WO2025055238A1 - 多通道阀门以及热管理系统 - Google Patents

多通道阀门以及热管理系统 Download PDF

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Publication number
WO2025055238A1
WO2025055238A1 PCT/CN2024/073085 CN2024073085W WO2025055238A1 WO 2025055238 A1 WO2025055238 A1 WO 2025055238A1 CN 2024073085 W CN2024073085 W CN 2024073085W WO 2025055238 A1 WO2025055238 A1 WO 2025055238A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
channel
flow channels
valve core
balancing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/CN2024/073085
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English (en)
French (fr)
Inventor
陈安邦
曲涛
孙宁
刘晓宇
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Johnson Electric International AG
Johnson Electric Guangdong Co Ltd
Original Assignee
Johnson Electric International AG
Johnson Electric Guangdong Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Johnson Electric International AG, Johnson Electric Guangdong Co Ltd filed Critical Johnson Electric International AG
Priority to CN202480003486.6A priority Critical patent/CN120712427A/zh
Priority to PCT/CN2024/073085 priority patent/WO2025055238A1/zh
Priority to EP24837827.5A priority patent/EP4545826A4/en
Priority to US19/036,177 priority patent/US20250237311A1/en
Publication of WO2025055238A1 publication Critical patent/WO2025055238A1/zh
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/072—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members
    • F16K11/074—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces
    • F16K11/0743—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces with both the supply and the discharge passages being on one side of the closure plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
    • F16K11/085—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug
    • F16K11/0853—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug having all the connecting conduits situated in a single plane perpendicular to the axis of the plug
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/04—Devices for relieving the pressure on the sealing faces for sliding valves
    • F16K39/045—Devices for relieving the pressure on the sealing faces for sliding valves of rotating or pivoting type

Definitions

  • the present invention relates to the field of valve technology, and in particular to a multi-channel valve and a thermal management system.
  • Multi-channel valves are common valves used to control fluid flow. For example, in the thermal management system of new energy vehicles, multi-channel valves are usually required to control the flow of coolant in different circuits. However, existing multi-channel valves have the problem of internal leakage, especially under high hydraulic pressure. Therefore, there is an urgent need for a multi-channel valve that can reduce or avoid internal leakage.
  • the present invention aims to provide a multi-channel valve and a thermal management system, wherein the multi-channel valve can reduce or avoid internal leakage.
  • the present invention provides a multi-channel valve, including a valve housing and a valve core rotatably arranged in the valve housing, the valve housing is provided with a plurality of valve ports, the valve core is provided with a plurality of flow channels, the two ends of each flow channel can be respectively connected to two of the valve ports of the valve housing, a plurality of buffer chambers are formed between the inner surface of the valve housing and the outer surface of the valve core, and the plurality of buffer chambers are sealed and separated from each other, a plurality of balancing holes are provided on the valve core, each balancing hole is arranged corresponding to a corresponding flow channel, and each of the buffer chambers is connected to the corresponding flow channel through the balancing hole.
  • the present invention provides a thermal management system, which includes the aforementioned multi-channel valve and multiple heat exchange branches, and the two ends of each heat exchange branch are connected to the corresponding two valve ports, thereby forming a closed fluid circuit through the corresponding flow channels.
  • the multi-channel valve of the present invention even when the valve core has a high fluid pressure, part of the fluid in the valve core can be discharged to the corresponding buffer chamber through the balancing hole, and the fluid pressure in the buffer chamber and the fluid pressure in the valve core can be balanced through the balancing hole, thereby reducing the squeezing and impact of the high-pressure fluid on the valve core, and further reducing or avoiding the internal leakage caused thereby.
  • FIG1 is a perspective schematic diagram of a multi-channel valve according to an embodiment of the present invention.
  • FIG2A is a cross-sectional view of the multi-channel valve shown in FIG1 ;
  • FIG2B is an enlarged view of A of the multi-channel valve shown in FIG2A ;
  • FIG3 is an exploded view of the multi-channel valve shown in FIG1 ;
  • FIG4 is an exploded view of the lower valve housing, the first sealing ring, and the sealing gasket of the multi-channel valve shown in FIG3 ;
  • FIG5 is an exploded view of the preload member, each sealing ring and the corrugated gasket of the multi-channel valve shown in FIG2A;
  • FIG6 is a top view of the valve core body and the cover plate of the multi-channel valve shown in FIG3 , wherein the valve core body is shown in dotted lines;
  • FIG. 7 is a simplified schematic diagram of a thermal management system according to an embodiment of the present invention.
  • a multi-channel valve 1 according to an embodiment of the present invention comprises a valve housing 10 and a valve core 20 rotatably disposed in the valve housing 10.
  • the valve housing 10 is provided with a plurality of valve ports 31.
  • the valve core 20 is provided with a plurality of flow channels 32. The two ends of each flow channel 32 can be respectively connected to two of the valve ports 31 of the valve housing 10.
  • a plurality of buffer chambers 40 are formed between the inner surface of the valve housing 10 and the outer surface of the valve core 20, and the plurality of buffer chambers 40 are sealed and separated from each other.
  • valve core 20 has a higher fluid pressure (such as the hydraulic pressure from the coolant)
  • part of the fluid in the valve core 20 can be discharged to the corresponding buffer chamber 40 through the balancing hole 50, and the fluid pressure in the buffer chamber 40 and the fluid pressure in the valve core 20 can be balanced through the balancing hole 50, thereby reducing the squeezing and impact of the high-pressure fluid on the valve core 20, and further reducing or avoiding the internal leakage caused thereby.
  • the valve port 31 is arranged on a plane perpendicular to the rotation axis of the valve housing 10.
  • the fluid flows axially from one of the valve ports 31 into the flow channel 32, and flows axially from the flow channel 32 to the other valve port 31.
  • the balancing hole 50 also extends axially, so as to more effectively reduce the axial pressure caused by the high-pressure fluid on the valve core 20, and the effect of reducing or avoiding internal leakage is better.
  • the valve housing 10 includes an upper valve housing 11 and a lower valve housing 12 of split design, and the upper valve housing 11 and the lower valve housing 12 are fixedly connected (e.g., by screws).
  • the upper valve housing 11 and the lower valve housing 12 are sealed and connected by a first sealing ring 13.
  • the valve port 31 is defined by the lower valve housing 12.
  • the main body of the lower valve housing 12 is roughly cylindrical, including a bottom wall 120, a peripheral wall 121, and a diaphragm 122 axially spaced from the bottom wall 120 and surrounded by the peripheral wall 121.
  • the bottom wall 120 and the peripheral wall 121 together enclose a cavity, and the diaphragm 122 is roughly located in the axial middle position of the cavity to divide the cavity into an upper cavity and a lower cavity.
  • the valve port 31 is arranged on the diaphragm 122.
  • the lower valve housing 12 is further provided with a plurality of radially distributed longitudinal partitions 123 between the transverse partition 31c and the wall 120 (i.e., in the lower cavity), thereby forming a plurality of valve housing cavities 124 between the transverse partition 31c and the bottom wall 120.
  • the valve housing cavities 124 are in one-to-one communication with the valve ports 31.
  • a plurality of valve housing ports 125 are protrudingly provided on the outer side of the peripheral wall 121 of the lower valve housing 12 corresponding to the valve housing cavities 124.
  • the valve housing ports 125 are in one-to-one communication with the valve housing cavities 124.
  • valve core 20 includes a valve core body 21 and a cover plate 22 of separate design, wherein the cover plate 22 covers the axial top end of the valve core body 21 and is fixedly connected to the valve core body 21 (for example, by means of clamping, bonding, welding, etc.).
  • each of the flow passages 32 includes two valve core ports 32a separated from each other and a valve core cavity 32b communicating with the two valve core ports 32a.
  • the valve core port 32a is provided at the bottom end of the valve core body 21 (i.e., the second axial end 202 of the valve core 20) and axially penetrates the second axial end 202, and the valve core port 32a is used to communicate with the corresponding valve port 31.
  • the valve core cavity 32b is defined by a valve core partition 32c in the valve core body 21.
  • the fluid will flow from one of the valve ports 31 (the fluid flows into the valve port 31 through the corresponding valve housing port 125 and the valve housing cavity 124) to the valve core cavity 32b along the axial direction through one of the valve core ports 32a, and then flow out from the valve core cavity 32b along the axial direction through the other valve core port 32a to the other valve port 31 (the fluid is discharged through the corresponding valve housing port 125 and the valve housing cavity 124).
  • the first flow channel 321 is connected to the first valve port 311 and the seventh valve port 317
  • the second flow channel 322 is connected to the eighth valve port 318 and the ninth valve port 319
  • the third flow channel 323 is connected to the second valve port 312 and the third valve port 31
  • the fourth flow channel 324 is connected to the fourth valve port 314 and the sixth valve port 316
  • the fifth valve port 315 is blocked and not connected to any flow channel 32.
  • the valve core 20 can also rotate relative to the valve housing 10, so that in different states, each flow channel 32 can be connected to a different valve port 31.
  • the preload member 70 is generally in the shape of a disk, and has a through hole 700 in the center thereof for the rotation shaft 23 to pass through.
  • the axial upper end surface of the preload member 70 is sealedly connected to the axial lower end surface of the upper valve housing 11 (also one of the axial inner end surfaces of the valve housing 11), and the axial lower end surface of the preload member 70 includes a first convex portion 701 located radially outward and away from the rotation shaft 23, a second convex portion 702 located radially inward and close to the rotation shaft 23, and a first concave portion 703 and a second concave portion 704 located between the first convex portion 701 and the second convex portion 702.
  • the first protrusion 701 is provided with a plurality of engaging grooves 705, and the first protrusion 701 is accommodated between the first ring portion 221 and the second ring portion 222 of the cover plate 22, and each of the engaging portions 223 (as shown in FIG. 3 ) on the cover plate 22 is engaged with the corresponding engaging groove 705, thereby realizing the synchronous transmission connection between the preload member 70 and the cover plate 22.
  • the second ring portion 222 is inserted into the first recessed portion 703.
  • the second recessed portion 704 and the second protrusion 702 are located between the inner side of the second ring portion 222 and the rotating shaft 23.
  • an elastic corrugated gasket 704a can be arranged on the second recessed portion 704, and the corrugated gasket 704a is elastically supported between the preload member 70 and the cover plate 22 to improve the dynamic sealing effect between the cover plate 22 and the upper valve housing 11.
  • the outer circumferential wall and the inner circumferential wall of the first convex portion 701 respectively form a first step 706 and a second step 707
  • a second sealing ring 706a is arranged on the first step 706, and a third sealing ring 707a is arranged on the second step 707.
  • a third step 708 is also formed on the inner circumferential wall of the second convex portion 702, and a fourth sealing ring 708a is arranged on the third step 708.
  • the second sealing ring 706a is sealingly connected between the first ring portion 221 and the first convex portion 701, so as to seal and separate the buffer cavity 40 (hereinafter referred to as the first buffer cavity 41) corresponding to the area of the plate portion 220 located outside the first ring portion 221 from other buffer cavities 40.
  • the buffer cavity 40 hereinafter referred to as the first buffer cavity 41
  • the first buffer cavity 41 extends in the circumferential direction in a circular ring shape, and is formed by the axial lower end surface of the upper valve housing 11, the axial upper end surface of the plate portion 220, the inner peripheral wall of the valve housing 10, and the outer peripheral wall of the valve core 20 (as shown in FIG2A ).
  • the third sealing ring 707a is sealingly connected between the second ring portion 222 and the first convex portion 701, so that the second sealing ring 706a and the third sealing ring 707a seal and separate the buffer cavity 40 (hereinafter referred to as the second buffer cavity 42) corresponding to the area between the first ring portion 221 and the second ring portion 222 of the plate portion 220 from other buffer cavities 40.
  • the buffer cavity 40 hereinafter referred to as the second buffer cavity 42
  • the second buffer cavity 42 also extends circumferentially in a circular ring shape and is formed between the axial lower end surface of the upper valve shell 11 and the axial upper end surface of the plate portion 220, but the second buffer cavity 42 of this embodiment is formed by the first convex portion 701 and the area between the first ring portion 221 and the second ring portion 222 of the plate portion 220, and is located radially inside the first buffer cavity 41.
  • the fourth sealing ring 708a is sealingly connected between the second protrusion 702 and the rotating shaft 23, so that the third sealing ring 707a and the fourth sealing ring 708a seal and separate the buffer cavity 40 (hereinafter referred to as the third buffer cavity 43) corresponding to the area of the plate portion 220 located within the second ring portion 222 from other buffer cavities 40.
  • the third buffer cavity 43 also extends circumferentially in a circular ring shape and is formed between the axial lower end surface of the upper valve shell 11 and the axial upper end surface of the plate portion 220.
  • the third buffer cavity 43 of this embodiment is formed by the second recessed portion 704, the second protrusion 702 and the area of the plate portion 220 located within the second ring portion 222, and is located radially inside the second buffer cavity 42.
  • buffer chambers 41-43 are only shown as examples.
  • multiple buffer chambers 40 that are sealed and separated from each other can be formed between the axial lower end surface of the upper valve shell 11 and the axial upper end surface of the plate portion 220 by other structures/methods.
  • the number of buffer chambers 40 is not limited to the three buffer chambers 41-43 shown in the figure, but can be two or four or more buffer chambers 40. Accordingly, the relative positional relationship of each buffer chamber 40 is not limited to the positional relationship shown in the figure.
  • the area of the plate portion 220 located outside the first ring portion 221 (as mentioned above, corresponding to the first buffer cavity 41) is provided with two balancing holes 50 (hereinafter referred to as first balancing holes 51), and the first balancing holes 51 are communicated with the first buffer cavity 41.
  • first balancing holes 51 correspond to the fourth flow channel 324 communicated with the valve core body 21.
  • the plate portion 220 is provided with two balancing holes 50 (hereinafter referred to as second balancing holes 52) in the region between the first ring portion 221 and the second ring portion 222 (as mentioned above, corresponding to the second buffer cavity 42), and the second balancing holes 52 are connected to the second buffer cavity 42.
  • the second balancing holes 52 are radially offset inward relative to the first balancing holes 51.
  • the second balancing holes 52 correspond to the third flow channel 323 connected to the valve core body 21.
  • the area of the plate portion 220 located within the second ring portion 222 (as mentioned above, it corresponds to the third buffer cavity 43) is provided with two balancing holes 50 (hereinafter referred to as third balancing holes 53), and the third balancing holes 53 are connected to the third buffer cavity 43.
  • the third balancing holes 53 are radially offset inward relative to the second balancing holes 52.
  • the third balancing holes 53 correspond to the second flow channel 322 connected to the valve core body 21.
  • the first flow channel 321 of the valve core body 21 is not provided with the corresponding balancing hole 50. Therefore, in this embodiment, the total number of flow channels 32 of the valve core body 21 is greater than the number of flow channels 32 correspondingly provided with the balancing hole 50. Specifically, in this embodiment, the total number of flow channels 32 of the valve core body 21 is 4, and the number of flow channels 32 correspondingly provided with the balancing hole 50 is 3.
  • the total number of flow channels 32 of the valve core body 21 is greater than the number of buffer chambers 40.
  • the total number of flow channels 32 of the valve core body 21 is 4, and the number of buffer chambers 40 is 3 (as mentioned above, each buffer chamber 40 is connected to the corresponding flow channel 32 through the corresponding balancing hole 50, so the number of buffer chambers 40 is actually equivalent to the number of flow channels 32 correspondingly provided with the balancing hole 50).
  • each buffer cavity 40 is not limited to being connected to the corresponding flow channel 32 by the two balancing holes 50 shown in the figure, and each buffer cavity 40 may be connected to the corresponding flow channel 32 through one balancing hole 50 or three balancing holes 50 or more balancing holes 50.
  • an embodiment of the present invention further provides a thermal management system, comprising the aforementioned multi-channel valve 1 (which is briefly shown in FIG. 7 ), a plurality of heat exchange branches L, and a plurality of pumps P disposed on the branches L. Both ends of each heat exchange branch L are respectively communicated with the corresponding two valve housing ports 125 (as shown in FIG. 3 ) of the aforementioned multi-channel valve 1, thereby communicating with the corresponding flow channel 32 of the multi-channel valve 1 through the corresponding valve housing cavity 124 and the valve port 31, thereby forming a closed fluid circuit.
  • the thermal management system includes four heat exchange branches L (a first heat exchange branch L1, a second heat exchange branch L2, a third heat exchange branch L3, and a fourth heat exchange branch L4) and three pumps P (a first pump P1, a second pump P2, and a third pump P3), wherein the first pump P1 is arranged on the first heat exchange branch L1, the second pump P2 is arranged on the third heat exchange branch L3, the third pump P3 is arranged on the fourth heat exchange branch L4, and no pump P is arranged on the second heat exchange branch L2.
  • the two ends of the first heat exchange branch L1 are connected to the first valve port 311 and the second valve port 312 via the corresponding valve shell ports 125
  • the two ends of the second heat exchange branch L2 are connected to the fourth valve port 314 and the seventh valve port 317 via the corresponding valve shell ports 125
  • the two ends of the third heat exchange branch L3 are connected to the fifth valve port 315 and the sixth valve port 316 via the corresponding valve shell ports 125
  • the fourth heat exchange branch L4 is connected to the eighth valve port 318 and the ninth valve port 319 via the corresponding valve shell ports 125.
  • the first flow channel 321 connects the first valve port 311 and the seventh valve port 317
  • the second flow channel 322 connects the eighth valve port 318 and the ninth valve port 319
  • the third flow channel 323 connects the second valve port 312 and the fourth valve port 31
  • the fourth flow channel 324 connects the fifth valve port 315 and the sixth valve port 316
  • the third valve port 313 is blocked and not connected to any of the flow channels 321-324.
  • the first heat exchange branch L1, the third flow channel 323, the second heat exchange branch L2 and the first flow channel 321 are connected in series to form a fluid loop.
  • the second flow channel 322 is connected to the fourth heat exchange branch L4 to form a fluid loop.
  • the fourth flow channel 324 is connected to the third heat exchange branch L3 to form a fluid loop.
  • the fourth flow channel 324 is provided with the first balancing hole 51, and the third heat exchange branch L3 is provided with a second pump P2, thereby the fourth flow channel 324 and the third heat exchange branch L3 form a closed fluid loop, and the fluid flowing through the fourth flow channel 324 can be partially introduced into the corresponding first buffer chamber 41 through the first balancing hole 51, so that the first buffer chamber 41 is used to balance the fluid pressure of the fourth flow channel 324.
  • the second flow channel 322 is provided with the third balancing hole 53, and the fourth heat exchange branch L4 is provided with a third pump P3, thereby the second flow channel 322 and the fourth heat exchange branch L4 form a closed fluid loop, and the fluid flowing through the second flow channel 322 can be partially introduced into the corresponding third buffer chamber 41 through the third balancing hole 53, so that the fluid pressure of the second flow channel 322 can be balanced by the third buffer chamber 43.
  • the third flow channel 323 is provided with the second balancing hole 52, but the first flow channel 321 is not provided with the balancing hole 50.
  • the second heat exchange branch L2 is not provided with a pump P, but the first heat exchange branch L1 is provided with a first pump P1.
  • the first flow channel 321 and the third flow channel 323 are connected in series through the first heat exchange branch L1 and the second heat exchange branch L2 and form a closed fluid circuit together. Since the third flow channel 323 is provided with the second balancing hole 52 and the second buffer chamber 42, the second buffer chamber 42 can balance the fluid pressure of the first flow channel 321 and the third flow channel 323 at the same time.
  • the fluid pressure borne by the third flow channel 323 is greater than the fluid pressure borne by the first flow channel 321, that is, the fluid pressure borne by the third flow channel 323 corresponding to the second balancing hole 52 is greater than the fluid pressure borne by the first flow channel 321 not corresponding to the balancing hole 50, so as to more effectively reduce or avoid internal leakage of the multi-channel valve 1.
  • the first pump P1 is provided on the first heat exchange branch L1, and the fluid from the first heat exchange branch L1 is pumped out by the first pump P1 and first flows into the third flow channel 323, and then flows through the second heat exchange branch L2 and the first flow channel 321 not corresponding to the balancing hole.
  • the thermal management system may also include other numbers of heat exchange branches L and pumps P.
  • the connection method between each heat exchange branch L and the multi-channel valve 1 may also change, and the arrangement of the pump P may also be adjusted according to actual needs.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Multiple-Way Valves (AREA)

Abstract

一种多通道阀门以及热管理系统，多通道阀门（1）包括阀壳（10）以及转动设置于阀壳（10）内的阀芯（20），阀壳（10）设有多个阀口（31），阀芯（20）设有多个流道（32），每一流道（32）的两端可分别连通阀壳（10）的其中两个阀口（31）。多个缓冲腔（40）形成于阀壳（10）的内表面和阀芯（20）的外表面之间，且多个缓冲腔（40）彼此密封隔开，阀芯（20）上设有多个平衡孔（50），每一平衡孔（50）与一相应的流道（32）对应设置，每一缓冲腔（40）通过平衡孔（50）与相应的流道（32）连通，该多通道阀门（1）可以减少或者避免内部泄露。

Description

多通道阀门以及热管理系统 技术领域
本发明涉及阀门技术领域，具体涉及一种多通道阀门以及热管理系统。
 背景技术
多通道阀门是用于控制流体流动的常见阀门。例如，在新能源汽车的热管理系统中，通常需要多通道阀门以控制冷却剂在不同回路中的流动。然而，现有的多通道阀门存在内部泄露的问题，特别是在较高的液压情况下。因此，亟需一种可以减少或者避免内部泄露的多通道阀门。
发明内容
有鉴于此，本发明旨在提供一种多通道阀门以及热管理系统，所述多通道阀门可以减少或者避免内部泄露。
为此，本发明一方面提供一种多通道阀门，包括阀壳以及转动设置于所述阀壳内的阀芯，所述阀壳设有多个阀口，所述阀芯设有多个流道，每一流道的两端可分别连通所述阀壳的其中两个阀口，多个缓冲腔形成于所述阀壳的内表面和所述阀芯的外表面之间，且所述多个缓冲腔彼此密封隔开，所述阀芯上设有多个平衡孔，每一平衡孔与一相应的所述流道对应设置，每一所述缓冲腔通过所述平衡孔与相应的所述流道连通。
另一方面，本发明提供一种热管理系统，所述热管理系统包括前述的多通道阀门及多个热交换支路，每一热交换支路的两端连通相应的两个阀口，进而通过对应的流道而形成闭合的流体回路。
通过本发明的多通道阀门，即使在阀芯具有较高的流体压力的情况下，也可以通过平衡孔将阀芯内的部分流体排放至相应的缓冲腔，并通过所述平衡孔平衡缓冲腔的流体压力和阀芯内的流体压力，从而减少高压流体对阀芯的挤压、冲击，进而减小或避免由此导致的内部泄露。
 附图说明
图1是本发明一实施例的多通道阀门的立体示意图；
图2A是图1所示多通道阀门的剖视图；
图2B是图2A所示多通道阀门的A的放大图；
图3是图1所示多通道阀门的爆炸图；
图4是图3所示多通道阀门的下阀壳、第一密封圈、密封垫的爆炸图；
图5是图2A所示多通道阀门的预载件、各密封圈以及波形垫片的爆炸图；
图6是图3所示多通道阀门的阀芯体和盖板的俯视图，其中阀芯体以虚线示出；
图7是本发明一实施例的热管理系统的简要示意图。
具体实施方式
以下将结合附图以及具体实施方式对本发明进行详细说明，以使得本发明的技术方案及其有益效果更为清晰明了。可以理解，附图仅提供参考与说明用，并非用来对本发明加以限制，附图中显示的尺寸仅仅是为了便于清晰描述，而并不限定比例关系。
在本发明的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对发明的限制。此外，本文中的“多个”包括两个、三个、或者更多个。
参考图1、图2A和图3，本发明一实施例的多通道阀门1包括阀壳10以及转动设置于阀壳10内的阀芯20。所述阀壳10设有多个阀口31。所述阀芯20设有多个流道32。每一流道32的两端可分别连通所述阀壳10的其中两个阀口31。多个缓冲腔40形成于所述阀壳10的内表面和所述阀芯20的外表面之间，且所述多个缓冲腔40彼此密封隔开。所述阀芯20上设有多个平衡孔50，每一平衡孔50与一相应的流道32对应设置，且每一所述缓冲腔40通过相应的一个或多个所述平衡孔50与相应的所述流道32连通。
由此，即使在阀芯20具有较高的流体压力（例如来自冷却剂的液压）的情况下，也可以通过所述平衡孔50将阀芯20内的部分流体排放至相应的缓冲腔40，并通过所述平衡孔50平衡缓冲腔40的流体压力和阀芯20内的流体压力，从而减少高压流体对阀芯20的挤压、冲击，进而减小或避免由此导致的内部泄露。
如图2A至图3所示，本实施例中，所述阀口31设于所述阀壳10的垂直于其转动轴的平面。流体从其中一阀口31沿轴向流入流道32，并从该流道32沿轴向流出至另一阀口31。优选地，所述平衡孔50也沿轴向延伸，以便更有效地减少高压流体对阀芯20造成的轴向压力，减小或避免内部泄露的效果更佳。
具体地，同时参考图2A至图4，所述阀壳10包括分体设计的上阀壳11和下阀壳12，所述上阀壳11和所述下阀壳12（例如通过螺钉）固定连接。优选地，所述上阀壳11和所述下阀壳12之间通过第一密封圈13密封连接。本实施例中，所述阀口31由所述下阀壳12限定。
更具体地，所述下阀壳12主体大致为圆筒状，包括底壁120、周壁121及与底壁120轴向间隔设置并被所述周壁121环绕的横隔板122。所述底壁120与所述周壁121共同围合形成一腔，所述横隔板122大致位于所述腔内的轴向中部位置而将该腔分为上腔和下腔。所述阀口31设置在所述横隔板122上。作为示例，本实施例中，所述横隔板122上开设有沿周向依次分布的第一阀口311、第二阀口312、第三阀口313、第四阀口314、第五阀口315、第六阀口316、第七阀口317、第八阀口318以及第九阀口319，各阀口311-319彼此隔离、不连通。还应理解地，在其他实施例中，所述阀壳10也可以包括其他数量（例如八个）和/或布置的阀口31。
本实施例中，所述下阀壳12于所述横隔板31c与所述壁120之间（即所述下腔内）还设有若干呈辐射状分布的纵隔板123，从而在所述横隔板31c与所述底壁120之间形成多个阀壳腔124。所述阀壳腔124与所述阀口31一一对应连通。此外，所述下阀壳12的周壁121外侧还对应所述阀壳腔124突设若干阀壳端口125。所述阀壳端口125与所述阀壳腔124一一对应连通。
本实施例中，同时参考图2A和图3，所述阀芯20的一部分收容于所述下阀壳12的上腔内，另一部分收容于所述上阀壳11内。具体地，所述阀芯20包括分体设计的阀芯体21和盖板22，所述盖板22盖合于所述阀芯体21的轴向顶端并与所述阀芯体21固定连接（例如通过卡合、粘接、焊接等方式）。所述盖板22的中心一体连接有转轴23，所述转轴23的上端与所述上阀壳11转动连接，所述转轴23的下端穿过所述阀芯体21的中心的连接轴210并与所述下阀壳12转动连接。可以理解地，在其他实施例中，阀芯20也可一体成型。本实施例中，所述平衡孔50设于所述盖板22并沿轴向贯穿所述盖板22（即所述阀芯20的第一轴向端201）。所述流道32由所述阀芯体21限定。
具体地，如图3所示，每一所述流道32包括两个彼此相互隔开的阀芯端口32a以及连通两个阀芯端口32a的阀芯腔32b。所述阀芯端口32a设于所述阀芯体21的底端（即所述阀芯20的第二轴向端202）并轴向贯穿所述第二轴向端202，所述阀芯端口32a用于与对应的阀口31连通。所述阀芯腔32b由所述阀芯体21内的阀芯隔板32c限定。由此，流体将从其中一阀口31（流体通过相应的阀壳端口125和阀壳腔124流入阀口31）经由其中一阀芯端口32a沿轴向流入阀芯腔32b，然后从该阀芯腔32b经由另一阀芯端口32a沿轴向流出至另一阀口31（流体通过相应的阀壳端口125和阀壳腔124排出）。
作为示例，本实施例中，所述阀芯20包括彼此不连通的多个流道32，分别为第一流道321、第二流道322、第三流道323以及第四流道324，其中第一流道321沿径向横跨所述阀芯20，第二流道322位于第一流道321的径向一侧，第三流道323和第四流道324位于第一流道321的径向另一侧，且第二流道322、第三流道323以及第四流道324在阀芯20的周向上间隔分布。还应理解地，在其他实施例中，所述阀芯20也可以包括其他数量（例如三个）和/或布置的流道32。
所述第一流道321连通所述第一阀口311和所述第七阀口317，所述第二流道322连通所述第八阀口318和所述第九阀口319，所述第三流道323连通所述第二阀口312和所述第三阀口313，所述第四流道324连通所述第四阀口314和所述第六阀口316，所述第五阀口315封堵而不与任何流道32连通。如前所述，所述阀芯20还可相对所述阀壳10转动，由此，在不同状态下，各流道32可连通不同的阀口31。
还优选地，为提高所述阀芯20与所述阀壳10之间的动密封效果，所述阀芯20与所述阀壳10之间还布置一密封垫60。如图2A和图4所示，所述密封垫60布置在所述横隔板122和所述阀芯体21的底端之间，包括内圈61、外圈62以及连接内圈61和外圈62的多个肋部63。所述多个肋部63与所述多个纵隔板123相对应，且相邻肋部63之间形成一开口64，每一开口64与一相应的阀口31对应。
附加地或替换地，所述多通道阀门1还包括预载件70（图2A可见），所述预载件70布置于所述上阀壳11和所述盖板22之间，以为所述阀芯20与所述阀壳10之间的动密封提供压力，动密封效果更佳。进一步地，所述预载件70与所述上阀壳11和所述盖板22均密封连接，以提供前述的彼此密封隔开的多个缓冲腔40。
具体地，如图2B和图3所示，所述盖板22包括圆盘状的板部220、以及垂直固定于所述板部220的轴向上端面（也为阀芯20的其中一轴向外端面）的第一环部221和第二环部222。所述第一环部221与所述板部220的外周缘间隔一定距离。所述第二环部222位于所述第一环部221的内侧并与所述第一环部221间隔一定距离。进一步地，本实施例中，所述盖板22还包括位于第一环部221和第二环部222之间的沿周向间隔布置的多个卡合部223。
如图2B和图5所示，所述预载件70大体呈圆盘状，其中心具有一通孔700用于供所述转轴23穿设。本实施例中，所述预载件70的轴向上端面与所述上阀壳11的轴向下端面（也为阀壳11的其中一轴向内端面）密封连接，所述预载件70的轴向下端面包括位于径向外侧的远离所述转轴23的第一凸部701、位于径向内侧的靠近所述转轴23的第二凸部702、以及位于第一凸部701和第二凸部702之间的第一凹陷部703和第二凹陷部704。
所述第一凸部701上开设有多个卡合槽705，所述第一凸部701收容于所述盖板22的第一环部221和第二环部222之间，且盖板22上的各所述卡合部223（图3可见）接合至相应的卡合槽705，由此实现预载件70和盖板22的同步传动连接。所述第二环部222插入所述第一凹陷部703。所述第二凹陷部704和所述第二凸部702位于所述第二环部222的内侧和所述转轴23之间。优选地，所述第二凹陷部704上可以布置一弹性的波形垫片704a，波形垫片704a弹性支撑于预载件70和盖板22之间，以提高所述盖板22与所述上阀壳11之间的动密封效果。
进一步地，所述第一凸部701的外周壁和内周壁分别形成一第一台阶706和第二台阶707，第一台阶706上布置一第二密封圈706a，第二台阶707上布置一第三密封圈707a。所述第二凸部702的内周壁上也形成一第三台阶708，第三台阶708上布置一第四密封圈708a。
如图2B所示，第二密封圈706a密封连接于所述第一环部221和所述第一凸部701之间，从而将所述板部220的位于所述第一环部221之外的区域对应的缓冲腔40（下文称之为第一缓冲腔41）与其他缓冲腔40密封隔开。对应于所述板部220的位于所述第一环部221之外的区域的周向延伸方向，本实施例中，第一缓冲腔41在周向上延伸呈圆环状，由上阀壳11的轴向下端面、板部220的轴向上端面、阀壳10的内周壁和阀芯20的外周壁围合形成（图2A可见）。
如图2B所示，第三密封圈707a密封连接于所述第二环部222和所述第一凸部701之间，由此，第二密封圈706a和第三密封圈707a将所述板部220的位于第一环部221和所述第二环部222之间的区域对应的缓冲腔40（下文称之为第二缓冲腔42）与其他缓冲腔40密封隔开。对应于所述板部220的位于第一环部221和所述第二环部222之间的区域的周向延伸方向，本实施例中，第二缓冲腔42也沿周向延伸呈圆环状，且形成于上阀壳11的轴向下端面和板部220的轴向上端面之间，不过本实施例的第二缓冲腔42由第一凸部701和板部220的位于第一环部221和所述第二环部222之间的区域共同围合形成，并位于所述第一缓冲腔41的径向内侧。
如图2B所示，第四密封圈708a密封连接于所述第二凸部702和所述转轴23之间，由此，第三密封圈707a和第四密封圈708a将所述板部220的位于所述第二环部222之内的区域对应的缓冲腔40（下文称之为第三缓冲腔43）与其他缓冲腔40密封隔开。对应于所述板部220的位于所述第二环部222之内的区域的周向延伸方向，本实施例中，第三缓冲腔43也沿周向延伸呈圆环状，且形成于上阀壳11的轴向下端面和板部220的轴向上端面之间，不过本实施例的第三缓冲腔43由第二凹陷部704和第二凸部702以及板部220的位于第二环部222之内的区域共同围合形成，并位于所述第二缓冲腔42的径向内侧。
可以理解地，上述各缓冲腔41-43的形成方式仅作为示例示出，在其他实施例中，也可以通过其他构造/方式在上阀壳11的轴向下端面和板部220的轴向上端面之间形成彼此密封隔开的多个缓冲腔40。缓冲腔40的数量也并不限于图示的三个缓冲腔41-43，而可以是两个或者四个或者更多个缓冲腔40。相应地，各缓冲腔40的相对位置关系也并不限于图示所示的位置关系。
同时结合图2B和图6所示，本实施例中，所述板部220的位于所述第一环部221的外侧的区域（如前所述，其对应于所述第一缓冲腔41）设有两个所述平衡孔50（下文称之为第一平衡孔51），所述第一平衡孔51与所述第一缓冲腔41连通。特别地，本实施例中，所述第一平衡孔51对应连通所述阀芯体21的所述第四流道324。
所述板部220的位于第一环部221和所述第二环部222之间的区域（如前所述，其对应于所述第二缓冲腔42）设有两个所述平衡孔50（下文称之为第二平衡孔52），所述第二平衡孔52与所述第二缓冲腔42连通。对应于所述第二缓冲腔42位于所述第一缓冲腔41的径向内侧的位置关系，本实施例中，所述第二平衡孔52相对所述第一平衡孔51径向向内偏移。特别地，本实施例中，所述第二平衡孔52对应连通所述阀芯体21的所述第三流道323。
所述板部220的位于所述第二环部222之内的区域（如前所述，其对应于所述第三缓冲腔43）设有两个所述平衡孔50（下文称之为第三平衡孔53），所述第三平衡孔53与所述第三缓冲腔43连通。对应于所述第三缓冲腔43位于所述第二缓冲腔42的径向内侧的位置关系，本实施例中，所述第三平衡孔53相对所述第二平衡孔52径向向内偏移。特别地，所述第三平衡孔53对应连通所述阀芯体21的所述第二流道322。
从图6可见，本实施例中，所述阀芯体21的所述第一流道321未对应设置所述平衡孔50。因此，本实施例中，所述阀芯体21的总的流道32的数量大于对应设置有平衡孔50的流道32的数量，具体地，在本实施例中，所述阀芯体21的总的流道32的数量为4个，而对应设置有平衡孔50的流道32的数量为3个。
或者说本实施例中，所述阀芯体21的总的流道32的数量大于缓冲腔40的数量，具体地，在本实施例中，所述阀芯体21的总的流道32的数量为4个，缓冲腔40的数量为3个（如前所述，每一缓冲腔40通过相应的平衡孔50与相应的流道32连通，因此缓冲腔40的数量实际上等同于对应设置有平衡孔50的流道32的数量）。
可以理解地，在其他实施例中，并不一定是所述第一流道321未对应设置平衡孔50，也可以是其他流道32未对应设置平衡孔50。或者，还可以是两个或更多个流道32未对应设置平衡孔50。或者，每一缓冲腔40也不限于图示的两个平衡孔50与相应的流道32连通，每一缓冲腔40可以通过一个平衡孔50或者三个平衡孔50或者更多个平衡孔50与相应的流道32连通。
同时参考图7，本发明一实施例还提供了一种热管理系统，包括前述多通道阀门1（其在图7中简要示出）、多个热交换支路L以及设置在所述支路L上的若干泵P。每一热交换支路L的两端分别与前述的多通道阀门1的相应的两个阀壳端口125（如图3所示）连通，从而通过相应的所述阀壳腔124、阀口31与多通道阀门1的相应的流道32连通，从而形成闭合的流体回路。
作为示例，本实施例中，所述热管理系统包括四个热交换支路L（第一热交换支路L1、第二热交换支路L2、第三热交换支路L3、第四热交换支路L4）以及三个泵P（第一泵P1、第二泵P2、第三泵P3），其中第一泵P1设置在第一热交换支路L1上，第二泵P2设置在第三热交换支路L3上，第三泵P3设置在第四热交换支路L4上，而第二热交换支路L2上未设置泵P。
本实施例中，第一热交换支路L1的两端分别经由对应的阀壳端口125与第一阀口311和第二阀口312连通，第二热交换支路L2的两端分别经由对应的阀壳端口125与第四阀口314和第七阀口317连通，第三热交换支路L3的两端分别经由对应的阀壳端口125与第五阀口315和第六阀口316连通，第四热交换支路L4分别经由对应的阀壳端口125与第八阀口318和第九阀口319连通。
在图7中，所述第一流道321连通所述第一阀口311和所述第七阀口317，所述第二流道322连通所述第八阀口318和所述第九阀口319，所述第三流道323连通所述第二阀口312和所述第四阀口314，所述第四流道324连通所述第五阀口315和所述第六阀口316，而所述第三阀口313封堵而不与流道321-324中的任一个连通。
由此，如图7所示，所述第一热交换支路L1、所述第三流道323、所述第二热交换支路L2及所述第一流道321依次串联形成一流体回路。所述第二流道322与第四热交换支路L4连通形成一流体回路。所述第四流道324与第三热交换支路L3连通形成一流体回路。
同时结合图6和图7，如前所述，所述第四流道324对应设置所述第一平衡孔51，而所述第三热交换支路L3上设有第二泵P2，由此所述第四流道324与第三热交换支路L3形成闭合的流体回路，且可以通过所述第一平衡孔51将流经所述第四流道324的流体部分引入对应的第一缓冲腔41，从而利用第一缓冲腔41平衡第四流道324的流体压力。所述第二流道322对应设置所述第三平衡孔53，而所述第四热交换支路L4上设有第三泵P3，由此所述第二流道322与第四热交换支路L4形成闭合的流体回路，且可以通过所述第三平衡孔53将流经所述第二流道322的流体部分引入对应的第三缓冲腔41，从而利用第三缓冲腔43平衡第二流道322的流体压力。所述第三流道323对应设置所述第二平衡孔52，但所述第一流道321未对应设置所述平衡孔50，所述第二热交换支路L2上未设置泵P，但所述第一热交换支路L1上设置有第一泵P1。如前所述，第一流道321和第三流道323通过所述第一热交换支路L1和所述第二热交换支路L2串联并共同形成闭合的流体回路。而由于第三流道323对应设置有第二平衡孔52和第二缓冲腔42，因此，第二缓冲腔42可以同时平衡第一流道321和第三流道323的流体压力。
由此可见，如图6和图7所示，本实施例中虽然并不是所有流道321-324都对应设有平衡孔50和相应的缓冲腔40，但是所有流道321-324都与平衡孔50以及相应的缓冲腔40连通，且每一流体回路都与平衡孔50以及相应的缓冲腔40连通。因此，本实施例的热管理系统可以有效地减少或避免多通道阀门1内部各流体回路之间相互泄露，即使是在较高的液压情况下。
优选地，所述第三流道323 所承受的流体压力大于所述第一流道321所承受的流体压力，即对应设置有第二平衡孔52的第三流道323所承受的流体压力大于未对应设置有平衡孔50的第一流道321所承受的流体压力，以更有效地减少或避免多通道阀门1内部泄露。具体而言，本实施方式中，所述第一热交换支路L1上设置有第一泵P1，流体从而第一热交换支路L1由所述第一泵P1泵出后先流入第三流道323，再依次流过第二热交换支路L2及未对应设置所述平衡孔的第一流道321。可以理解，在流体回路中，第三流道323离所述第一泵P1的下游近，所以所述第三流道323内的流体压力较高。对应地，第一流道321离所述第一泵P1的下游较远，从而使得所述第一流道321内的流体压力较低。可以理解地，以上仅作为示例示出，在其他实施例中，热管理系统还可以包括其他数量的热交换支路L和泵P，各热交换支路L与多通道阀门1的连接方式也可能发生改变，泵P的布置也可能根据实际需要而调整。
以上所述仅为本发明较佳的具体实施方式，本发明的保护范围不限于以上列举的实施例，任何熟悉本技术领域的技术人员在本发明披露的技术范围内，可显而易见地得到的技术方案的简单变化或等效替换均落入本发明的保护范围内。

Claims (16)

  1. 一种多通道阀门，包括阀壳以及转动设置于所述阀壳内的阀芯，所述阀壳设有多个阀口，所述阀芯设有多个流道，每一流道的两端可分别连通所述阀壳的其中两个阀口，其特征在于，多个缓冲腔形成于所述阀壳的内表面和所述阀芯的外表面之间，且所述多个缓冲腔彼此密封隔开，所述阀芯上设有多个平衡孔，每一平衡孔与一相应的所述流道对应设置，每一所述缓冲腔通过所述平衡孔与相应的所述流道连通。
  2. 根据权利要求1所述的多通道阀门，其特征在于，所述阀壳于垂直转动轴的平面设有所述多个阀口，且流体适于从其中一所述阀口沿轴向流入所述流道和/或从所述流道沿轴向流出至另一所述阀口。
  3. 根据权利要求2所述的多通道阀门，其特征在于，所述阀芯包括相对的第一轴向端和第二轴向端，所述平衡孔设于所述阀芯的所述第一轴向端并轴向贯穿所述第一轴向端，每一所述流道包括设于所述阀芯的所述第二轴向端并轴向贯穿所述第二轴向端的两个阀芯端口，所述阀芯端口用于与对应的阀口连通。
  4. 根据权利要求1所述的多通道阀门，其特征在于，所述缓冲腔至少形成于所述阀芯的一轴向外端面和所述阀壳的一轴向内端面之间，每一所述缓冲腔在周向上延伸，所述多个缓冲腔相对彼此在径向上间隔分布使得多个所述缓冲腔对应的所述平衡孔也相对彼此在径向上偏移。
  5. 根据权利要求1所述的多通道阀门，其特征在于，每一缓冲腔呈圆环状。
  6. 根据权利要求1或5所述的多通道阀门，其特征在于，还包括预载件，所述预载件密封连接于所述阀壳和所述阀芯之间，且至少部分所述缓冲腔形成于所述预载件和所述阀芯之间。
  7. 根据权利要求6所述的多通道阀门，其特征在于，所述阀芯包括阀芯体以及盖设于所述阀芯体一轴向端的盖板，所述盖板包括板部以及垂直设于所述板部的一轴向端面的第一环部和第二环部，所述多个缓冲腔包括形成于所述第一环部径向外侧的第一缓冲腔、形成于所述第一环部和所述第二环部之间的第二缓冲腔以及形成于所述第二环部径向内侧的第三缓冲腔，所述第一缓冲腔、第二缓冲腔、第三缓冲腔彼此密封隔开。
  8. 根据权利要求7所述的多通道阀门，其特征在于，所述盖板的中心设有转轴；所述预载件包括径向远离所述转轴的第一凸部以及径向靠近所述转轴的第二凸部；所述第一凸部收容于所述第一环部和所述第二环部之间，并在其间形成所述第二缓冲腔；所述第二凸部收容于所述第二环部和所述转轴之间，并在其间形成所述第三缓冲腔。
  9. 根据权利要求1所述的多通道阀门，其特征在于，所述流道的数量大于对应设置有所述平衡孔的流道的数量。
  10. 根据权利要求1或9所述的多通道阀门，其特征在于，所述多个流道包括对应设置有所述平衡孔的流道以及未对应设置所述平衡孔的流道，对应设置有所述平衡孔的流道可通过外界支路与未对应设置所述平衡孔的流道串联。
  11. 根据权利要求10所述的多通道阀门，其特征在于，对应设置有所述平衡孔的流道所承受的流体压力大于未对应设置所述平衡孔的流道所承受的流体压力。
  12. 一种热管理系统，其特征在于，所述热管理系统包括权利要求1至8中任一项所述的多通道阀门及多个热交换支路，每一热交换支路的两端连通相应的两个阀口，进而通过对应的流道而形成闭合的流体回路。
  13. 根据权利要求12所述的热管理系统，其特征在于，所述流道的数量大于对应设置有所述平衡孔的流道的数量。
  14. 根据权利要求13所述的热管理系统，其特征在于，所述多个流道包括对应设置有所述平衡孔的流道以及未对应设置所述平衡孔的流道，所述多个热交换支路包括第一热交换支路和第二热交换支路，所述第一热交换支路、对应设置有所述平衡孔的流道、未对应设置所述平衡孔的流道及所述第二热交换支路依次串联形成一流体回路，其中对应设置有所述平衡孔的流道中的流体压力大于未对应设置所述平衡孔的流道中的流体压力。
  15. 根据权利要求14所述的热管理系统，其特征在于，所述第一热交换支路上设有泵，所述第二热交换支路上未设泵，流体从所述第一支路流出后先流入对应设置有所述平衡孔的流道，再依次流过第二热交换支路及未对应设置所述平衡孔的流道。
  16. 根据权利要求13所述的热管理系统，其特征在于，每一所述流体回路均通过相应的一个或多个所述平衡孔与一所述缓冲腔连通。
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