Fluid management valve and thermal management system

Abstract

The present disclosure provides a fluid management valve, comprising: a valve body having a valve port and a main opening; the valve element is provided with a main flow channel, is located in the valve body and is provided with a communicating position and a closing position relative to the valve body; when the valve element is located at the communicating position, the main runner communicates with the valve port and the main opening. When the valve element is located at the closed position, the valve port and the main opening are separated by the valve element. By means of the design, switching of the fluid management valve among different working modes can be achieved, the main opening has the throttling function, the design can replace a complex scheme of multiple stop valves and / or three-way valves in the prior art, the structure is simplified, assembling is convenient, cost is reduced, control is easy, and the product integration degree is improved.

Description

Technical Field

[0001] The present disclosure relates to a fluid management valve and a thermal management system including the fluid management valve. Background Art

[0002] The thermal management system of a vehicle usually includes a refrigerant circuit and a coolant circuit, wherein the refrigerant circuit is mainly formed by connecting components such as a compressor, a heat exchanger, and a throttling device through pipes. In order to achieve switching and control between multiple thermal management modes (such as refrigeration, heat pump, etc.), it is usually necessary to set multiple stop valves and / or three-way valves on the refrigerant circuit. However, such a system configuration will not only result in high cost of the vehicle thermal management system, a large number of parts, difficult assembly, and heavy weight, but also a relatively complex control strategy.

[0003] Therefore, how to design a fluid management valve to replace multiple shut-off valves and / or three-way valves to simplify the vehicle's thermal management system, reduce the cost of the entire system, make it simple to assemble, easy to control, and more compact and lightweight has become an urgent problem that needs to be solved. Summary of the invention

[0004] The purpose of the present disclosure is to provide a fluid management valve, a main opening and a valve port are arranged on the valve body, a main flow channel including a main body section and a throttling section is arranged on the valve core, and the main opening can be made to correspond to the main body section or the throttling section of the main flow channel by rotating the valve core, and selectively connected to the valve port, so that the fluid management valve can be switched between different working modes, and the main opening can have a throttling function. Specifically, the main opening can be adjusted between full opening, throttling and closing. This design can not only replace the complex structure of multiple stop valves and / or three-way valves in the prior art, but also has simple assembly and low cost, is also easy to control and can simplify the pipeline structure, thereby improving product integration.

[0005] The present disclosure provides a fluid management valve, comprising: a valve body, the valve body having a valve port and a main opening; a valve core, the valve core having a main flow channel; the valve core is located within the valve body and has a connecting position and a closing position relative to the valve body; when the valve core is located at the connecting position, the main flow channel connects the valve port and the main opening; when the valve core is located at the closing position, the valve port and the main opening are separated by the valve core.

[0006] The present invention discloses a fluid management valve having the above-mentioned design, which can realize switching between different working modes, and the main opening can be selectively connected to the valve port. This design has a simple structure, is easy to assemble, has a low cost, is easy to control, and can simplify the pipeline structure, thereby improving product integration.

[0007] In one or more embodiments, the main flow channel has a main body section and a throttling section; the connecting position includes a fully open position and a throttling position; when the valve core is located at the fully open position, the main body section directly connects the main opening and the valve port; when the valve core is located at the throttling position, the throttling section is located between the main opening and the main body section, so that the main body section is connected to the main opening via the throttling section.

[0008] The present invention can realize the throttling function of the main opening through the above-mentioned design of the main flow channel of the valve core, and the main opening can be adjusted between full opening, throttling and closing.

[0009] In one or more embodiments, the valve port includes a first valve port and a second valve port; the fully open position includes a first fully open position and a second fully open position; when the valve core is located at the first fully open position, the main opening is connected to the first valve port through the main body section; when the valve core is located at the second fully open position, the main opening is connected to the second valve port through the main body section.

[0010] In one or more embodiments, the valve core also has a central flow channel; the valve port also includes a third valve port and a fourth valve port; when the valve core is located at the first fully open position, the third valve port is connected to the fourth valve port through the central flow channel; when the valve core is located at the closed position, the third valve port is connected to the first valve port through the central flow channel; when the valve core is located at the second fully open position, the third valve port is connected to the first valve port through the central flow channel; when the valve core is located at the throttling position, the third valve port is connected to the first valve port through the central flow channel.

[0011] In one or more embodiments, the central flow channel is defined by an arcuate edge, a first straight edge, and a second straight edge to form a fan-shaped shape; wherein the third valve port is located at the intersection of the first straight edge and the second straight edge; during the movement of the valve core relative to the valve body, the fourth valve port and the first valve port move relative to the valve core along the arcuate edge.

[0012] The present disclosure can ensure that the third valve port of the valve body is always connected to the central flow channel through the above arrangement of the central flow channel.

[0013] In one or more embodiments, the valve core also has an edge flow channel; the valve port also includes a fifth valve port; when the valve core is located at the first fully open position, the fifth valve port is connected to the second valve port through the edge flow channel; when the valve core is located at the closed position, the fifth valve port is connected to the second valve port through the edge flow channel; when the valve core is located at the second fully open position, the fifth valve port is connected to the fourth valve port through the edge flow channel; when the valve core is located at the throttling position, the fifth valve port is connected to the fourth valve port through the edge flow channel.

[0014] In one or more embodiments, the edge flow channel is an arc-shaped cavity extending along the circumference of the fluid management valve.

[0015] In one or more embodiments, the valve body has a top wall, a bottom wall, and a side wall between the top wall and the bottom wall, the valve port is disposed on the bottom wall, and the main opening is disposed on the side wall.

[0016] In one or more embodiments, the central flow channel and the edge flow channel open on a bottom wall of the valve core.

[0017] In one or more embodiments, the main channel forms a first channel opening on the bottom wall of the valve core; the main channel forms a second channel opening on the side wall of the valve core; wherein the second channel opening includes a first opening area for defining the main body section and a second opening area for defining the throttling section; when the valve core is located in the fully open position, the first opening area at least partially overlaps with the main opening; when the valve core is located in the throttling position, the second opening area at least partially overlaps with the main opening.

[0018] The present invention adopts the above-mentioned design of the flow channel on the valve core and the valve port and main opening on the valve body, and can realize the switching of the four working modes of the fluid management valve by rotating the valve core between multiple positions, which is easy to control and improves the integration of the product.

[0019] In one or more embodiments, the fluid management valve further includes a sealing member disposed between the valve body and the valve core.

[0020] The present invention can effectively avoid the problem of internal leakage caused by the cross-flow of fluid between the valve core and the valve body by arranging a sealing member between the valve body and the valve core.

[0021] In one or more embodiments, the throttling section is a groove extending from a connection with the main body section toward a direction away from the main body section.

[0022] In one or more embodiments, the groove gradually decreases in a direction away from the main body section.

[0023] In one or more embodiments, the fluid management valve further includes an actuator connected to the valve core to drive the valve core to rotate between the communication position and the closing position.

[0024] The present disclosure also provides a thermal management system for a vehicle, comprising the aforementioned fluid management valve.

[0025] The thermal management system disclosed in the present invention can simplify the system structure and control strategy and reduce the cost of the entire system by including the fluid management valve of the aforementioned structure. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 A perspective view of a fluid management valve according to an embodiment of the present disclosure is shown;

[0027] Figure 2 A perspective view of a fluid management valve according to an embodiment of the present disclosure at another viewing angle is shown, wherein the arrangement of the main opening and the first to fifth valve ports is shown;

[0028] Figure 3 A perspective view of a valve body according to an embodiment of the present disclosure is shown;

[0029] Figure 4 A perspective view of a valve core according to an embodiment of the present disclosure is shown;

[0030] Figure 5 A three-dimensional view of a valve core according to an embodiment of the present disclosure at another viewing angle is shown;

[0031] Figure 6 A cross-sectional view of a fluid management valve according to an embodiment of the present disclosure in a first working mode is shown, wherein the valve core is in a first fully open position;

[0032] Figure 7 A cross-sectional view of a fluid management valve according to an embodiment of the present disclosure in a second working mode is shown, wherein the valve core is in a closed position;

[0033] Figure 8 A cross-sectional view of a fluid management valve according to an embodiment of the present disclosure in a third working mode is shown, wherein the valve core is in a second fully open position;

[0034] Fig. 9 A cross-sectional view of a fluid management valve according to an embodiment of the present disclosure in a fourth working mode is shown, wherein the valve core is in a throttling position;

[0035] Fig.10 A connection diagram of a thermal management system according to an embodiment of the present disclosure is shown;

[0036] Fig.11A connection diagram of a thermal management system according to another embodiment of the present disclosure is shown;

[0037] Fig.12 A schematic diagram showing the connection of a thermal management system according to another embodiment of the present disclosure when operating in AC mode;

[0038] Fig.13 A schematic diagram showing the connection of a thermal management system according to another embodiment of the present disclosure when operating in a self-circulation mode;

[0039] Fig.14 A schematic diagram showing the connection of a thermal management system according to another embodiment of the present disclosure when operating in a dehumidification mode;

[0040] Fig.15 A schematic diagram showing the connection of a thermal management system according to another embodiment of the present disclosure when operating in a heat pump mode;

[0041] Fig.16 A connection diagram of a thermal management system according to another embodiment of the present disclosure is shown;

[0042] Fig.17 A connection diagram of a thermal management system according to yet another embodiment of the present disclosure when operating in a delta cycle mode is shown. DETAILED DESCRIPTION

[0043] The following describes the implementation of the present disclosure through specific embodiments. Those skilled in the art can easily understand other advantages and effects of the present disclosure from the contents disclosed in this specification.

[0044] It should be noted that the structures, proportions, sizes, etc. illustrated in the drawings attached to this specification are only used to match the contents disclosed in the specification for the understanding and reading of those skilled in the art, and are not used to limit the limiting conditions for the implementation of the present disclosure, so they have no substantial technical significance. Any structural modification, change in proportional relationship, or adjustment of size, without affecting the effects and purposes that can be achieved by the present disclosure, should still fall within the scope of the technical contents disclosed by the present disclosure. At the same time, the terms such as "on" and "one" quoted in this specification are only for the convenience of description, and are not used to limit the scope of the implementation of the present disclosure. The change or adjustment of their relative relationship should also be regarded as the scope of the implementation of the present disclosure without substantially changing the technical contents.

[0045] In order to more clearly understand the present disclosure, various embodiments of the present disclosure are described in detail below with reference to the accompanying drawings.

[0046] The present disclosure provides a fluid management valve 1, see Figures 1 to 4The fluid management valve 1 includes a valve body 10 having a valve port and a main opening 93 , and a valve core 20 located inside the valve body 10 and rotatable relative to the valve body 10 between a plurality of positions.

[0047] The valve body 10 is generally cylindrical and has a top wall 101, a bottom wall 102, and a side wall 103 between the top wall 101 and the bottom wall 102. The valve port of the valve body 10 is arranged on the bottom wall 102, and the main opening 93 is arranged on the side wall 103. Such an arrangement allows the valve port to be directly connected to the flow channel on the flow channel plate (not shown), simplifies the pipeline arrangement, and optimizes the system structure.

[0048] In this embodiment, the valve body 10 may have five valve ports, namely a first valve port 95, a second valve port 96, a third valve port 94, a fourth valve port 91, and a fifth valve port 92. Figure 2 and Figure 3 As shown, at least two valve ports or at least one valve port and the main opening 93 can be connected via the flow channel of the valve core 20 to form a fluid passage. The valve body 10 can be provided with an opening on the top wall 101 for receiving the valve core 20, and the valve core 20 can be fixed in the valve body 10 by a flange installed on the top wall 101.

[0049] See also Figure 4 and Figure 5 The valve core 20 may be substantially cylindrical and also have a top wall 201, a bottom wall 202, and a circumferential side wall 203 between the top wall 201 and the bottom wall 202, so that it can rotate relative to the valve body 10. In this embodiment, the valve core 20 may be in a communication position (i.e., a position where the valve port and the main opening 93 may be communicated by the flow channel of the valve core 20) and a closed position (i.e., a position where the valve port and the main opening 93 are separated by the valve core 20, such as Figure 7 As shown), the connecting position includes a fully open position (at which time the main opening 93 is in a fully open state) and a throttle position (at which time the main opening 93 is in a throttle state, as shown Fig. 9 As shown), the fully open position includes the first fully open position (as shown Figure 6 as shown) and a second fully open position (as shown Figure 8 The valve core 20 further includes a plurality of flow channels, so that the valve core 20 can connect at least two valve ports or at least one valve port with the main opening 93 when in the above-mentioned positions.

[0050] Please continue to see Figure 4 and Figure 5 The valve core 20 includes a main flow channel 23. When the valve core 20 is in the communication position (such as Figure 6 and Figure 8), the main flow channel 23 is used to connect the valve port and the main opening 93. Specifically, the main flow channel 23 includes a main body section 230 and a throttling section 231 arranged on one side of the main body section 230 along the circumferential direction, and has a first flow channel opening 232 opened on the bottom wall 202 and a second flow channel opening 233 opened on the side wall 203, and the first and second flow channel openings 232 and 233 can overlap the valve port and the main opening 93 respectively to achieve the connection between the two. In detail, the second flow channel opening 233 includes a first opening area 2331 for defining the main body section 230 and a second opening area 2332 for defining the throttling section 231. That is to say, the first opening area 2331 is the opening area of ​​the main body section 230 on the side wall 203, and the second opening area 2332 is the opening area of ​​the throttling section 231 on the side wall 203, and the two opening areas 2331 and 2332 are connected to each other on the side wall.

[0051] In this embodiment, the main body section 230 of the main flow channel 23 may be substantially an arc-shaped cavity extending along the circumference of the valve core 20. The throttling section 231 is a groove extending from the connection with the main body section 230 toward the direction away from the main body section 230. Preferably, the groove may gradually change in the direction away from the main body section 230 (that is, in the direction away from the main body section 230, the size of the second opening area 2332 of the throttling section 231 in the direction of the central axis of the valve core 20 gradually changes), for example, gradually shrinks, so that the valve core 20 can accurately control the throttling amount of the main opening 93 corresponding to the throttling section 231 when the valve core 20 is in different positions. It should be noted that the maximum size of the second opening area 2332 in the direction of the central axis of the valve core 20 is less than or equal to the size of the first opening area 2331 in the above-mentioned central axis direction, so that the main opening 93 corresponding to the second opening area 2332 can have a throttling effect. Of course, the present disclosure is not limited to the above-mentioned shape of the main flow channel 23 , as long as the valve port and the main opening 93 can be connected, and the throttling section 231 of the main flow channel 23 can adjust the flow of the main opening 93 .

[0052] Please refer to Figure 5 The valve core 20 may further include a central flow channel 21. When the valve core 20 is in the first fully open position (eg Figure 6 ), the central flow channel 21 is used to connect the third valve port 94 and the fourth valve port 91, and when the valve core 20 is in the closed position (as shown in FIG. Figure 7 As shown), the second fully open position (as shown Figure 8 as shown) and the throttle position (as shown Fig. 9 As shown in FIG. 1 , the central flow channel 21 is used to connect the third valve port 94 and the first valve port 95. The central flow channel 21 is opened on the bottom wall 202 of the valve core 20 to connect the above valve ports.

[0053] In this embodiment, the central flow channel 21 is generally a fan-shaped cavity. Viewed from the bottom wall 202 of the valve core 20, the central flow channel 21 is a fan-shaped cavity surrounded / defined by the arc-shaped edge 210, the first straight edge 211, and the second straight edge 212, wherein the third valve port 94 of the valve body 10 corresponds to the intersection of the first straight edge 211 and the second straight edge 212, so that during the rotation of the valve core 20, the third valve port 94 can always be connected to the central flow channel 21, while the fourth valve port 91 and the first valve port 95 move along the arc-shaped edge 210 relative to the valve core 20, so that when the valve core 20 is in different positions, the third valve port 94 can selectively connect to the fourth valve port 91 or the first valve port 95.

[0054] Please continue to see Figure 5 The valve core 20 may further include an edge flow channel 22. When the valve core 20 is in the first fully open position (eg Figure 6 as shown) and the closed position (as Figure 7 As shown), the edge flow channel 22 is used to connect the second valve port 96 and the fifth valve port 92; and when the valve core is in the second fully open position (as shown Figure 8 ) and throttle position (as shown Fig. 9 ), the edge flow channel 22 is used to connect the fourth valve port 91 and the fifth valve port 92. The edge flow channel 22 is opened on the bottom wall 202 of the valve core 20 to connect the above valve ports.

[0055] In this embodiment, the edge flow channel 22 may be substantially an arc-shaped cavity extending along the fluid management valve 1, especially along the circumference of the valve core 20. Of course, the present disclosure is not limited to the specific structure of each of the above-mentioned flow channels, as long as it can achieve that when the valve core 20 is in different positions, at least two valve ports can be connected or at least one valve port can be connected to the main opening 93.

[0056] Please return to see Figure 1 The fluid management valve 1 further includes an actuator 30 for driving the valve core 20 to rotate between different positions. In one embodiment, the actuator 30 may include a stepping motor to control the rotation angle of the valve core 20. Specifically, a driving part may be provided on the top wall 201 of the valve core 20, and a flange fixed on the top wall 101 of the valve body 10 is provided with a through hole exposing the driving part. The output shaft of the actuator 30 is matched with the driving part of the valve core 20 via the through hole to drive the valve core 20 to rotate relative to the valve body 10.

[0057] In addition, the fluid management valve 1 of the present disclosure may also include a seal, which is disposed between the valve body 10 and the valve core 20. Specifically, the seal is, for example, a plurality of sealing rings, which may be respectively disposed between each valve port of the valve body 10 and the valve core 20 and between the main opening 93 and the valve core 20, so as to effectively avoid the problem of internal leakage caused by the cross-flow of the fluid between the valve core 20 and the valve body 10. Of course, the seal of the present disclosure is not limited to the above structure, as long as it can achieve the sealing between the valve body 10 and the valve core 20.

[0058] The following will combine Figures 4 to 9 The four working modes of the fluid management valve 1 are specifically described.

[0059] Figure 6 2 shows the flow state of the fluid management valve 1 when the valve core 20 is in the first fully open position, that is, the first working mode of the fluid management valve 1. Figure 4 , Figure 5 and Figure 6 , when the valve core 20 is in the first fully open position: the main opening 93 of the valve body 10 is connected to the second flow channel opening 233 of the main flow channel 23 of the valve core 20 (especially, its first opening area 2331, so that the main opening 93 is in a fully open state), and the first flow channel opening 232 of the main flow channel 23 is connected to the first valve port 95, that is, the main opening 93 of the valve body 10 is connected to the first valve port 95 via the main body section 230 of the main flow channel 23 of the valve core 20, and the fluid can flow into the fluid management valve 1 from the main opening 93 and flow out from the first valve port 95, as shown in FIG. Figure 6 As shown by the arrow above; the third valve port 94 and the fourth valve port 91 of the valve body 10 are both connected to the opening of the central flow channel 21 of the valve core 20, that is, the third valve port 94 is connected to the fourth valve port 91 via the central flow channel 21 of the valve core 20, and the fluid can flow into the fluid management valve 1 from the third valve port 94 and flow out from the fourth valve port 91, as shown in FIG. Figure 6 As shown by the arrow on the lower left; at the same time, the second valve port 96 and the fifth valve port 92 of the valve body 10 are both connected to the opening of the edge flow channel 22 of the valve core 20, that is, the second valve port 96 is connected to the fifth valve port 92 via the edge flow channel 22, and the fluid can flow into the fluid management valve 1 from the second valve port 96 and flow out from the fifth valve port 92, as shown in FIG. Figure 6 As shown by the arrow on the lower right side, it can be seen that when the valve core 20 is in the first fully open position, the main opening 93 of the valve body 10 is connected to the first valve port 95, and the main opening 93 is in a fully open state, the third valve port 94 is connected to the fourth valve port 91, and the second valve port 96 is connected to the fifth valve port 92, and the fluid management valve 1 is in the first working mode.

[0060] Figure 7The flow state of the fluid management valve 1 when the valve core 20 is in the closed position is shown, that is, the second working mode of the fluid management valve 1. As shown in the figure, when the valve core 20 is in the closed position: the first valve port 95 and the third valve port 94 of the valve body 10 are both connected to the opening of the central flow channel 21 of the valve core 20, that is, the third valve port 94 is connected to the first valve port 95 via the central flow channel 21, and the fluid can flow into the fluid management valve 1 from the third valve port 94 and flow out from the first valve port 95. Figure 7 As shown by the arrow above; at the same time, the second valve port 96 and the fifth valve port 92 of the valve body 10 are both connected to the opening of the edge flow channel 22 of the valve core 20, that is, the second valve port 96 is connected to the fifth valve port 92 via the edge flow channel 22, and the fluid can flow into the fluid management valve 1 from the second valve port 96 and flow out from the fifth valve port 92, as shown in FIG. Figure 7 As shown by the arrow below; in addition, the main flow channel 23 of the valve core 10 is only connected to the main opening 93 of the valve body 10, so that the main opening 93 is not connected to other valve ports (that is, the main opening 93 is in a closed state). It can be seen that when the valve core 20 is in the closed position, the first valve port 95 of the valve body is connected to the third valve port 94, the second valve port 96 is connected to the fifth valve port 92, the main opening 93 is in a closed state, and the fluid management valve 1 is in the second working mode.

[0061] Figure 8 2 shows the flow state of the fluid management valve 1 when the valve core 20 is in the second fully open position, that is, the third working mode of the fluid management valve 1. Figure 4 , Figure 5 and Figure 8 , when the valve core 20 is in the second fully open position: the main opening 93 of the valve body 10 is connected to the second flow channel opening 233 of the main flow channel 23 of the valve core 20 (especially, its first opening area 2331, so that the main opening 93 is in a fully open state), and the first flow channel opening 232 of the main flow channel 23 is connected to the second valve port 96, that is, the main opening 93 of the valve body 10 is connected to the second valve port 96 via the main body section 230 of the main flow channel 23 of the valve core 20, and the fluid can flow into the fluid management valve 1 from the second valve port 96 and flow out from the main opening 93, as shown in FIG. Figure 8 As shown by the arrow on the upper right; the third valve port 94 and the first valve port 95 of the valve body 10 are both connected to the opening of the central flow channel 21 of the valve core 20, that is, the third valve port 94 is connected to the first valve port 95 via the central flow channel 21 of the valve core 20, and the fluid can flow into the fluid management valve 1 from the third valve port 94 and flow out from the first valve port 95, as shown in FIG. Figure 8 As shown by the arrow on the upper left; at the same time, the fourth valve port 91 and the fifth valve port 92 of the valve body 10 are both connected to the opening of the edge flow channel 22 of the valve core 20, that is, the fourth valve port 91 is connected to the fifth valve port 92 via the edge flow channel 22, and the fluid can flow into the fluid management valve 1 from the fourth valve port 91 and flow out from the fifth valve port 92, as shown in FIG. Figure 8As shown by the arrow below. It can be seen that when the valve core 20 is in the second fully open position, the main opening 93 of the valve body 10 is connected to the second valve port 96, and the main opening 93 is in a fully open state, the third valve port 94 is connected to the first valve port 95, and the fourth valve port 91 is connected to the fifth valve port 92, and the fluid management valve 1 is in the third working mode.

[0062] Fig. 9 2 shows the flow state of the fluid management valve 1 when the valve core 20 is in the throttling position, that is, the fourth working mode of the fluid management valve 1. Figure 4 , Figure 5 and Fig. 9 When the valve core 20 is in the throttling position: the main opening 93 of the valve body 10 is connected to the second flow channel opening 233 of the main flow channel 23 of the valve core 20 (especially, its second opening area 2332 makes the main opening 93 in the throttling state), and the first flow channel opening 232 of the main flow channel 23 is connected to the second valve port 96, that is, the main opening 93 of the valve body 10 is connected to the second valve port 96 via the throttling section 231 and the main body section 230 of the main flow channel 23 of the valve core 20, and the fluid can flow into the fluid management valve 1 from the second valve port 96 and flow out from the main opening 93, as shown in FIG. Figure 8 As shown by the arrow in the upper right corner; the third valve port 94 and the first valve port 95 of the valve body 10 are both connected to the opening of the central flow channel 21 of the valve core 20, that is, the third valve port 94 is connected to the first valve port 95 via the central flow channel 21 of the valve core 20, and the fluid can flow into the fluid management valve 1 from the third valve port 94 and flow out from the first valve port 95, as shown in FIG. Figure 8 As shown by the arrow on the upper left; at the same time, the fourth valve port 91 and the fifth valve port 92 of the valve body 10 are both connected to the opening of the edge flow channel 22 of the valve core 20, that is, the fourth valve port 91 is connected to the fifth valve port 92 via the edge flow channel 22, and the fluid can flow into the fluid management valve 1 from the fourth valve port 91 and flow out from the fifth valve port 92, as shown in FIG. Figure 8 As shown by the arrow below. It can be seen that when the valve core 20 is in the throttling position, the second valve port 96 of the valve body 10 is connected to the main opening 93, and the main opening 93 is in the throttling state, the third valve port 94 is connected to the first valve port 95, and the fourth valve port 91 is connected to the fifth valve port 92, and the fluid management valve 1 is in the fourth working mode.

[0063] It should be noted that the fluid management valve 1 is generally referred to as the fourth working mode when the main opening 93 is in the throttling state. Of course, the fourth working mode of the fluid management valve 1 is not limited to the above Fig. 9In the valve core position shown, for example, when the valve core 20 rotates to the point where the second opening area 2332 of the second flow channel opening 233 of the main flow channel 23 partially overlaps the main opening 93, the main opening 93 is in a throttling state, and the fluid management valve 1 is in the fourth working mode, with only a different throttling amount of the second valve port 93. In this embodiment, the second valve port 93 can be adjusted between 100% (fully open) and 0% (closed).

[0064] It can be seen that the fluid management valve 1 in the present disclosure can realize the switching between different working modes of the fluid management valve 1 by changing the position of the valve core 20 (for example, rotating the valve core 20), and the main opening 93 can be adjusted between full open, throttling and closing. It is easy to control and can replace the combination of multiple three-way valves and / or stop valves in the prior art. It is simple to assemble, and can simplify the pipeline structure, improve the integration, and reduce the occupied space.

[0065] Although the above-mentioned embodiment of the present disclosure is described with the valve body 10 having five valve ports and one main opening 93, the main opening 93 having a throttling function, the valve core 20 having three flow channels, and the fluid management valve 1 having four working modes, the present disclosure is not limited thereto. For example, the valve body 10 may have one, two, three, four or more valve ports in combination with one main opening 93, and the valve ports may be set to have a throttling function as needed, and the valve core 20 may be in other positions and may have other flow channels, so that the fluid management valve 1 is in other working modes (for example, the fifth working mode: the main opening 93 is connected to the third valve port 94; the fourth valve port 91 is connected to the fifth valve port 92; and the first valve port 95 and the second valve port 96 are not connected to other valve ports; or the sixth working mode: only the third valve port 94 is connected to the fifth valve port 92), as long as the valve core 20 can connect at least two valve ports or at least one valve port and the main opening 93 when in different positions, it is possible to realize the switching between different working modes of the fluid management valve 1.

[0066] In addition, the present disclosure Figures 6 to 9 The arrows representing the flow channels are not intended to limit the flow direction of the fluid, but are only for ease of explanation. For example, the fluid may also flow in the opposite direction of the arrow as long as the area passed by the arrow is connected.

[0067] The present disclosure also provides a thermal management system including the above-mentioned fluid management valve. Figures 10 to 17 To illustrate various embodiments of the thermal management system. It should be noted that the thermal management system of each embodiment of the present disclosure only shows the refrigerant circuit (for example, the refrigerant circulating is Freon), and the coolant circuit is omitted. Moreover, the fluid management valve in the thermal management system of the present disclosure only illustrates the valve ports and main openings included, but does not show the specific positional relationship between each valve port and the main opening.

[0068] See also Fig.10, which shows a connection diagram of a thermal management system according to an embodiment of the present disclosure. As shown in the figure, the thermal management system includes the above-mentioned fluid management valve 1, a first fluid circuit C1, a second fluid circuit C2 and a third fluid circuit C3.

[0069] The first fluid circuit C1 is provided with a compressor 2 and a first heat exchanger 801 in sequence along the flow direction of the fluid, wherein the upstream of the compressor 2 is connected to the fifth valve port 92 of the fluid management valve 1, and the downstream of the first heat exchanger 801 is connected to the third valve port 94 of the fluid management valve 1, that is, the two ends of the first fluid circuit C1 are respectively connected to the fifth valve port 92 and the third valve port 94 of the fluid management valve 1. Specifically, the air intake of the compressor 2 is connected to the fifth valve port 92, the exhaust hole of the compressor 2 is connected to the air intake of the first heat exchanger 801, and the exhaust port of the first heat exchanger 81 is connected to the third valve port 94. In this embodiment, the first heat exchanger 801 can be a built-in condenser to convert the compressed gaseous refrigerant into liquid and dissipate the released heat to the surrounding environment to produce a heating effect.

[0070] In one embodiment, the first fluid circuit C1 may further include a gas-liquid separator 3 disposed between the fifth valve port 92 and the air intake port of the compressor 2 for storing unevaporated liquid refrigerant and discharging gaseous refrigerant to prevent the liquid refrigerant from flowing into the compressor.

[0071] The second fluid circuit C2 is provided with a second heat exchanger 802, and the pipelines on both sides of the second heat exchanger 802 are respectively connected to the fourth valve port 91 and the main opening 93 of the fluid management valve 1. The second flow channel circuit C2 may also be provided with a second throttling device 1012, and the second throttling device 1012 is located between the second heat exchanger 802 and the main opening 93. In this embodiment, the second heat exchanger 802 may be an evaporative condenser, and the flow direction of the refrigerant in the second fluid circuit C2 may be switched according to different modes of the thermal management system. The second throttling device 1012 may be an expansion ball valve, which has three states: fully open, throttling and closed. Specifically, when the second throttling device 1012 is in a fully open state, the refrigerant is not throttled and reduced in pressure when passing through the second throttling valve device 1012, that is, the refrigerant passes through the second throttling device 1012 in a non-throttling state; when the second throttling device 1012 is in a throttling state, the refrigerant is throttled and reduced in pressure when passing through the second throttling device 1012; when the second throttling device 1012 is in a closed state, the refrigerant cannot pass through the second throttling device 1012.

[0072] The third fluid circuit C3 is provided with a first throttling device 1011 and a third heat exchanger 803 in sequence along the flow direction of the fluid, wherein the upstream of the first throttling device 1011 is connected to the first valve port 95 of the fluid management valve 1, and the downstream of the third heat exchanger 803 is connected to the second valve port 96 of the fluid management valve 1, that is, the two ends of the third fluid circuit C3 are connected to the first valve port 95 and the second valve port 96 of the fluid management valve 1, respectively. In this embodiment, the third heat exchanger 803 can be an evaporator, which is used to convert liquid refrigerant into gaseous state and absorb heat from the surrounding environment to produce a cooling effect; and along the flow direction of the air (the direction of the hollow arrow in the figure), the third heat exchanger 803 is located upstream of the first heat exchanger 801. The first throttling device 1011 can also be an expansion ball valve, which has three states: fully open, throttling and closed. Specifically, when the first throttling device 1011 is in a fully open state, the refrigerant is not throttled and reduced in pressure when passing through the first throttling device 1011, that is, the refrigerant passes through the first throttling device 1011 in a non-throttling state; when the first throttling device 1011 is in a throttling state, the refrigerant is throttled and reduced in pressure when passing through the first throttling valve device 1011; when the first throttling device 1011 is in a closed state, the refrigerant cannot pass through the first throttling device 1011.

[0073] Please continue to see Fig.10 , the thermal management system may also include a first branch B1. The first branch B1 is sequentially provided with a third throttling device 1013 and a fourth heat exchanger 804 along the flow direction of the fluid, and the first branch B1 is connected in parallel with the third loop C3. Specifically, the upstream of the third throttling device 1013 is connected to the pipeline between the first valve port 95 and the first throttling device 1011, and the downstream of the fourth heat exchanger 804 is connected to the pipeline between the second valve port 96 and the third heat exchanger 803. For example, a first junction may be provided on the pipeline between the first valve port 95 and the first throttling device 1011, and a second junction may be provided on the pipeline between the second valve port 96 and the third heat exchanger 803, the upstream of the third throttling device 1013 is connected to the first junction, and the downstream of the fourth heat exchanger 804 is connected to the second junction. In this embodiment, the fourth heat exchanger 804 is a direct cooling plate, which can be attached to the battery to cool the battery. The third throttling device 1013 can be an expansion ball valve with three states: fully open, throttling and closed. The flow conditions of the expansion ball valve in different states are as described above and will not be repeated here.

[0074] It should be noted that the fluid management valve 1 in the thermal management system described in this embodiment has the first working mode, the second working mode and the third working mode mentioned above, that is, the main opening 93 is either fully open or closed, and does not need to have a throttling function.

[0075] The following will describe different embodiments of the thermal management system of the present disclosure. For simplicity, the following will mainly describe the differences between the embodiments, and the similarities will not be repeated. In addition, the same elements in the embodiments of the present disclosure are marked with the same reference numerals to facilitate mutual comparison between the embodiments.

[0076] See also Fig.11 , which shows a connection diagram of a thermal management system according to another embodiment of the present disclosure. Fig.10 The difference of the thermal management system shown is that the second throttling device 1012 is omitted in the second fluid circuit C2, and the fluid management valve 1 has four working modes, namely, the first to fourth working modes. Specifically, the fluid management valve 1 in this embodiment has not only the first working mode, the second working mode and the third working mode described above, but also the fourth working mode described above, that is, the main opening 93 of the fluid management valve 1 can be in a fully open state, a closed state and a throttling state. When the main opening 93 is in a throttling state, the main opening 93 has a throttling function, so that the second throttling device 1012 in the second fluid circuit C2 can be omitted.

[0077] In order to better understand the present invention, the operation mode of the thermal management system disclosed in the present invention is described below with reference to the accompanying drawings. It should be noted that: Fig.11 The connection relationship of the thermal management system shown is similar to Fig.10 is roughly the same, except that Fig.10 The function of the second throttling device 1012 is incorporated into the main opening 93 of the fluid management valve 1, so Fig.10 and Fig.11 The thermal management system shown in the figure operates in the same way. Fig.11 In addition, for the sake of comparison, the following description will take the compressor as the starting point to explain the refrigerant circuit in each operating mode.

[0078] See also Fig.12 , which shows the AC mode (also known as the cabin cooling mode) of the thermal management system. In this mode, the fluid management valve 1 of the thermal management system is in the first working mode (i.e., the third valve port 94 is connected to the fourth valve port 91; the main opening 93 (in the fully open state) is connected to the first valve port 95; the second valve port 96 is connected to the fifth valve port 92), and the air entering the cabin can be cooled by the third heat exchanger 803 (evaporator) to achieve cabin cooling.

[0079] Specifically, in the first fluid circuit C1, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor 2 flows through the first heat exchanger 801 (built-in condenser), the third valve port 94 and the fourth valve port 91 of the fluid management valve 1 in sequence to reach the second fluid circuit C2, wherein the first heat exchanger 801 does not perform heat exchange but is only used to connect the fluid; then the refrigerant is condensed into liquid through the second heat exchanger 802 (evaporative condenser) in the second fluid circuit C2, and passes through the main opening 93 and the first valve port 95 of the fluid management valve 1 to reach the third fluid circuit C3; then it passes through the first throttling device 1011 of the third fluid circuit C3, and enters the third heat exchanger 803 (evaporator) after throttling and reducing the pressure through the first throttling device 1011, and the refrigerant evaporates and absorbs heat at the third heat exchanger 803 to cool the air in the surrounding environment flowing through the third heat exchanger 803 (as shown by the hollow arrow in the figure), and the cooled air enters the cabin to achieve cabin cooling. In addition, most of the refrigerant flowing through the third heat exchanger 803 is converted into gas, and the refrigerant continues to flow through the second valve port 96 and the fifth valve port 92 of the fluid management valve 1, and flows back to the gas-liquid separator 3 of the first fluid circuit C1. The liquid refrigerant is stored in the gas-liquid separator 3, and the gaseous refrigerant enters the suction port of the compressor 2 and is compressed into a high-temperature and high-pressure gaseous refrigerant, thus completing a complete cycle of the refrigerant circuit in this mode.

[0080] In AC mode, the battery cooling function can also be selectively turned on. Specifically, the third throttling device 1013 in the first branch B1 is turned on, so that part of the refrigerant flows through the third throttling device 1013 and then throttles and reduces pressure, and enters the fourth heat exchanger 804 (direct cooling plate) to evaporate and absorb heat, thereby achieving battery cooling.

[0081] See also Fig.13 , which shows the self-circulation mode of the thermal management system. The self-circulation mode is an intermediate transition mode between the AC mode and the heat pump mode. When the thermal management system switches from the AC mode to the heat pump mode, the refrigerant in the second fluid circuit C2 will switch to reverse flow, that is, the fluid directly switches, which may cause the fluid management valve 1 to be unable to switch normally between different working modes. In order to solve this defect, the thermal management system of the present invention adds a self-circulation mode, which can put the refrigerant in the second circuit C2 in a paused state before the thermal management system switches to the heat pump mode, thereby avoiding the problem of the fluid management valve 1 being unable to switch normally due to direct fluid reversal.

[0082] In the self-circulation mode, the fluid management valve 1 of the thermal management system is in the second working mode (i.e., the third valve port 94 is connected to the first valve port 95; the second valve port 96 is connected to the fifth valve port 92; and the main valve port 93 and the fourth valve port 91 are not connected) so that the refrigerant in the second circuit C2 is in a paused state.

[0083] Specifically, in the first fluid circuit C1, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor 2 flows through the first heat exchanger 801 (built-in condenser), the third valve port 94 and the first valve port 95 of the fluid management valve 1 in sequence, and reaches the third fluid circuit C3; then the refrigerant passes through the first throttling device 1011 of the third fluid circuit C3 and the third heat exchanger 803 (evaporator), reaches the fluid management valve 1, and flows back to the gas-liquid separator 3 of the first fluid circuit C1 through the second valve port 96 and the fifth valve port 92, and flows into the compressor 2. It can be seen that in this mode, the refrigerant does not pass through the second fluid circuit C2, that is, the refrigerant in the second circuit C2 is in a suspended state. In addition, it should be noted that since the self-circulation mode belongs to the intermediate transition mode between the AC mode and the heat pump mode, in this mode, the first throttling device 1011 can be fully open, and the first heat exchanger 801 and the second heat exchanger 802 can only play the role of fluid communication without cooling or heating the surrounding environment.

[0084] See also Fig.14 , which shows the dehumidification mode of the thermal management system. The principle of dehumidification is to cool the air through the evaporator (i.e., the third heat exchanger 803) and reduce its temperature to below the dew point temperature, so that the water vapor condenses into small water droplets and separates from the air, thereby achieving the dehumidification effect. It can be seen that the dehumidification mode requires cooling the air entering the cabin.

[0085] When the ambient temperature is low, if the dehumidified air is directly circulated to the cabin, the cabin temperature will further decrease, causing discomfort to the occupants. To avoid this problem, the damper of the first heat exchanger 801 (built-in condenser) can be opened so that the dehumidified air is heated by the first heat exchanger 801 and then circulated to the cabin. In this case, the fluid management valve 1 of the thermal management system is in the third working mode, that is, the fourth valve port 91 is connected to the fifth valve port 92; the main opening 93 is connected to the second valve port 96; and the third valve port 94 is connected to the first valve port 95.

[0086] Specifically, please refer to Fig.14In the first fluid circuit C1, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor 2 enters the first heat exchanger 801 (built-in condenser) and condenses to release heat, heating the air in the surrounding environment that has passed through the third heat exchanger 803, that is, heating the dehumidified air. The heated air is circulated into the vehicle cabin, which can avoid the problem of further lowering the cabin temperature due to dehumidification when the ambient temperature is low, causing discomfort to the driver and passengers. In addition, the refrigerant flowing through the first heat exchanger 801 is condensed into liquid, and passes through the third valve port 94 and the first valve port 95 of the fluid management valve 1 to reach the third fluid circuit C3, and then passes through the first throttling device 1011 of the third fluid circuit C3, and enters the third heat exchanger 803 (evaporator) after throttling and reducing the pressure by the first throttling device 101. The refrigerant evaporates and absorbs heat at the third heat exchanger 803, so as to cool the air in the surrounding environment that flows through the third heat exchanger 803 to below the dew point, thereby achieving the dehumidification effect. In addition, most of the refrigerant flowing through the third heat exchanger 803 is converted into gas, and continues to pass through the second valve port 96 and the main opening 93 of the fluid management valve 1 to reach the second fluid circuit C2, and then flows through the second heat exchanger 802 of the second fluid circuit C2 (at this time, the second heat exchanger 802 is only used for fluid communication), and flows back to the gas-liquid separator 3 of the first fluid circuit C1 through the fourth valve port 91 and the fifth valve port 92 of the fluid management valve 1. The liquid refrigerant is stored in the gas-liquid separator 3, and the gaseous refrigerant enters the air intake of the compressor 2 and is compressed into a high-temperature and high-pressure gaseous refrigerant, thus completing a complete cycle of the refrigerant circuit in this mode. For the surrounding environment, along the flow direction of the air, the air first flows through the third heat exchanger 803 for cooling and dehumidification, and then flows through the first heat exchanger 801 for heating, and the heated air circulates into the cabin.

[0087] When the ambient temperature is high, the dehumidified air can be circulated directly to the cabin to cool the cabin, which is the AC mode mentioned above. I will not go into details here. In other words, the AC mode has its own dehumidification function.

[0088] See also Fig.15 , which shows the heat pump mode of the thermal management system. The heat pump mode is used to heat the cabin. In this mode, the fluid management valve 1 of the thermal management system is in the fourth working mode (i.e., the second valve port 96 is connected to the main opening 93, and the main opening 93 is in a throttling state, the third valve port 94 is connected to the first valve port 95, and the fourth valve port 91 is connected to the fifth valve port 92), and the air entering the cabin can be heated by the first heat exchanger 801 (built-in condenser) to achieve heating of the cabin.

[0089] Specifically, in the first fluid circuit C1, the high-temperature and high-pressure gaseous refrigerant compressed by the compressor 2 enters the first heat exchanger 801 (built-in condenser) and condenses to release heat, heating the air in the surrounding environment that has passed through the third heat exchanger 803. The heated air is circulated into the vehicle cabin to achieve heating of the vehicle cabin. In addition, the refrigerant flowing through the first heat exchanger 801 is partially condensed into liquid, and reaches the third fluid circuit C3 through the third valve port 94 and the first valve port 95 of the fluid management valve 1, and flows through the first throttling device 1011 in the third fluid circuit C3 (at this time, the first throttling device 1011 is in a fully open state, and only serves as a fluid connection, and does not throttle or reduce the pressure of the refrigerant) and the third heat exchanger 803. It should be noted that the temperature of the refrigerant flowing out of the first heat exchanger 801 is higher than the temperature of the third heat exchanger 803, and the refrigerant is not throttled or reduced in pressure by the first throttling device 1011 before entering the third heat exchanger 803. Therefore, when the refrigerant with a higher temperature flows through the third heat exchanger 803, it will exchange heat with the air in the surrounding environment, thereby preheating the air entering the cabin. In addition, the refrigerant flowing through the third heat exchanger 803 releases heat and passes through the second valve port 96 and the main opening 93 of the fluid management valve 1 (at this time, the main opening 93 is in a throttling state), wherein the refrigerant is throttled and depressurized after flowing through the main opening 93, and the throttled and depressurized refrigerant reaches the second fluid circuit C2, and evaporates and absorbs heat through the second heat exchanger 802, so that most of the refrigerant is converted into a gas state, and the refrigerant continues to flow through the fourth valve port 91 and the fifth valve port 92 of the fluid management valve 1, and flows back to the gas-liquid separator 3 of the first fluid circuit C1, and the liquid refrigerant is stored in the gas-liquid separator 3, and the gaseous refrigerant enters the air intake of the compressor 2 and is compressed into a high-temperature and high-pressure gaseous refrigerant, thus completing a complete cycle of the refrigerant circuit in this mode. For the surrounding environment, along the flow direction of the air, the air first flows through the third heat exchanger 803 for preheating, and then flows through the first heat exchanger 801 for heating, and the heated air circulates into the cabin to achieve cabin heating.

[0090] In the heat pump mode, the battery heating function can also be selectively turned on. Specifically, the third throttling device 1013 in the first branch B1 is turned on, so that part of the refrigerant flowing out of the first valve port 95 flows through the third throttling device 1013 (at this time, the third throttling device 1013 is in a fully open state, only plays a role in fluid communication, and does not throttle and reduce the pressure of the refrigerant) and the fourth heat exchanger 804. It should be noted that the temperature of the refrigerant flowing out of the first heat exchanger 801 is higher than the temperature of the fourth heat exchanger 804, and the refrigerant is not throttled and reduced in pressure by the third throttling device 1013 before entering the fourth heat exchanger 804. Therefore, when the higher temperature refrigerant flowing out of the first valve port 95 flows through the fourth heat exchanger 804, heat exchange will be performed to achieve battery heating.

[0091] See also Fig.16, which shows a connection diagram of a thermal management system according to another embodiment of the present disclosure. Fig.11 The difference between the thermal management systems shown is that the connection position of the first branch B1 is different. Specifically, the first branch B1 is provided with a third throttling device 1013 and a fourth heat exchanger 804 in sequence along the flow direction of the fluid, wherein the upstream of the third throttling device 1013 is connected to the pipeline between the first valve port 95 and the first throttling device 1011, and the downstream of the fourth heat exchanger 804 is connected to the pipeline between the fifth valve port 92 and the gas-liquid separator 3. For example, a first junction point may be provided on the pipeline between the first valve port 95 and the first throttling device 1011, and a second junction point may be provided on the pipeline between the fifth valve port 92 and the gas-liquid separator 3, the upstream of the third throttling device 1013 is connected to the first junction point, and the downstream of the fourth heat exchanger 804 is connected to the second junction point.

[0092] In this embodiment, the fourth heat exchanger 804 may be a battery cooler to cool the battery. The third throttling device 1013 may be an expansion ball valve with three states: fully open, throttling and closed. The flow conditions of the expansion ball valve in different states are as described above and will not be repeated here.

[0093] Preferably, the thermal management system may further include a second branch B2. A fourth throttling device 1014 is provided on the second branch B2, the upstream of the fourth throttling device 1014 is connected to the pipeline between the compressor 2 and the first heat exchanger 801, and the downstream of the fourth throttling device 1014 is connected to the inlet of the gas-liquid separator 3. For example, a third junction may be provided on the pipeline between the exhaust port of the compressor 2 and the first heat exchanger 801, the upstream of the fourth throttling device 1014 is connected to the third junction, and the downstream thereof is connected to the inlet of the gas-liquid separator 3.

[0094] Next, the operating mode of the thermal management system described in this embodiment is explained in conjunction with the accompanying drawings. In addition to the AC mode, self-circulation mode, dehumidification mode and heat pump mode described above, the thermal management system of this embodiment also has a triangular circulation mode. When the ambient temperature is low and the heat pump efficiency is low, you can choose to turn on the triangular circulation mode. The triangular circulation mode is to use the compressor to work on the refrigerant, convert electrical energy into thermal energy, and transfer it to the cabin through the first heat exchanger 801 (built-in condenser) to achieve heating of the cabin in a low temperature environment. In this mode, the fluid management valve 1 of the thermal management system is in the second working mode, that is, the third valve port 94 is connected to the first valve port 95, the second valve port 96 is connected to the fifth valve port 92, and the main opening 93 is not connected to the fourth valve port 91; and the first throttling device 1011 is in a closed state.

[0095] Specifically, see Fig.17, the refrigerant is compressed by the compressor 2 (i.e., the compressor 2 does work on the refrigerant and converts the electrical energy into thermal energy) into a high-temperature and high-pressure gaseous refrigerant, which enters the first heat exchanger 801 (built-in condenser) and condenses and releases heat, heating the air in the surrounding environment. After the air is heated, it circulates into the cabin to achieve cabin heating. In addition, the refrigerant flowing through the first heat exchanger 801 is partially condensed into a liquid state, and passes through the third valve port 94 and the first valve port 95 of the fluid management valve 1 to reach the first branch B1, throttled and reduced in pressure by the third throttling device 1013 in the first branch B1, and then flows through the fourth heat exchanger 804 to evaporate and absorb heat, converting most of the refrigerant into a gaseous state, and the refrigerant continues to flow into the gas-liquid separator 3, the liquid refrigerant is stored in the gas-liquid separator 3, and the gaseous refrigerant enters the air intake of the compressor 2 and is compressed. In this cycle, the compressor mainly does work on the refrigerant to convert the electrical energy into thermal energy, and transfers it to the cabin through the built-in condenser, thereby achieving cabin heating in a low-temperature environment.

[0096] When the gas-liquid separator 3 can no longer store the liquid refrigerant in the system (otherwise the liquid refrigerant will be discharged to the suction port of the compressor), the second branch B2 can be opened to allow part of the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 2 to flow through the fourth throttling device 1014 and be throttled and reduced in pressure before circulating into the gas-liquid separator 3, and heating the liquid refrigerant in the gas-liquid separator 3 into a gaseous state. This can prevent excessive liquid refrigerant from circulating directly to the compressor, thereby improving the performance of the compressor.

[0097] It can be seen that the thermal management system provided by the present disclosure can realize multiple thermal management modes, simplify the pipeline connection and control strategy of the thermal management system, and reduce the cost of the entire system because it includes the fluid pipe valve 1 of the above structure.

[0098] Although the present disclosure describes the self-circulation mode as an intermediate transition mode between the AC mode and the heat pump mode, the present disclosure is not limited to this. For example, the self-circulation mode can also be used as an intermediate transition mode between the AC mode and the dehumidification mode. As long as the flow directions of the refrigerant in the second fluid circuits C2 corresponding to the two modes are opposite, the self-circulation mode can be used as the intermediate transition mode between the two modes.

[0099] In summary, the present disclosure provides a fluid management valve and a thermal circulation system including the fluid management valve. The fluid management valve includes a valve body and a valve core located in the valve body and capable of rotating between different positions relative to the valve body. The valve body is provided with a valve port and a main opening, and the valve core is provided with a main flow channel, wherein the main flow channel includes a main body section and a throttling section. By rotating the valve core, the main opening can correspond to the main body section or the throttling section of the main flow channel, and selectively connect the valve port, so that the fluid management valve can be switched between different working modes, and the main opening can adjust the fluid flow, specifically, it can be adjusted between full opening, throttling and closing. This design can not only replace the complex structure of multiple stop valves and / or three-way valves in the prior art, but also has simple assembly, low cost, easy control, and can simplify the pipeline structure and improve product integration. Since the thermal management system includes the fluid management valve of the above structure, the pipeline connection and control strategy of the thermal management system can be simplified, and the cost of the entire system can be reduced.

[0100] The above describes exemplary implementations of the fluid management valve and thermal management system provided by the present disclosure with reference to preferred embodiments. However, those skilled in the art will appreciate that, without departing from the concept of the present disclosure, various modifications and variations may be made to the above-mentioned specific embodiments, and various technical features and structures proposed in the present disclosure may be combined in various ways without exceeding the protection scope of the present disclosure, which is determined by the appended claims.

Claims

1. A fluid management valve (1), comprising: A valve body (10), the valve body (10) having a valve port and a main opening (93); A valve core (20), the valve core (20) having a main flow channel (23); the valve core (20) is located in the valve body (10) and has a connecting position and a closing position relative to the valve body (10); When the valve core (20) is located at the communication position, the main flow channel (23) communicates with the valve port and the main opening (93); When the valve core (20) is located at the closed position, the valve port and the main opening (93) are separated by the valve core (20).

2. The fluid management valve (1) according to claim 1, wherein the main flow channel (23) has a main body section (230) and a throttling section (231); the communication position includes a fully open position and a throttling position; When the valve core (20) is located at the fully open position, the main body section (230) directly connects the main opening (93) and the valve port; When the valve core (20) is located at the throttling position, the throttling section (231) is located between the main opening (93) and the main body section (230), so that the main body section (230) is communicated with the main opening (93) via the throttling section (231).

3. The fluid management valve (1) of claim 2, wherein the valve port comprises a first valve port (95) and a second valve port (96); the fully open position comprises a first fully open position and a second fully open position; When the valve core (20) is located at the first fully open position, the main opening (93) is connected to the first valve port (95) through the main body section (230); When the valve core (20) is located at the second fully open position, the main opening (93) is in communication with the second valve port (96) through the main body section (230).

4. The fluid management valve (1) according to claim 3, wherein the valve core (20) further has a central flow channel (21); the valve port further comprises a third valve port (94) and a fourth valve port (91); When the valve core (20) is located at the first fully open position, the third valve port (94) is connected to the fourth valve port (91) through the central flow channel (21); When the valve core (20) is located at the closed position, the third valve port (94) is connected to the first valve port (95) through the central flow channel (21); When the valve core (20) is located at the second fully open position, the third valve port (94) is connected to the first valve port (95) through the central flow channel (21); When the valve core (20) is located at the throttling position, the third valve port (94) is in communication with the first valve port (95) through the central flow channel (21).

5. The fluid management valve (1) according to claim 4, wherein the central flow channel (21) is defined into a fan-shaped shape by the arc-shaped edge portion (210), the first straight edge portion (211) and the second straight edge portion (212); wherein, The third valve port (94) is located at the intersection of the first straight edge portion (211) and the second straight edge portion (212); During the movement of the valve core (20) relative to the valve body (10), the fourth valve port (91) and the first valve port (95) move along the arc-shaped edge (210) relative to the valve core (20).

6. The fluid management valve (1) according to claim 4, wherein the valve core (20) further comprises an edge flow channel (22); the valve port further comprises a fifth valve port (92); When the valve core (20) is located at the first fully open position, the fifth valve port (92) is connected to the second valve port (96) through the edge flow channel (22); When the valve core (20) is located at the closed position, the fifth valve port (92) is communicated with the second valve port (96) through the edge flow channel (22); When the valve core (20) is located at the second fully open position, the fifth valve port (92) is connected to the fourth valve port (91) through the edge flow channel (22); When the valve core (20) is located at the throttling position, the fifth valve port (92) is communicated with the fourth valve port (91) through the edge flow channel (22).

7. The fluid management valve (1) according to claim 6, wherein the edge flow channel (22) is an arc-shaped cavity extending along the circumference of the fluid management valve (1).

8. A fluid management valve (1) as described in claim 1, wherein the valve body (10) has a top wall (101), a bottom wall (102) and a side wall (103) located between the top wall (101) and the bottom wall (102), the valve port is arranged on the bottom wall (102), and the main opening (93) is arranged on the side wall (103).

9. The fluid management valve (1) according to claim 6, wherein the central flow channel (21) and the edge flow channel (22) open on the bottom wall (202) of the valve core (20).

10. The fluid management valve (1) according to claim 2, wherein the main flow channel (23) is formed with a first flow channel opening (232) on the bottom wall (202) of the valve core (20); the main flow channel (23) is formed with a second flow channel opening (233) on the side wall (203) of the valve core (20); in, The second flow channel opening (233) comprises a first opening area (2331) for defining the main body section (230) and a second opening area (2332) for defining the throttling section (231); When the valve core (20) is located at the fully open position, the first opening area (2331) at least partially overlaps with the main opening (93); When the valve core (20) is located at the throttling position, the second opening area (2332) at least partially overlaps with the main opening (93).

11. The fluid management valve (1) according to claim 1, wherein the fluid management valve (1) further comprises a sealing member disposed between the valve body (10) and the valve core (20).

12. The fluid management valve (1) according to claim 2, wherein the throttling section (231) is a groove extending from a connection with the main body section (230) toward a direction away from the main body section (230).

13. The fluid management valve (1) of claim 12, wherein the groove tapers in a direction away from the body section (230).

14. The fluid management valve (1) according to claim 1, wherein the fluid management valve (1) further comprises an actuator (30) connected to the valve core (20) to drive the valve core (20) to rotate between the connecting position and the closing position.

15. A thermal management system, wherein the thermal management system comprises the fluid management valve (1) according to any one of claims 1 to 14.

Images