the intermediate heat exchanger 8 has a first heat exchanger opening 8a, a second heat exchanger opening 8b, a third heat exchanger opening 8c and a fourth heat exchanger opening 8d; the first and third heat exchanger openings 8a, 8c define a first intermediate heat exchange channel 81; the second and fourth heat exchanger openings 8b, 8d define a second intermediate heat exchanger channel 82; the first heat exchanger opening 8a is communicated with the first valve body opening 70a, the second heat exchanger opening 8b is communicated with the sixth valve body opening 70f, the third heat exchanger opening 8c is communicated with the outlet 6b of the liquid storage dryer 6, and the fourth heat exchanger opening 8d is communicated with the inlet of the compressor 96. The refrigerant in the first intermediate heat exchange channel 81 exchanges heat with the refrigerant in the second intermediate heat exchanger channel 82.

Fig. 19-26 illustrate a plurality of operating modes of the vehicle thermal management system 900. In a first mode of operation of the vehicle thermal management system 900 shown in fig. 19, both the external electronic expansion valve 991 and the external shutoff valve 992 are in a closed state and no refrigerant flows in the external heat exchanger 98. No coolant flows in the heater core 91.

The refrigerant discharged from the compressor 96 enters the second heat exchanger 5 through the third refrigerant opening 5c, and exits the second heat exchanger 5 from the fourth refrigerant opening 5 d. In the second heat exchanger 5, the refrigerant condenses and releases heat. Thereafter, the refrigerant passes through the receiver-drier 6 and the first intermediate heat exchange passage 81 of the intermediate heat exchanger 8, and enters the valve body 70 through the first valve body opening 70a, flowing toward the first intermediate chamber 70g. The first expansion valve 71 is closed so that no refrigerant flows from the first intermediate chamber 70g in the first heat exchanger 1. The second expansion valve 72 opens and throttles the refrigerant from the first intermediate chamber 70g, and the throttled refrigerant enters the evaporator 94 and evaporates to absorb heat from the airflow passing through the evaporator 94, thereby generating a reduced temperature airflow to be delivered into the passenger compartment. The refrigerant flowing out of the evaporator 94 enters the valve body 70 from the fifth valve body opening 70 e. The shutoff valve 73 is in an open state, allowing the refrigerant to flow out of the valve body 70 through the second intermediate chamber 70h and the sixth valve body opening 70f. The refrigerant flowing out of the valve body 70 from the sixth valve body opening 70f passes through the second intermediate heat exchange passage 82 of the intermediate heat exchanger 8 and enters the discharge port of the compressor 96.

The coolant flowing out of the outlet of the first coolant pump 2211 enters the second heat exchanger 5 through the third coolant opening 5a and exits the second heat exchanger 5 through the fourth coolant opening 5 b. In the second heat exchanger 5, the heat released from the refrigerant is absorbed by the coolant, and the temperature of the refrigerant rises. The fourth coolant opening 5b communicates with the inlet of the coolant heating device 95, and the coolant leaving the second heat exchanger 5 enters the coolant heating device 95. An outlet of the coolant heating apparatus 95 communicates with the sixth port portion 21a 6. The coolant exiting the coolant heating apparatus 95 enters the coolant distribution assembly 2 from the sixth interface portion 21a6 and joins the coolant exiting the motor 93 under the control of the third coolant valve 2223. The merged coolant flows to the fourth port portion 21a4 under the control of the second coolant valve 2222, and flows out of the coolant distribution assembly 2 from the fourth port portion 21a4 toward the radiator 97. The outlet of the radiator 97 communicates with the second connecting port portion 21a2, the coolant exiting the radiator 97 enters the coolant distribution assembly 2 from the second connecting port portion 21a2, more specifically, the upstream passage chamber 20e ', a part of the upstream passage chamber 20e ' flows toward the third coolant opening 5a and enters the second heat exchanger 5 under the driving of the first coolant pump 2211, and another part of the upstream passage chamber 20e ' exits the coolant distribution assembly 2 through the second coolant pump 2212 and the third connecting port portion 21a3 and flows toward the electric motor 93. The first and second coolant valves 2221 and 2222 are provided such that no coolant flows in the first heat exchanger 1 and no coolant passes through the third coolant pump 2213 and the battery 92, so that the battery 92 does not exchange heat with the coolant.

In a second mode of operation of the vehicle thermal management system 900 shown in fig. 20, the first and second coolant valves 2221, 2222 are arranged such that there is coolant flow in the first and third coolant pumps 1, 2213, and the first expansion valve 71 is open such that there is refrigerant flow in the first heat exchanger 1 from the first intermediate cavity 70g, as compared to the first mode of operation. The refrigerant in the first heat exchanger 1 evaporates to absorb heat from the coolant in the first heat exchanger 1, so that the temperature of the coolant passing through the first heat exchanger 1 is lowered, and the lowered coolant can cool the battery 92. The distributor plate body 20 also has a fourth distribution opening 2d and a fifth distribution opening 2e. The coolant for cooling the cells 92 enters and exits the coolant distribution assembly 2 through the fourth distribution port 2d and the fifth distribution port 2e, wherein the distribution plate main body 20 further has a merging chamber 20h, and the merging chamber 20h communicates with the first distribution port 2a and the fifth distribution port 2e, respectively. The merging chamber 20h also communicates with the second valve mounting chamber 20d ″ -2.

In a third mode of operation of the vehicle thermal management system 900 shown in fig. 21, coolant leaving the coolant heating apparatus 95 at a higher temperature enters the coolant distribution assembly 2 from the sixth interface 21a6 and flows to the heater core 91 under the control of the third coolant valve 2223, as compared to the first mode of operation, so that the heater core 91 is able to heat the airflow after being cooled by the evaporator 94. The distribution plate body 20 also has a sixth distribution port 2f. The coolant passing through the heater core 91 enters and exits the coolant distribution assembly 2 via the first interface portion 21a1 and the sixth distribution port 2f. The coolant leaving the heater core 91 enters the coolant distribution block 2 through the first connection port portion 21a1 and then enters the upstream channel chamber 20e'. The coolant exiting the motor 93 no longer joins the coolant exiting the coolant heating device 95, but flows to the fourth interface portion 21a4 under the control of the second coolant valve 2222, and flows from the fourth interface portion 21a4, out of the coolant distribution assembly 2, to the radiator 97.

In a fourth mode of operation of the vehicle thermal management system 900 shown in fig. 22, the external electronic expansion valve 991 is in a closed state and the external shutoff valve 992 is in an open state, as compared to the first mode of operation. The shut-off valve 73 of the refrigerant valve assembly 7 is in a closed state so that the refrigerant flowing out of the evaporator 94 does not enter the valve body 70 but flows to the exterior intermediate heat exchanger 99, passes through the exterior intermediate heat exchanger 99, and then passes through the exterior shut-off valve 992 to flow to the exterior heat exchanger 98. The refrigerant leaving the exterior heat exchanger 98 passes through the exterior intermediate heat exchanger 99 and flows to the suction port of the compressor 96. In this mode of operation, the exterior heat exchanger 98 acts as an evaporator to absorb heat from the exterior airflow. The coolant with higher temperature leaving the coolant heating device 95 enters the coolant distribution assembly 2 from the sixth interface 21a6 and flows to the heater core 91 under the control of the third coolant valve 2223, so that the heater core 91 can heat the air flow cooled by the evaporator 94. The coolant leaving the electric motor 93 no longer joins the coolant leaving the coolant heating apparatus 95, but flows to the fourth interface portion 21a4 under the control of the second coolant valve 2222, and flows from the fourth interface portion 21a4, away from the coolant distribution assembly 2, to the radiator 97. The first and second coolant valves 2221 and 2222 are arranged so that no coolant flows in the first heat exchanger 1 and coolant passes through the battery 92 and the third coolant pump 2213. This causes the battery 92 to exchange heat with the coolant, and the battery 92 is cooled.

In a fifth mode of operation of the vehicle thermal management system 900 shown in fig. 23, the external electronic expansion valve 991 is in an open state and the external shutoff valve 992 is in a closed state, as compared to the fourth mode of operation. In this mode, the external electronic expansion valve 991 throttles the refrigerant entering the external heat exchanger 98, thereby achieving a lower evaporation temperature than in the fourth mode of operation. The exterior heat exchanger 98 functions as an evaporator in this mode.

In a sixth mode of operation of the vehicle thermal management system 900 shown in fig. 24, the second coolant valve 2222 is set such that no coolant flows in the radiator 97 as compared to the fourth mode of operation. The coolant leaving the motor 93 has been heated by the motor 93, and this heated coolant enters the coolant distribution assembly 2 via the fifth interface portion 21a5 and flows to the joining chamber 20h under the guidance of the second coolant valve 2222, then exits the coolant distribution assembly 2 through the first distribution port 2a, and then enters the first heat exchanger 1 through the first coolant opening 1a, and the second coolant valve 2221 is arranged to guide the coolant exiting the first heat exchanger 1 from the second coolant opening 1b into the upstream passage chamber 20e', and no coolant flows in the battery 92 and the third coolant pump 2213. The first expansion valve 71 is opened so that there is a flow of refrigerant from the first intermediate chamber 70g in the first heat exchanger 1. The refrigerant in the first heat exchanger 1 evaporates to absorb heat from the coolant in the first heat exchanger 1. The refrigerant leaving the first heat exchanger 1 flows through the second intermediate chamber 70h to the intermediate heat exchanger 8. The refrigerant leaving the intermediate heat exchanger 8 and the refrigerant leaving the external intermediate heat exchanger 99 are joined together and flow to the suction port of the compressor 96.

In the seventh mode of operation of the vehicle thermal management system 900 shown in fig. 25, no refrigerant flows in the refrigerant circuit. In the coolant loop, the coolant heating device 95 heats the coolant leaving the second heat exchanger 5 from the fourth coolant opening 5b, the heated coolant being split into two paths guided by the third coolant valve 2223, one path passing through the battery 92 to heat the battery, and the other path passing through the heater core 91 to heat the air flow passing through the heater core 91. The coolant leaving the battery 92 and the coolant leaving the heater core 91 enter the upstream passage chamber 20e', respectively, and flow toward the third coolant opening 5a of the second heat exchanger 5 under the suction of the first coolant pump 2211.

In the eighth mode of operation of the vehicle thermal management system 900 shown in fig. 26, no refrigerant flows in the refrigerant circuit and no coolant flows in the coolant heating apparatus 95 and the second heat exchanger 5. The coolant leaving the motor 93 passes through the battery 92 so that heat generated during operation of the motor 93 can be transferred to the battery 92, thereby enabling the co-worker battery 92, which is cooling down the motor 93, to warm up.

Although the present invention has been described with reference to the preferred embodiments, it is not intended to limit the present invention, and any person skilled in the art can make possible changes and modifications without departing from the spirit and scope of the present invention, and any modifications, equivalent changes and modifications made to the above embodiments by the technical spirit of the present invention fall within the scope of protection defined by the claims of the present invention.

Claims (10)

1. A coolant distribution assembly includes a distribution plate main body (20), a cover body (21), and a coolant distribution unit (22); characterized in that the distributor plate body (20) has a mounting cavity (20 d), a passage cavity (20 e) and a through hole (20 f); the through hole (20 f) communicates the mounting cavity (20 d) and the passage cavity (20 e);

the mounting cavity (20 d) having a mounting opening (205), the passage cavity (20 e) having a passage opening (206); the coolant distribution unit (22) is mounted to the mounting cavity (20 d) through the mounting opening (205); the cover (21) covers the passage opening (206).

2. The coolant distribution assembly of claim 1, characterized in that the coolant distribution unit (22) comprises a coolant pump (221), the mounting cavity (20 d) comprising a pump mounting cavity (20 d'); the coolant pump (221) is mounted to the pump mounting cavity (20 d'); the coolant pump (221) is used for enabling the pump installation cavity (20 d') to suck in and discharge the coolant;

wherein the through-hole (20 f) comprises an upstream through-hole (20 f ') and a downstream through-hole (20 f "), and the passage chamber (20 e) comprises an upstream passage chamber (20 e ') and a downstream passage chamber (20 e '); the pump installation chamber (20 d ') communicates with the upstream passage chamber (20 e ') through the upstream through hole (20 f '); the pump installation chamber (20 d') communicates with the downstream passage chamber (20 e ") through the downstream through hole (20 f");

the pump installation chamber (20 d ') is provided to suck the coolant from the upstream passage chamber (20 e ') through the upstream through hole (20 f ') and to discharge the coolant to the downstream passage chamber (20 e ") through the downstream through hole (20 f").

3. The coolant distribution assembly of claim 2, wherein the first bottom wall (201) of the pump mounting cavity (20 d') is recessed to form a scroll flow passage (201 a); wherein the swirl flow passage (201 a) widens gradually in a direction directed toward the downstream through hole (20 f').

4. The coolant distribution assembly of claim 2, wherein the pump mounting cavity (20 d ') includes a first pump mounting cavity (20d ' 1) and a second pump mounting cavity (20d ' 2); the coolant pump (221) includes a first coolant pump (2211) mounted to the first pump mounting cavity (20d '1) and a second coolant pump (2212) mounted to the second pump mounting cavity (20d' 2); the upstream through hole (20 f ') includes a first upstream through hole (20f ' 1) and a second upstream through hole (20f ' 2); the downstream through-hole (20 f ") includes a first downstream through-hole (20f '1) and a second downstream through-hole (20f' 2); the downstream channel chamber (20 e ") includes a first downstream channel chamber (20e '1) and a second downstream channel chamber (20e' 2);

the first pump mounting chamber (20d ' 1) is provided to suck a coolant from the upstream channel chamber (20 e ') through the first upstream through-hole (20f ' 1), and to discharge the coolant to the first downstream channel chamber (20e ' 1) through the first downstream through-hole (20f ' 1); the second pump mounting chamber (20d ' 2) is provided to suck a coolant from the upstream channel chamber (20 e ') through the second upstream through hole (20f ' 2), and to discharge the coolant to the second downstream channel chamber (20e ' 2) through the second downstream through hole (20f ' 2).

5. The coolant distribution assembly according to claim 4, characterized in that the interface portion (21 a) of the cover (21) includes a first interface portion (21 a 1) and a second interface portion (21 a 2); the first and second interface portions (21 a1, 21a 2) are in communication with the upstream channel cavity (20 e '), respectively, wherein the first interface portion (21 a 1) is disposed coaxially with the first upstream through hole (20f ' 1), and the second interface portion (21 a 2) is disposed coaxially with the second upstream through hole (20f ' 2).

6. The coolant distribution assembly of claim 4 wherein the coolant distribution unit (22) further comprises a coolant valve (222); said mounting chamber (20 d) further comprising a valve mounting chamber (20 d "); the coolant valve (222) is mounted to the valve mounting cavity (20 d ");

wherein the coolant valve (222) comprises a first coolant valve (2221); the valve installation chamber (20 d') includes a first valve installation chamber (20d 1); the first coolant valve (2221) is mounted to the first valve mounting chamber (20d)' -1;

the through-hole (20 f) includes a first intermediate through-hole (20 f-1); the upstream passage chamber (20 e ') communicates with the first valve installation chamber (20d)' -1) through the first intermediate through-hole (20 f-1);

the first intermediate through hole (20 f-1), the first upstream through hole (20f ' 1) and the second upstream through hole (20f ' 2) are distributed in the extending direction of the upstream channel cavity (20 e '); wherein the second upstream via (20f '2) is located between the first intermediate via (20 f-1) and the first upstream via (20f' 1).

7. The coolant distribution assembly of claim 1, wherein the cover (21) has an interface portion (21 a); the interface portion (21 a) communicates with the passage chamber (20 e).

8. The coolant distribution assembly of claim 7, wherein the same cover body (21) has a plurality of the connecting port portions (21 a).

9. A thermal management module, characterized by comprising a first heat exchanger (1), a second heat exchanger (5) and a coolant distribution assembly (2);

the first heat exchanger (1) has a first coolant opening (1 a) and a second coolant opening (1 b);

the second heat exchanger (5) having a third coolant opening (5 a) and a fourth coolant opening (5 b);

the coolant distribution assembly (2) has a first distribution port (2 a), a second distribution port (2 b), a third distribution port (2 c), a first intermediate through-hole (20 f-1), an upstream channel chamber (20 e') and a first downstream channel chamber (20e ″) 1;

the first coolant opening (1 a) communicates with the first distribution port (2 a); the second coolant opening (1 b) communicates with the second distribution port (2 b) and communicates with the upstream passage chamber (20 e') through the second distribution port (2 b) and the first intermediate through hole (20 f-1);

the third coolant opening (5 a) communicates with the third distribution port (2 c), and communicates with the first downstream passage chamber (20e ″) 1 through the third distribution port (2 c).

10. A vehicle thermal management system, comprising a heater core (91) and a thermal management module (90); the thermal management module (90) comprises a coolant distribution assembly (2); an outlet (91 a) of the heater core (91) communicates with a first interface portion (21 a 1) of the coolant distribution assembly (2), and communicates with an upstream passage chamber (20 e') of the coolant distribution assembly (2) through the first interface portion (21 a 1).

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