Fluid management valve and thermal management system

Abstract

The invention provides a fluid management valve which comprises a valve body provided with a valve port; the valve ports comprise a first valve port and a second valve port; a first flow channel is formed in the peripheral wall of the valve element; the first flow channel is provided with a main body section and a throttling section; the valve element is located in the valve body and has a full-open position and a throttling position relative to the valve body. When the valve element is located at the fully-open position, the main body part section directly communicates with the first valve port and the second valve port; when the valve element is located at the throttling position, the throttling part section is located between the first valve port and the second valve port, so that the first valve port communicates with the second valve port through the throttling part section. By means of the design, switching of the fluid management valve among different working modes can be achieved, the second valve port 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, wherein a first and a second valve port are arranged on a valve body, and a first flow channel including a main body section and a throttling section is arranged on an outer peripheral wall of the valve core. By rotating the valve core, the second valve port can selectively correspond to the main body section or the throttling section of the first flow channel and be connected to the first valve port, so that the fluid management valve can be switched between different working modes and the second valve port has a throttling function. Specifically, the second valve port 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 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, having a valve port; the valve port comprises a first valve port and a second valve port; a valve core, a first flow channel being formed on the outer peripheral wall of the valve core; the first flow channel having a main body section and a throttling section; the valve core is located within the valve body and has a fully open position and a throttling position relative to the valve body; when the valve core is located at the fully open position, the main body section directly connects the first valve port and the second valve port; when the valve core is located at the throttling position, the throttling section is located between the first valve port and the second valve port, so that the first valve port is connected to the second valve port via the throttling section.

[0006] The present invention discloses a fluid management valve having the above-mentioned design, which can realize switching between different working modes, and the second valve port can be in a fully open or throttling state. This design has a simple structure, is easy to assemble, has a low cost, is easy to control, and can simplify the piping structure, thereby improving product integration.

[0007] In one or more embodiments, the throttling position includes a first throttling position and a second throttling position; when the valve core is located at the first throttling position, the throttling section is located between the main body section and the second valve port, and the main body section is located between the throttling section and the first valve port, so that the first valve port is connected to the second valve port via the main body section and the throttling section; when the valve core is located at the second throttling position, the throttling section directly connects the first valve port and the second valve port.

[0008] In one or more embodiments, the first flow channel is formed with a flow channel opening on the outer peripheral wall, and the flow channel opening includes a first opening area for defining the main body section and a second opening area for defining the throttling section; the first opening area and the second opening area are connected to each other on the outer peripheral wall; when the valve core is located at the fully open position, the first opening area at least partially overlaps with the first valve port and the second valve port, respectively; when the valve core is located at the first throttling position, the first opening area at least partially overlaps with the first valve port, and the second opening area at least partially overlaps with the second valve port; when the valve core is located at the second throttling position, the second opening area at least partially overlaps with the first valve port and the second valve port, respectively.

[0009] In one or more embodiments, the main body section is a fan-shaped cavity with the axis of the valve core as its center.

[0010] In one or more embodiments, the throttling section is an elongated groove extending from a connection with the main body section toward a direction away from the main body section.

[0011] The present disclosure enables the second valve port to adjust the throttling amount through the above-mentioned design of the fluid management valve.

[0012] In one or more embodiments, the valve port also includes a third valve port, a fourth valve port, a fifth valve port and a sixth valve port; the valve core also has a second flow channel and a third flow channel; when the valve core is located at the fully open position and the throttling position, the second flow channel connects the third valve port and the fourth valve port, and the third flow channel connects the fifth valve port and the sixth valve port.

[0013] In one or more embodiments, the first flow channel, the second flow channel, and the third flow channel are arranged in layers along the axis of the valve core and are independent of each other.

[0014] In one or more embodiments, the valve core also has a first connecting position relative to the valve body; the valve core also has a fourth flow channel, a fifth flow channel and a sixth flow channel; when the valve core is located at the first connecting position, the fourth flow channel connects the first valve port and the sixth valve port; the fifth flow channel connects the second valve port and the fourth valve port; the sixth flow channel connects the fifth valve port and the third valve port.

[0015] In one or more embodiments, the valve core also has a second connecting position relative to the valve body; the valve core also has a seventh flow channel, an eighth flow channel and a blocking portion; when the valve core is located at the second connecting position, the seventh flow channel connects the first valve port and the sixth valve port; the eighth flow channel connects the third valve port and the fourth valve port; and the blocking portion blocks the fifth valve port.

[0016] In one or more embodiments, the peripheral wall is a tapered wall.

[0017] Through the above-mentioned arrangement of the valve core in the present disclosure, after the valve core is placed in the valve body, the sealing performance between the valve core and the valve body can be improved by extrusion of the flange.

[0018] In one or more embodiments, the valve body includes a main body and a sealing member; the sealing member is disposed in the main body; the valve port passes through the main body and the sealing member; wherein the sealing member is disposed between the outer peripheral wall of the valve core and the main body along the radial direction of the valve core.

[0019] The present invention can effectively avoid the problem of internal leakage caused by cross-flow of fluid between the valve core and the valve body by arranging a sealing member between the valve core and the main body of the valve body.

[0020] In one or more embodiments, the valve core is in a truncated cone shape.

[0021] Through the above-mentioned arrangement of the valve core in the present disclosure, after the valve core is placed in the valve body, the sealing performance between the valve core and the valve body can be improved by extrusion of the flange.

[0022] 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 relative to the valve body.

[0023] The present disclosure also provides a thermal management system for a vehicle, comprising the aforementioned fluid management valve.

[0024] 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

[0025] Figure 1 A perspective view of a fluid management valve according to an embodiment of the present disclosure is shown;

[0026] Figure 2 A three-dimensional 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 first to sixth valve ports is shown;

[0027] Figure 3 A perspective view of a valve body according to an embodiment of the present disclosure is shown;

[0028] Figure 4 A perspective view of a seal according to an embodiment of the present disclosure is shown;

[0029] Figure 5 A schematic diagram of a valve core flow channel 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 communication position;

[0030] Figure 6 Shows Figure 5 A cross-sectional view of the valve core at the first layer, wherein the fourth flow channel of the valve core is shown;

[0031] Figure 7 Shows Figure 6 A three-dimensional view of the valve core from another viewing angle;

[0032] Figure 8 A schematic diagram of a valve core flow channel 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 second communication position;

[0033] Fig. 9 Shows Figure 8 A cross-sectional view of the valve core at the first layer, showing the seventh flow channel and the blocking portion of the valve core;

[0034] Fig.10 A schematic diagram of a valve core flow channel 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 fully open position;

[0035] Fig.11 A schematic diagram of a valve core flow channel 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 first throttling position;

[0036] Fig.12 A schematic diagram of a valve core flow channel 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 second throttling position;

[0037] Fig.13 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 fully open position;

[0038] Fig.14 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 first throttling position;

[0039] Fig.15 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 second throttling position;

[0040] Fig.16 A connection diagram of a thermal management system according to an embodiment of the present disclosure is shown;

[0041] Fig.17 A connection diagram of a thermal management system according to another embodiment of the present disclosure is shown;

[0042] Fig.18 A schematic diagram showing the connection of a thermal management system according to another embodiment of the present disclosure when operating in AC mode;

[0043] Fig.19 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;

[0044] Fig. 20 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;

[0045] Fig.21 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;

[0046] Fig. 22 A connection diagram of a thermal management system according to another embodiment of the present disclosure is shown;

[0047] Fig.23 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

[0048] 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.

[0049] 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.

[0050] 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.

[0051] The present disclosure provides a fluid management valve 1, see Figures 1 to 5 The fluid management valve 1 includes a valve body 10 having a plurality of valve ports and a valve core 20 located inside the valve body 10 and rotatable relative to the valve body 10 between a plurality of positions.

[0052] See also Figure 3 and Figure 4 The valve body 10 may include a main body 100 and a sealing member 101. The main body 100 is roughly cylindrical and may have a truncated cone-shaped cavity inside. The main body 100 includes a top wall 1001, a bottom wall 1002, and a side wall 1003 located between the top wall 1001 and the bottom wall 1002, wherein the top wall 1001 is located at the end with a larger diameter of the cavity, and the bottom wall 1002 is located at the end with a smaller diameter of the cavity. The sealing member 101 is arranged in the main body 100 and is located between the main body 100 and the valve core 20. A plurality of valve ports are penetrated through the main body 100 and the sealing member 101 to connect the flow channel on the valve core 20. The above-mentioned arrangement of the sealing member 101 can realize the sealed connection between the plurality of valve ports of the valve body 10 and the corresponding flow channels of the valve core 20, and effectively avoid the problem of internal leakage caused by the cross-flow between the fluid valve core 20 and the main body 100. The multiple valve ports of the valve body 10 may be located on the side wall 1003. Preferably, the multiple valve ports may be located in the same plane of the side wall 1003. Figure 2 As shown, such an arrangement allows the multiple valve ports to be directly connected to the flow channels on the flow channel plate (not shown), thereby simplifying the pipeline arrangement and optimizing the system structure.

[0053] In this embodiment, the valve body 10 may include six valve ports, namely a first valve port 96, a second valve port 93, a third valve port 94, a fourth valve port 95, a fifth valve port 91 and a sixth valve port 92, arranged in two vertical rows (eg Figure 2As shown in FIG. 1 , at least two valve ports 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 1001 for placing the valve core 20, and the valve core 20 can be fixed in the cavity of the valve core 10 by a flange installed on the top wall 1001.

[0054] See also Figures 5 to 12 The valve core 20 may be roughly in the shape of a truncated cone and have a roughly conical outer peripheral wall 200, so that after the valve core 20 is placed on the valve body 10, the sealing performance between the valve core 20 and the valve body 10 can be improved by squeezing the flange installed on the top wall 1001. In this embodiment, the valve core 20 can be relative to the valve body 10 in the first communication position (such as Figure 5 As shown), the second communication position (as shown Figure 8 as shown), fully open position (as shown Fig.10 ) and a plurality of positions such as a throttling position, wherein the throttling position includes a first throttling position (such as Fig.11 as shown) and the second throttle position (as shown) Fig.12 The valve core 20 includes a plurality of flow channels, so that the valve core 20 can be connected to at least two valve ports when in each of the above positions.

[0055] See also Figures 10 to 12 The valve core 20 may include a first flow channel 21, a second flow channel 22 and a third flow channel 23 which are layered and independent of each other and are arranged on the outer peripheral wall 200. Fig.10 ) and throttle position (as shown Fig.11 and Fig.12 As shown), the first flow channel 21 is used to connect the first valve port 96 and the second valve port 93, the second flow channel 22 is used to connect the third valve port 94 and the fourth valve port 95, and the third flow channel 23 is used to connect the fifth valve port 91 and the sixth valve port 92.

[0056] Specifically, the first flow channel 21 includes a main body section 210 and a throttling section 211 connected to the main body section 210, and has a flow channel opening 212 opened on the outer peripheral wall 200 to achieve communication between the two valve ports by overlapping the first and second valve ports 96 and 93. In detail, the flow channel opening 212 includes a first opening area 2121 for defining the main body section 210 and a second opening area 2122 for defining the throttling section 211. That is, the first opening area 2121 is the opening area of ​​the main body section 210 on the outer peripheral wall 200, and the second opening area 2122 is the opening area of ​​the throttling section 211 on the outer peripheral wall 200, and the two opening areas 2121 and 2122 are connected to each other on the outer peripheral wall 200.

[0057] In this embodiment, the main body section 210 of the first flow channel 21, the second flow channel 22 and the third flow channel can all be fan-shaped cavities with the axis A of the valve core 20 as the center. The throttling section 211 of the first flow channel 21 can be an elongated arc-shaped groove, extending from the connection with the main body section 210 in the direction away from the main body section 210, and along with the extension direction of the throttling section 211, the size of the second opening area 2122 of the throttling section 211 in the direction of the axis A gradually increases or decreases, so that the valve core 20 can accurately control the throttling amount of the valve port corresponding to the throttling section 211 when the valve core 20 is in different positions. It should be noted that the maximum size of the second opening area 2122 in the direction of the axis A is less than or equal to the size of the first opening area 2121 in the direction of the axis A, so that the valve port corresponding to the second opening area 2122 has a throttling effect. Of course, the present disclosure is not limited to the above-mentioned shapes of the first, second and third flow channels 21, 22 and 23, as long as they can connect different valve ports and the throttling section 211 of the first flow channel can adjust the throttling amount of the corresponding valve port.

[0058] See also Figure 5 The valve core 20 may further include a fourth flow channel 24, a fifth flow channel 25 and a sixth flow channel 26 which are longitudinally arranged and independent of each other. Figure 5 As shown), the fourth flow channel 24 is used to connect the first valve port 96 and the sixth valve port 92, the fifth flow channel 25 is used to connect the second valve port 93 and the fourth valve port 95, and the sixth flow channel 26 is used to connect the third valve port 94 and the fifth valve port 91.

[0059] In this embodiment, if Figures 5 to 7 As shown, the fourth flow channel 24 may be roughly Z-shaped and arranged close to the axis A, with openings formed at both ends on the peripheral wall 200 to respectively connect the first valve port 96 and the sixth valve port 92. The fifth flow channel 25 may be roughly I-shaped, formed on the peripheral wall 200 and located outside the fourth flow channel 24 in the radial direction, to connect the second valve port 93 and the fourth valve port 95. The sixth flow channel 26 may also be I-shaped, formed on the peripheral wall 200 and located beside the fourth flow channel 24 in the circumferential direction, to connect the third valve port 94 and the fifth valve port 91.

[0060] See also Figure 8 The valve core 20 may further include a blocking portion 29 and a seventh flow channel 27 and an eighth flow channel 28 that are overlapped and independent of each other. Figure 8), the seventh flow channel 27 is used to connect the first valve port 96, the second valve port 93 and the sixth valve port 92, the eighth flow channel 28 is used to connect the third valve port 94 and the fourth valve port 95, and the blocking portion 29 is used to block the fifth valve port 91 so that it is not connected to other valve ports. It should be noted that the seventh flow channel 27 of the valve core 20 is not limited to the above-mentioned connection form. For example, the seventh flow channel 27 can also only connect the first valve port 96 and the sixth valve port 92 without connecting the second valve port 93. In this case, the second valve port 93 can be blocked by the outer peripheral wall 200 of the valve core 20, as long as the first valve port 96 and the sixth valve port 92 are connected.

[0061] In this embodiment, if Figure 8 and Fig. 9 As shown, the seventh flow channel 27 may be roughly Z-shaped and disposed longitudinally close to the axis A, with openings formed at both ends on the peripheral wall 200 to connect the first valve port 96 and the sixth valve port 92, respectively. The eighth flow channel 28 may be roughly I-shaped and disposed transversely. The eighth flow channel 28 is formed on the peripheral wall 200 and is located outside the seventh flow channel 27 in the radial direction to connect the third valve port 94 and the fourth valve port 95. The blocking portion 29 may be roughly a cavity that is only connected to the fifth valve port 91. Of course, the present disclosure is not limited to this. For example, the blocking portion 29 may also be the peripheral wall 200 corresponding to the fifth valve port 91, as long as it can block the fifth valve port 91 so that it is not connected to other valve ports.

[0062] Please return to see Figure 5 The valve core 20 may also be provided with a mounting boss 201 at the center of its bottom wall, and correspondingly, a mounting groove 102 may be provided on the inner side of the bottom wall 1002 of the valve body 10 (such as Figure 3 As shown in FIG. 1 , the mounting boss 201 is located in the mounting groove 102 to support one end of the valve core 20 to facilitate the smooth rotation of the valve core 20. Of course, the present disclosure is not limited to the above structure. The valve core 20 is also provided with a spline 202 at the center of its top wall to spline-connect the actuator 30, and the actuator 30 can be used to drive the valve core 20 to rotate between different positions.

[0063] The following will combine Figure 2 , Figures 5 to 15 The four working modes of the fluid management valve 1 are specifically described.

[0064] Figure 5 2 shows a schematic diagram of the flow channel of the valve core 20 when the valve core 20 is in the first communication position. At this time, the fluid management valve 1 is in the first working mode. Figure 2 , Figures 5 to 7When the valve core 20 is in the first connecting position: the fourth flow channel 24 of the valve core 20 connects the first valve port 96 and the sixth valve port 92 of the valve body 10; the fifth flow channel 25 connects the second valve port 93 and the fourth valve port 95 of the valve body 10; the sixth flow channel 26 connects the fifth valve port 91 and the third valve port 94 of the valve body 10; the fluid management valve 1 is in the first working mode.

[0065] Figure 8 2 shows a schematic diagram of the flow channel of the valve core 20 when the valve core 20 is in the second communication position. At this time, the fluid management valve 1 is in the second working mode. Figure 2 , Figure 8 and Fig. 9 When the valve core 20 rotates clockwise from the first connecting position to the second connecting position: the seventh flow channel 27 of the valve core 20 connects the first valve port 96 and the sixth valve port 92 of the valve body 10; the eighth flow channel 28 connects the third valve port 94 and the fourth valve port 95 of the valve body 10; the blocking portion 29 blocks the fifth valve port 91 of the valve body 10 so that it is not connected to other valve ports, and the fluid management valve 1 is in the second working mode.

[0066] Fig.10 A schematic diagram of the flow path of the valve core 20 when the valve core 20 is in the fully open position is shown; Fig.13 2 shows a cross-sectional view of the fluid management valve 1 when the valve core 20 is in the fully open position. At this time, the fluid management valve 1 is in the third working mode. Figure 2 , Fig.10 and Fig.13 , when the valve core 20 rotates clockwise from the first or second connecting position to the fully open position: the first flow channel 21 of the valve core 20, especially the main body section 210 of the first flow channel 21, connects the first valve port 96 and the second valve port 93. Specifically, the main body section 210 is directly located between the first valve port 96 and the second valve port 93, so that the first valve port 96 is connected to the second valve port 93 only via the main body section 210, that is, the first opening area 2121 at least partially overlaps with the first valve port 96, and the first opening area 210 at least partially overlaps with the second valve port 93. At this time, the second valve port 93 is in a fully open state; the second flow channel 22 connects the third valve port 94 and the fourth valve port 95; the third flow channel 23 connects the fifth flow channel 91 and the sixth flow channel 92; the valve body management valve 1 is in the third working mode.

[0067] Fig.11 A schematic diagram of the flow passage of the valve core 20 when the valve core 20 is in the first throttling position is shown; Fig.14 2 shows a cross-sectional view of the fluid management valve 1 when the valve core 20 is in the first throttling position. At this time, the fluid management valve is in a form of the fourth working mode. Figure 2 , Fig.11 and Fig.14When the valve core 20 rotates clockwise from the first communication position, the second communication position or the fully open position to the first throttling position: the first flow channel 21 of the valve core 20, especially the main body section 210 and the throttling section 211 of the first flow channel 21, communicates with the first valve port 96 and the second valve port 93. Specifically, the main body section 210 is located between the first valve port 96 and the throttling section 211, and the throttling section 211 is located between the main body section 210 and the second valve port 93, so that the first valve port 96 is connected to the second valve port 93. The main body section 210 and the throttling section 211 are connected to the second valve port 93, that is, the first opening area 2121 at least partially overlaps with the first valve port 96, and the second opening area 2122 at least partially overlaps with the second valve port 93, at which time the second valve port 93 is in a throttling state; the second flow channel 22 connects the third valve port 94 and the fourth valve port 95; the third flow channel 23 connects the fifth flow channel 91 and the sixth flow channel 92; the valve body management valve 1 is in a form of the fourth working mode.

[0068] Fig.12 A schematic diagram of the flow passage of the valve core 20 when the valve core 20 is in the second throttling position is shown; Fig.15 2 shows a cross-sectional view of the fluid management valve 1 when the valve core 20 is in the second throttling position. At this time, the fluid management valve is in another form of the fourth working mode. Figure 2 , Fig.12 and Fig.15 When the valve core 20 rotates clockwise from the first connecting position, the second connecting position, the fully open position or the first throttling position to the second throttling position: the first flow channel 21 of the valve core 20, especially the throttling section 211 of the first flow channel 21, connects the first valve port 96 and the second valve port 93. Specifically, the throttling section 211 is directly located between the first valve port 96 and the second valve port 93, so that the first valve port 96 is connected to the second valve port 93 only via the throttling section 211. That is to say, the second opening area 2122 at least partially overlaps with the first valve port 96, and the second opening area 2122 at least partially overlaps with the second valve port 93. At this time, the second valve port 93 is still in a throttling state, but due to the size setting characteristics of the second opening area 2122, the throttling amount of the second valve port 93 is different from Fig.14 The throttling amount of the second valve port 93; the second flow channel 22 connects the third valve port 94 and the fourth valve port 95; the third flow channel 23 connects the fifth flow channel 91 and the sixth flow channel 92; the valve body management valve 1 is in another form of the fourth working mode.

[0069] It should be noted that the fluid management valve 1 is generally referred to as the fourth working mode when the second valve port 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.14 and Fig.15For example, when the valve core 20 is in any position between the first throttling position and the second throttling position, or the valve core 20 can continue to rotate clockwise from the second throttling position until the peripheral wall 200 completely blocks the second opening 93, the fluid management valve 1 is in the fourth working mode, and only the throttling amount of the second valve port 93 is different. In this embodiment, the second valve port 93 can be adjusted between 100% (fully open) and 0% (closed).

[0070] 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 second valve port 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.

[0071] Although the above-mentioned embodiment of the present disclosure is described with the valve body 10 having six valve ports, the second valve port 93 having a throttling function, the valve core 20 having eight 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 at least two valve ports, and other valve ports may be set to have a throttling function as needed. The valve core 20 may be in other positions, and may also have other flow channels, so that the fluid management valve 1 is in other working modes (for example, the fifth working mode: the second valve port 93 is connected to the third valve port 94; the fifth valve port 91 is connected to the sixth valve port 92; and the fourth valve port 95 and the first 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 sixth valve port 92). As long as the valve core 20 can connect at least two valve ports when in different positions, switching between different working modes of the fluid management valve 1 can be achieved.

[0072] In addition, the present disclosure Figures 5 to 15 The arrows representing the flow channels are not used to limit the flow direction of the fluid, but are only for the convenience of explanation. For example, the fluid can also flow in the opposite direction of the arrow as long as the sub-areas passed by the arrow are connected.

[0073] The present disclosure also provides a thermal management system including the above-mentioned fluid management valve, and various embodiments of the thermal management system will be described below in conjunction with the accompanying drawings. 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 various valve ports included, but does not show the specific positional relationship of the various valve ports.

[0074] See also Fig.16, 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.

[0075] 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 sixth 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 sixth 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 sixth 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.

[0076] In one embodiment, the first fluid circuit C1 may further include a gas-liquid separator 3 disposed between the sixth 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.

[0077] 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 fifth valve port 91 and the second valve port 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 second valve port 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.

[0078] 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 fourth valve port 95 of the fluid management valve 1, and the downstream of the third heat exchanger 803 is connected to the first valve port 96 of the fluid management valve 1, that is, the two ends of the third fluid circuit C3 are connected to the fourth valve port 95 and the first 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.

[0079] Please continue to see Fig.16 , 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 fourth 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 first valve port 96 and the third heat exchanger 803. For example, a first junction may be provided on the pipeline between the fourth valve port 95 and the first throttling device 1011, and a second junction may be provided on the pipeline between the first 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.

[0080] 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 second valve port 93 is either fully open or closed, and does not need to have a throttling function.

[0081] 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.

[0082] See also Fig.17 , which shows a connection diagram of a thermal management system according to another embodiment of the present disclosure. Fig.16 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 second valve port 93 of the fluid management valve 1 can be in a fully open state, a closed state and a throttling state. When the second valve port 93 is in a throttling state, the second valve port 93 has a throttling function, so that the second throttling device 1012 in the second fluid circuit C2 can be omitted.

[0083] 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.17 The connection relationship of the thermal management system shown is similar to Fig.16 is roughly the same, except that Fig.16 The function of the second throttling device 1012 is incorporated into the second valve port 93 of the fluid management valve 1, so Fig.16 and Fig.17 The thermal management system shown in the figure operates in the same way. Fig.17 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.

[0084] See also Fig.18 , 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 fifth valve port 91; the second valve port 93 (in the fully open state) is connected to the fourth valve port 95; the first valve port 96 is connected to the sixth valve port 92), and the air entering the cabin can be cooled by the third heat exchanger 803 (evaporator) to achieve cabin cooling.

[0085] 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 fifth 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 second valve port 93 and the fourth 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 first valve port 96 and the sixth 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.

[0086] 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.

[0087] See also Fig.19 , 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.

[0088] 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 fourth valve port 95; the first valve port 96 is connected to the sixth valve port 92; and the main valve port 93 and the fifth valve port 91 are not connected) so that the refrigerant in the second circuit C2 is in a paused state.

[0089] 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 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 first valve port 96 and the sixth 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.

[0090] See also Fig. 20 , 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.

[0091] 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 driver and passengers. 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 fifth valve port 91 is connected to the sixth valve port 92; the second valve port 93 is connected to the first valve port 96; and the third valve port 94 is connected to the fourth valve port 95.

[0092] Specifically, please refer to Fig. 20In 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 fourth 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 first valve port 96 and the second valve port 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 through the fifth valve port 91 and the sixth valve port 92 of the fluid management valve 1, it 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. 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.

[0093] 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.

[0094] See also Fig.21 , 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 first valve port 96 is connected to the second valve port 93, and the second valve port 93 is in a throttling state, the third valve port 94 is connected to the fourth valve port 95, and the fifth valve port 91 is connected to the sixth 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.

[0095] 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 fourth 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 first valve port 96 and the second valve port 93 of the fluid management valve 1 (at this time, the second valve port 93 is in a throttling state), wherein the refrigerant is throttled and depressurized after flowing through the second valve port 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 fifth valve port 91 and the sixth 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.

[0096] 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 fourth 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 fourth valve port 95 flows through the fourth heat exchanger 804, heat exchange will be performed to achieve battery heating.

[0097] See also Fig. 22, which shows a connection diagram of a thermal management system according to another embodiment of the present disclosure. Fig.17 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 fourth 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 sixth valve port 92 and the gas-liquid separator 3. For example, a first junction point may be provided on the pipeline between the fourth valve port 95 and the first throttling device 1011, and a second junction point may be provided on the pipeline between the sixth 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.

[0098] 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.

[0099] 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.

[0100] 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 fourth valve port 95, the first valve port 96 is connected to the sixth valve port 92, and the second valve port 93 is not connected to the fifth valve port 91; and the first throttling device 1011 is in a closed state.

[0101] Specifically, see Fig.23, 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 fourth valve port 95 of the fluid management valve 1 to reach the first branch B1, throttles and reduces the pressure through 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. The refrigerant continues to flow into the gas-liquid separator 3, and the liquid refrigerant is stored in the gas-liquid separator 3. 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.

[0102] 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.

[0103] 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 management valve 1 of the above structure.

[0104] 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.

[0105] 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 first and a second valve port, and the outer peripheral wall of the valve core is provided with a first flow channel including a main body section and a throttling section. By rotating the valve core, the second valve port can selectively correspond to the fifth flow channel, the main body section or the throttling section of the first flow channel, and connect to the first valve port, so that the fluid management valve can be switched between different working modes, and the second valve port has a throttling function. Specifically, the second valve port 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, and 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.

[0106] 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) having a valve port; the valve port comprises a first valve port (96) and a second valve port (93); as well as A valve core (20), wherein a first flow channel (21) is formed on an outer peripheral wall (200) of the valve core (20); the first flow channel (21) has a main body section (210) and a throttling section (211); the valve core (20) is located in the valve body (10) and has a fully open position and a throttling position relative to the valve body (10), wherein: When the valve core (20) is located at the fully open position, the main body section (210) is directly connected to the first valve port (96) and the second valve port (93); When the valve core (20) is located at the throttling position, the throttling section (211) is located between the first valve port (96) and the second valve port (93), so that the first valve port (96) is connected to the second valve port (93) via the throttling section (211).

2. The fluid management valve (1) of claim 1, wherein the throttle position comprises a first throttle position and a second throttle position; When the valve core (20) is located at the first throttling position, the throttling section (211) is located between the main body section (210) and the second valve port (93), and the main body section (210) is located between the throttling section (211) and the first valve port (96), so that the first valve port (96) is connected to the second valve port (93) via the main body section (210) and the throttling section (211); When the valve core (20) is located at the second throttling position, the throttling section (211) directly connects the first valve port (96) and the second valve port (93).

3. The fluid management valve (1) according to claim 2, wherein the first flow channel (21) is formed with a flow channel opening (212) on the peripheral wall (200), and the flow channel opening (212) includes a first opening area (2121) for defining the main body section (210) and a second opening area (2122) for defining the throttling section (211); the first opening area (2121) and the second opening area (2122) are connected to each other on the peripheral wall (200); When the valve core (20) is located at the fully open position, the first opening area (2121) at least partially overlaps with the first valve port (96) and the second valve port (93), respectively; When the valve core (20) is located at the first throttling position, the first opening area (2121) at least partially overlaps with the first valve port (96), and the second opening area (2122) at least partially overlaps with the second valve port (93); When the valve core (20) is located at the second throttling position, the second opening area (2121) at least partially overlaps with the first valve port (96) and the second valve port (93), respectively.

4. The fluid management valve (1) according to claim 1, wherein the main body section (210) is a fan-shaped cavity with the axis (A) of the valve core (20) as the center.

5. The fluid management valve (1) according to claim 1, wherein the throttling section (211) is an elongated groove and extends from a connection with the main body section (210) toward a direction away from the main body section (210).

6. The fluid management valve (1) according to claim 1, wherein the valve port further comprises a third valve port (94), a fourth valve port (95), a fifth valve port (91) and a sixth valve port (92); the valve core (20) further comprises a second flow channel (22) and a third flow channel (23); When the valve core (20) is located at the fully open position and the throttling position, the second flow channel (22) is connected to the third valve port (94) and the fourth valve port (95), and the third flow channel (23) is connected to the fifth valve port (91) and the sixth valve port (92).

7. The fluid management valve (1) according to claim 6, wherein the first flow channel (21), the second flow channel (22) and the third flow channel (23) are arranged in layers along the axis (A) of the valve core (20) and are independent of each other.

8. The fluid management valve (1) according to claim 6, wherein the valve core (20) further has a first communication position relative to the valve body (10); the valve core (20) further has a fourth flow channel (24), a fifth flow channel (25) and a sixth flow channel (26); When the valve core (20) is located at the first connecting position, the fourth flow channel (24) connects the first valve port (96) and the sixth valve port (92); the fifth flow channel (25) connects the second valve port (93) and the fourth valve port (95); and the sixth flow channel (26) connects the fifth valve port (91) and the third valve port (94).

9. The fluid management valve (1) according to claim 6, wherein the valve core (20) further has a second communication position relative to the valve body (10); the valve core (20) further has a seventh flow channel (27), an eighth flow channel (28) and a blocking portion (29); When the valve core (20) is located at the second communication position, the seventh flow channel (27) is connected to the first valve port (96) and the sixth valve port (92); the eighth flow channel (28) is connected to the third valve port (94) and the fourth valve port (95); The blocking portion (29) blocks the fifth valve port (91).

10. The fluid management valve (1) of claim 1, wherein the peripheral wall (200) is a tapered wall.

11. The fluid management valve (1) according to claim 6, wherein the valve body (10) comprises a main body (100) and a sealing member (101); the sealing member (102) is arranged in the main body (100); the valve port passes through the main body (10) and the sealing member (101); in, The sealing member (101) is arranged between the outer peripheral wall (200) of the valve core (20) and the main body (100) along the radial direction of the valve core (20).

12. The fluid management valve (1) according to claim 1, wherein the valve core (20) is in the shape of a truncated cone.

13. The fluid management valve (1) according to claim 1, wherein the fluid management valve (1) further comprises an actuator (40) connected to the valve core (20) to drive the valve core (20) to rotate relative to the valve body (10).

14. A thermal management system for a vehicle, wherein the thermal management system comprises a fluid management valve (1) according to any one of claims 1 to 13.

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