WO2024244655A1 - 泄压阀及空调系统 - Google Patents

泄压阀及空调系统 Download PDF

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Publication number
WO2024244655A1
WO2024244655A1 PCT/CN2024/084341 CN2024084341W WO2024244655A1 WO 2024244655 A1 WO2024244655 A1 WO 2024244655A1 CN 2024084341 W CN2024084341 W CN 2024084341W WO 2024244655 A1 WO2024244655 A1 WO 2024244655A1
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WIPO (PCT)
Prior art keywords
valve
cavity
guide sleeve
valve core
valve port
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.)
Ceased
Application number
PCT/CN2024/084341
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English (en)
French (fr)
Inventor
林元阳
俞舟
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Zhejiang Dunan Artificial Environment Co Ltd
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Zhejiang Dunan Artificial Environment Co Ltd
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Publication date
Application filed by Zhejiang Dunan Artificial Environment Co Ltd filed Critical Zhejiang Dunan Artificial Environment Co Ltd
Priority to KR1020257042209A priority Critical patent/KR20260008157A/ko
Publication of WO2024244655A1 publication Critical patent/WO2024244655A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0209—Check valves or pivoted valves
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member

Definitions

  • the present application relates to the field of valve technology, and in particular to a pressure relief valve and an air conditioning system.
  • the pressure relief valve is installed in the air conditioning system. Normally, the compression spring of the pressure relief valve pushes the valve core to block the valve port, so that the valve port is in a closed state. When a high-pressure fluid flows through the valve port, the high-pressure fluid pushes the valve core to overcome the elastic force of the compression spring to push the valve port open and open the valve core. However, when the pressure of the high-pressure fluid flowing through the valve port fluctuates greatly, the high-pressure fluid impacts the end of the valve core, making it easy for the valve core to vibrate when it moves.
  • a pressure relief valve and an air conditioning system are provided.
  • a pressure relief valve comprising a valve body assembly, a valve core and a guide sleeve.
  • the valve body assembly is provided with a valve cavity and a valve port connected to the valve cavity, and the valve core is movably arranged in the valve cavity to open or close the valve port.
  • the guide sleeve is arranged in the valve cavity, and one of the valve core and the guide sleeve is movably sleeved on the other, so that an end of the valve core away from the valve port cooperates with an end of the guide sleeve close to the valve port to form a buffer cavity, and a side wall of the valve core and a side wall gap of the guide sleeve cooperate to form a first flow channel, the first flow channel connects the valve cavity and the buffer cavity, and the flow area of the first flow channel is smaller than the flow area of the buffer cavity.
  • the diameter of the side wall of the valve core for cooperating with the guide sleeve is The diameter of the side wall of the guide sleeve used to cooperate with the valve core is Satisfies, ⁇ d 1 ⁇ 0.01mm. It can be understood that such a configuration enables the fluid to flow from the buffer chamber through the first flow The liquid is discharged slowly into the valve chamber.
  • the axial direction of the valve cavity is defined as the length direction of the first flow channel, and the length l 1 of the first flow channel satisfies l 1 ⁇ 10 mm. It can be understood that such a configuration enables the fluid to be slowly discharged from the buffer cavity into the valve cavity through the first flow channel.
  • valve core sleeve is arranged on the outside of the guide sleeve, the outer wall of the valve core and the inner wall of the valve cavity are gap-matched to form a second flow channel, and the flow area of the second flow channel is smaller than the flow area of the valve port.
  • the flow area s 1 of the second flow channel and the flow area s 2 of the valve port satisfy 0.8s 2 ⁇ s 1 ⁇ 0.9s 2 . It can be understood that such a configuration is conducive to more stably supporting the valve core to open the valve port.
  • the outer wall of the valve core is provided with a plurality of cut surfaces, each of which penetrates both ends of the valve core along the axial direction of the valve core, and the plurality of cut surfaces are evenly distributed along the axial direction of the valve core. It can be understood that such a configuration facilitates the high-pressure fluid to flow between the cut surface and the inner wall of the valve cavity, and can avoid the problem of eccentric jamming during the movement of the valve core.
  • the pressure relief valve further includes a compression spring, which is installed in the buffer chamber, one end of the compression spring is connected to the guide sleeve, and the other end is connected to the valve core, and the compression spring has a tendency to push the valve core toward the valve port. It can be understood that such a configuration facilitates the compression spring to push the valve core to close the valve port.
  • the pressure relief valve further comprises an adjusting block, one end of the guide sleeve away from the valve port is connected to the adjusting block, and the outer wall of the adjusting block is threadedly matched with the inner wall of the valve cavity, so that the adjusting block can drive the guide sleeve to be movably installed in the valve cavity along the axial direction of the valve cavity. It can be understood that, in such an arrangement, the pressure required for opening the valve can be adjusted by the installation position of the adjusting block.
  • the valve core includes a sleeve, a sealing head and a sealing member, wherein the sleeve is sleeved on the outer periphery of the guide sleeve, the sealing head is connected to one end of the sleeve close to the valve port, and the sealing member is sleeved between the sleeve and the sealing member.
  • the sealing head can be inserted into or separated from the valve port to close or open the valve port, and when the sealing head is inserted into the valve port, the inner wall of the valve port can squeeze the sealing member along the radial direction of the valve port. It can be understood that such an arrangement makes the valve port and the valve core seal more tightly when the valve port is closed to avoid internal leakage.
  • the cross-sectional area of the valve port gradually decreases along the direction from the sleeve to the sealing head, and a stop step is provided at the connection between the sleeve and the sealing head.
  • the stop step stops at the outer periphery of the valve port along the axial direction of the valve cavity.
  • the present application also provides an air conditioning system, which includes the pressure relief valve described in any one of the above embodiments.
  • FIG. 1 is a cross-sectional view of a pressure relief valve according to an embodiment of the present application.
  • FIG. 2 is a partial cross-sectional view of an embodiment provided in the present application.
  • FIG. 3 is an enlarged schematic diagram of point B in FIG. 2 .
  • Fig. 4 is a cross-sectional view of Fig. 2 taken along line A-A.
  • FIG. 5 is a schematic diagram of the structure of a valve core according to an embodiment of the present application.
  • FIG. 6 is a cross-sectional view of a pressure relief valve according to another embodiment of the present application.
  • FIG. 7 is a cross-sectional view of a pressure relief valve according to another embodiment of the present application.
  • FIG8 is a cross-sectional view of a pressure relief valve according to yet another embodiment of the present application.
  • Illustration numerals 100, valve body assembly; 110, valve seat; 111, valve cavity; 112, valve port; 113, snap-fit groove; 120, valve tube; 121, snap-fit protrusion; 200, guide sleeve; 300, valve core; 310, sleeve; 311, cut surface; 320, sealing head; 330, sealing element; 340, stop step; 350, snap-fit groove; 360, annular protrusion; 370, spherical plug; 400, first flow channel; 500, second flow channel; 600, compression spring; 700, adjusting block; 710, mounting through hole; 720, adjusting groove; 800, buffer cavity.
  • first and second are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as “first” and “second” may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality” is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.
  • a first feature is “above” or “below” a second feature.
  • the first feature may be in direct contact with the second feature, or the first feature may be in indirect contact with the second feature through an intermediate medium.
  • the first feature being “above”, “above” and “above” the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature.
  • the first feature being “below”, “below” and “below” the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.
  • the pressure relief valve includes a valve body assembly 100, a valve core 300 and a guide sleeve 200.
  • the valve body assembly 100 is provided with a valve cavity 111 and a valve port 112 connected to the valve cavity 111.
  • the valve core 300 can be movably arranged in the valve cavity 111 to open or close the valve port 112.
  • the guide sleeve 200 is arranged in the valve cavity 111, and one of the valve core 300 and the guide sleeve 200 is movably sleeved on the other, so that the end of the valve core 300 away from the valve port 112 cooperates with the end of the guide sleeve 200 close to the valve port 112 to form a buffer cavity 800, and one or both of the valve core 300 and the guide sleeve 200 are provided with a first flow channel 400, the first flow channel 400 connects the valve cavity 111 and the buffer cavity 800, and the flow area of the first flow channel 400 is smaller than the flow area of the buffer cavity 800.
  • the first flow channel 400 there are two ways to set the first flow channel 400. As shown in FIG. 1 and FIG. 2, when the valve core 300 is sleeved on the outer side of the guide sleeve 200, the inner wall of the valve core 300 and the outer wall of the guide sleeve 200 are gap-matched to form the first flow channel 400. Alternatively, when the guide sleeve 200 is sleeved on the outer side of the valve core 300, The outer wall of the valve core 300 and the inner wall of the guide sleeve 200 are clearance-matched to form a first flow channel 400 .
  • one of the valve core 300 and the guide sleeve 200 is movably mounted on the other, so that the end of the valve core 300 away from the valve port 112 cooperates with the end of the guide sleeve 200 close to the valve port 112 to form a buffer chamber 800. Therefore, when the high-pressure fluid flows through the valve port 112 and impacts the end of the valve core 300, the high-pressure fluid pushes the valve core 300 to move upward and compresses the buffer chamber 800.
  • the first flow channel 400 connects the valve chamber 111 and the buffer chamber 800. Therefore, the fluid in the buffer chamber 800 will be discharged from the buffer chamber 800 through the first flow channel 400.
  • the buffer chamber 800 can produce a certain resistance to the valve core 300, thereby consuming the impact kinetic energy of the high-pressure fluid, that is, the buffer chamber 800 can produce a buffering effect, which can reduce the vibration caused by the frequent reciprocating motion of the valve core 300 due to the huge pressure fluctuation of the valve core 300 toward the valve port 112 during the operation of the valve core 300, thereby improving the operation stability of the valve core 300 and reducing the noise when opening the valve.
  • the side wall diameter of the valve core 300 used to cooperate with the guide sleeve 200 is The diameter of the side wall of the guide sleeve 200 for cooperating with the valve core 300 is It satisfies that ⁇ d 1 ⁇ 0.01 mm, and the axial direction of the valve cavity 111 is defined as the length direction of the first flow channel 400 , and the length l 1 of the first flow channel 400 satisfies that l 1 ⁇ 10 mm.
  • the flow area of the first flow channel 400 is small and the flow length is long, that is, the resistance of the fluid along the first flow channel 400 is appropriate, which is conducive to the fluid slowly being discharged from the buffer chamber 800 through the first flow channel 400 into the valve chamber 111, that is, the buffer chamber 800 has a suitable pressure relief capacity.
  • This can avoid the buffer chamber 800 from releasing pressure too quickly, leading to poor shock filtering effect of the buffer chamber 800. It can also avoid the buffer chamber 800 from releasing pressure too slowly, causing the buffer chamber 800 to generate greater resistance to the valve core 300, making it difficult to open the valve port 112.
  • the valve core 300 is sleeved on the outer side of the guide sleeve 200 .
  • the outer wall of the valve core 300 is gap-matched with the inner wall of the valve cavity 111 to form a second flow channel 500 .
  • the flow area of the second flow channel 500 is smaller than the flow area of the valve port 112 .
  • the second flow channel 500 can throttle the high-pressure fluid, so that the side of the valve core 300 close to the valve port 112 and the side of the valve core 300 away from the valve port 112 maintain a pressure difference of appropriate size, so as to push the valve core 300 to move toward the direction close to the guide sleeve 200 and compress the fluid in the buffer chamber 800.
  • Such a configuration can prevent the second flow channel 500 from having too strong a pressure relief capacity, so that the pressure difference between the side of the valve core 300 close to the valve port 112 and the side of the valve core 300 away from the valve port 112 is insufficient to support the valve core, and further cause the valve core 300 to move unsteadily, or even fall back and block the valve port 112.
  • the flow area s 1 of the second flow channel 500 and the flow area s 2 of the valve port 112 satisfy 0.8s 2 ⁇ s 1 ⁇ 0.9s 2 .
  • s 1 0.8s 2
  • the specific conditions can be determined according to actual conditions and are not listed here one by one.
  • the outer wall of the valve core 300 is provided with a plurality of cut surfaces 311, each of the cut surfaces 311 passes through both ends of the valve core 300 along the axial direction of the valve core 300, and the plurality of cut surfaces 311 are evenly distributed along the circumference of the valve core 300.
  • the high-pressure fluid can flow between the cut surface 311 and the inner wall of the valve cavity 111, and by setting multiple cut surfaces 311 evenly distributed along the axial direction of the valve core 300, the high-pressure fluid can flow more evenly around the valve core 300, thereby avoiding the problem of eccentric jamming during the movement of the valve core 300.
  • the pressure relief valve also includes a compression spring 600, which is installed in the buffer chamber 800.
  • One end of the compression spring 600 is connected to the guide sleeve 200, and the other end is connected to the valve core 300.
  • the compression spring 600 has a tendency to push the valve core 300 to move toward the direction close to the valve port 112.
  • valve core 300 presses against the valve port 112 under the elastic force of the compression spring 600, so that the valve port 112 is in a closed state.
  • the valve core 300 is pushed upward to open the valve port 112 by overcoming the elastic force of the compression spring 600 .
  • the pressure relief valve also includes an adjusting block 700, and one end of the guide sleeve 200 away from the valve port 112 is connected to the adjusting block 700, and the outer wall of the adjusting block 700 is threadedly matched with the inner wall of the valve cavity 111, so that the adjusting block 700 can drive the guide sleeve 200 to be movably installed in the valve cavity 111 along the axial direction of the valve cavity 111.
  • the adjustment block 700 drives the guide sleeve 200 to move downward, and the guide sleeve 200 cooperates with the valve core 300 to increase the compression of the compression spring 600. In this way, a greater pressure is required at the valve port 112 to push the valve core 300 to move upward to open the valve port 112.
  • the adjustment block 700 drives the guide sleeve 200 to move upward, and the guide sleeve 200 cooperates with the valve core 300 to reduce the compression of the compression spring 600. In this way, the valve port 112 can be opened when the pressure at the valve port 112 is small.
  • the pressure required for opening the valve can be adjusted by adjusting the installation position of the adjustment block 700 .
  • the valve body assembly 100 includes a valve tube 120 and a valve seat 110 installed in the valve tube 120.
  • the outer wall of the valve seat 110 is provided with a clamping groove 113.
  • the valve tube 120 is provided with a clamping protrusion 121 corresponding to the clamping groove 113.
  • the clamping protrusion 121 is inserted into the clamping groove 113 along the radial direction of the valve cavity 111, so that the valve seat 110 and the valve tube 120 are clamped and matched.
  • the valve port 112 is provided at one end of the valve seat 110, and the other end of the valve seat 110 is provided with an adjustment groove 720.
  • the adjustment block 700 is threadedly connected to the inner wall of the adjustment groove 720.
  • the adjustment block 700 is provided with a mounting through hole 710, and the end of the guide sleeve 200 is riveted to the mounting through hole 710.
  • the adjustment block 700 and the guide sleeve 200 can also be connected in other ways, such as clamping, threading, etc.
  • the adjusting block 700 may also be configured to be non-adjustable. As shown in FIGS. 6 and 7 , the adjusting block 700 is configured to be in the shape of a baffle plate, and the adjusting block 700 is clamped in the valve cavity. The inner wall of 111.
  • the valve core 300 includes a sleeve 310, a sealing head 320 and a sealing member 330.
  • the sleeve 310 and the sealing head 320 are integrally formed and arranged.
  • the sleeve 310 is sleeved on the outer periphery of the guide sleeve 200.
  • the sealing head 320 can be inserted into or separated from the valve port 112 to close or open the valve port 112.
  • the sealing member 330 is sleeved at the connection between the sleeve 310 and the sealing head 320.
  • the cross-sectional area of the valve port 112 gradually decreases, so that when the sealing head 320 is inserted into the valve port 112, the inner wall of the valve port 112 can squeeze the sealing member 330 along the radial direction of the valve cavity 111.
  • the outer diameter of the sleeve 310 is greater than the outer diameter of the sealing head 320, so that a stop step 340 is formed at the connection point of one end of the sleeve 310 close to the sealing head.
  • sealing member 330 is made of a material that is easily elastically deformed, such as rubber.
  • the inner wall of the valve port 112 squeezes the sealing member 330 along the radial direction of the valve cavity 111, so that the valve port 112 and the valve core 300 are more tightly sealed to avoid internal leakage.
  • the cross-sectional area of the valve port 112 gradually decreases along the direction from the sleeve 310 to the sealing head 320, as the sealing head 320 gradually extends into the valve port 112, the squeezing effect of the inner wall of the valve cavity 111 on the sealing member 330 gradually increases.
  • the stop step 340 stops at the outer periphery of the valve port 112 along the axial direction of the valve cavity 111, which can avoid the problem that the sealing head 320 is excessively extended into the valve port 112, resulting in excessive squeezing of the sealing member 330 and reduced service life.
  • the sealing form between the valve core 300 and the valve port 112 is also in other situations.
  • an annular protrusion 360 is provided at the valve port 112, and a groove 350 is provided at one end of the valve core 300 facing the valve port 112.
  • the sealing member 330 is fixed in the groove 350.
  • a spherical plug 370 is provided at the end of the valve core 300 close to the valve port 112 .
  • the spherical plug 370 forms a line seal with the valve port 112 to improve the sealing accuracy of the valve port 112 .
  • the present application also provides an air conditioning system, which includes the pressure relief valve described in any one of the above embodiments.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)

Abstract

公开了一种泄压阀及空调系统。泄压阀包括阀体组件(100)、阀芯(300)和导向套(200)，阀体组件(100)设有阀腔(111)和连通阀腔(111)的阀口(112)，阀芯(300)可活动地设于阀腔(111)；导向套(200)设于阀腔(111)，阀芯(300)和导向套(200)中的一者活动套设于另一者，以使阀芯(300)远离阀口(112)的一端与导向套(200)靠近阀口(112)的一端配合形成缓冲腔(800)，阀芯(300)的侧壁和导向套(200)侧壁间隙配合形成第一流道(400)，第一流道(400)连通阀腔(111)和缓冲腔(800)，第一流道(400)的流通面积小于缓冲腔(800)的流通面积。

Description

泄压阀及空调系统
相关申请
本申请要求2023年5月31日申请的，申请号为202310636600.6，名称为“泄压阀及空调系统”的中国专利申请的优先权，在此将其全文引入作为参考。
技术领域
本申请涉及阀门技术领域，特别是涉及一种泄压阀及空调系统。
背景技术
泄压阀安装于空调系统中。通常情况下，泄压阀的压缩弹簧推动阀芯封堵阀口，以使阀口处于关闭状态，当有高压流体流过阀口时，高压流体推动阀芯克服压缩弹簧的弹力，以推开阀口并打开阀芯。但是，当流经阀口的高压流体压强波动较大时，高压流体冲击阀芯端部，使得阀芯移动时容易发生震颤。
发明内容
根据本申请的各种实施例，提供一种泄压阀及空调系统。
一种泄压阀，泄压阀包括阀体组件、阀芯和导向套。阀体组件设有阀腔和连通阀腔的阀口，阀芯可活动地设于阀腔，以打开或者关闭阀口。导向套设于阀腔，且阀芯和导向套中的一者活动套设于另一者，以使阀芯远离阀口的一端与导向套靠近阀口的一端配合形成缓冲腔，并且，阀芯的侧壁与导向套的侧壁间隙配合形成第一流道，第一流道连通阀腔和缓冲腔，第一流道的流通面积小于缓冲腔的流通面积。
在其中一个实施例中，阀芯用于与导向套配合的侧壁直径为导向套用于与阀芯配合的侧壁的直径为 满足，△d1≤0.01mm。可以理解的是，如此设置，使得流体能够从缓冲腔通过第一流 道缓慢地排入阀腔。
在其中一个实施例中定义阀腔的轴向为第一流道的长度方向，第一流道的长度l1，满足，l1≥10mm。可以理解的是，如此设置，使得流体能够从缓冲腔通过第一流道缓慢地排入阀腔。
在其中一个实施例中，阀芯套设于导向套的外侧，阀芯的外壁与阀腔的内壁间隙配合，并形成第二流道，第二流道的流通面积小于阀口的流通面积。
在其中一个实施例中，第二流道的流通面积s1，阀口的流通面积s2，满足，0.8s2≤s1≤0.9s2。可以理解的是，如此设置，有利于更加稳定地支撑阀芯打开阀口。
在其中一个实施例中，阀芯的外壁设有多个切面，每一个切面均沿着阀芯的轴向贯穿阀芯的两端，并且，多个切面沿着阀芯的轴向均匀分布。可以理解的是，如此设置，便于高压流体从切面与阀腔的内壁之间流过，并且，能够避免阀芯移动过程中发生偏心卡滞的问题。
在其中一个实施例中，泄压阀还包括压缩弹簧，压缩弹簧装设于缓冲腔内，压缩弹簧一端连接导向套，另一端连接阀芯，且压缩弹簧具有推动阀芯朝向靠近阀口的方向移动的趋势。可以理解的是，如此设置，便于通过压缩弹簧推动阀芯关闭阀口。
在其中一个实施例中，泄压阀还包括调节块，导向套远离阀口的一端连接于调节块，调节块的外壁与阀腔的内壁螺纹配合，以使调节块能够带动导向套沿着阀腔的轴向可移动地安装于阀腔内。可以理解的是，如此设置，能够通过调节块的安装位置调节开阀需要的压强。
在其中一个实施例中，阀芯包括套筒、密封头和密封件，套筒套设于导向套的外周，密封头连接于套筒靠近阀口的一端，密封件套设于套筒和密封 头的连接处，密封头能够伸入或者脱离阀口，以关闭或者打开阀口，且当密封头伸入阀口时，阀口的内壁能够沿着阀口的径向挤压密封件。可以理解的是，如此设置，使得阀口关闭时，阀口与阀芯密封更加严密，以避免内漏。
在其中一个实施例中，沿着从套筒到密封头的方向，阀口的横截面积逐渐减小，套筒与密封头的连接处设有止挡台阶，当密封头伸入阀口的预设位置时，止挡台阶沿着阀腔的轴向止挡于阀口的外周。可以理解的是，如此设置，能够避免密封头过度伸入阀口，导致密封件被过度挤压而降低使用寿命的问题。
本申请还提供一种空调系统，该空调系统包括以上任意一个实施例所述的泄压阀。
本申请的一个或多个实施例的细节在下面的附图和描述中提出。本申请的其它特征、目的和优点将从说明书、附图以及权利要求书变得明显。
附图说明
为了更好地描述和说明这里公开的那些发明的实施例和/或示例，可以参考一幅或多幅附图。用于描述附图的附加细节或示例不应当被认为是对所公开的发明、目前描述的实施例和/或示例以及目前理解的这些发明的最佳模式中的任何一者的范围的限制。
图1为本申请提供的一实施例的泄压阀的剖视图。
图2为本申请提供的一实施例的局部剖视图。
图3为图2在B处的放大示意图。
图4为图2在A-A处的剖视图。
图5为本申请提供的一实施例的阀芯的结构示意图。
图6为本申请提供的另一实施例的泄压阀的剖视图。
图7为本申请提供的又一实施例的泄压阀的剖视图。
图8为本申请提供的再一实施例的泄压阀的剖视图。
附图标记：100、阀体组件；110、阀座；111、阀腔；112、阀口；113、卡接槽；120、阀管；121、卡接凸起；200、导向套；300、阀芯；310、套筒；311、切面；320、密封头；330、密封件；340、止挡台阶；350、卡槽；360、环状凸起；370、球状堵头；400、第一流道；500、第二流道；600、压缩弹簧；700、调节块；710、安装通孔；720、调节槽；800、缓冲腔。
具体实施方式
为使本申请的上述目的、特征和优点能够更加明显易懂，下面结合附图对本申请的具体实施方式做详细的说明。在下面的描述中阐述了很多具体细节以便于充分理解本申请。但是本申请能够以很多不同于在此描述的其它方式来实施，本领域技术人员可以在不违背本申请内涵的情况下做类似改进，因此本申请不受下面公开的具体实施例的限制。
需要说明的是，当组件被称为“固定于”或“设置于”另一个组件，它可以直接在另一个组件上或者也可以存在居中的组件。当一个组件被认为是“连接”另一个组件，它可以是直接连接到另一个组件或者可能同时存在居中组件。本申请的说明书所使用的术语“垂直的”、“水平的”、“上”、“下”、“左”、“右”以及类似的表述只是为了说明的目的，并不表示是唯一的实施方式。
此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本申请的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本申请中，除非另有明确的规定和限定，第一特征在第二特征“上”、“下” 可以是第一特征直接和第二特征接触，或第一特征和第二特征间接地通过中间媒介接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅表示第一特征水平高度小于第二特征。
除非另有定义，本申请的说明书所使用的所有的技术和科学术语与属于本申请的技术领域的技术人员通常理解的含义相同。在本申请的说明书中所使用的术语只是为了描述具体的实施方式的目的，不是旨在于限制本申请。本申请的说明书所使用的术语“及/或”包括一个或多个相关的所列项目的任意的和所有的组合。
请参阅图1-图2，为了解决当流经阀口的高压流体压强波动较大时，高压流体冲击阀芯端部，使得阀芯移动时容易发生震颤的问题，本申请提供一种泄压阀及空调系统。具体地，泄压阀包括阀体组件100、阀芯300和导向套200，阀体组件100设有阀腔111和连通阀腔111的阀口112，阀芯300可活动地设于阀腔111，以打开或者关闭阀口112。导向套200设于阀腔111，且阀芯300和导向套200中的一者活动套设于另一者，以使阀芯300远离阀口112的一端与导向套200靠近阀口112的一端配合形成缓冲腔800，并且，阀芯300和导向套200中的一者或者两者设有第一流道400，第一流道400连通阀腔111和缓冲腔800，并且，第一流道400的流通面积小于缓冲腔800的流通面积。
具体地，第一流道400的设置形式有两种，如图1和图2所示，当阀芯300套设于导向套200的外侧时，阀芯300的内壁与导向套200的外壁间隙配合形成第一流道400。或者，也可以是当导向套200套设于阀芯300的外侧时， 阀芯300的外壁与导向套200的内壁间隙配合形成第一流道400。
由于阀芯300和导向套200中的一者活动套设于另一者，以使阀芯300远离阀口112的一端与导向套200靠近阀口112的一端配合形成缓冲腔800，因此，当高压流体流经阀口112并冲击到阀芯300的端部时，高压流体推动阀芯300上移，并压缩缓冲腔800。并且，第一流道400连通阀腔111和缓冲腔800，因此，缓冲腔800内的流体会通过第一流道400排出缓冲腔800，又因为第一流道400的流通面积小于缓冲腔800的流通面积，如此，导致缓冲腔800内的流体不能及时通过第一流道400排到阀腔111中，此时，缓冲腔800能够对阀芯300产生一定的阻力，从而消耗高压流体的冲击动能，也即，缓冲腔800能够产生缓冲的效果，能够减小阀芯300动作过程中因阀芯300朝向阀口112一端的压力波动巨大造成阀芯300的频繁往复运动导致的震颤，从而提高阀芯300的动作稳定性，以及降低开阀时的噪声。
在一实施例中，如图2和图3所示，阀芯300用于与导向套200配合的侧壁直径为导向套200用于与阀芯300配合的侧壁的直径为 满足，△d1≤0.01mm，并且，定义阀腔111的轴向为第一流道400的长度方向，第一流道400的长度l1，满足，l1≥10mm。
如此，使得第一流道400流通面积较小且流通长度较长，也即，从而使得流体在第一流道400内沿程阻力大小合适，进而有利于流体从缓冲腔800通过第一流道400缓慢地排入阀腔111，也即，使得缓冲腔800具有合适的泄压能力。以避免缓冲腔800泄压过快，导缓冲腔800滤震效果不佳。也能避免缓冲腔800泄压过慢，并导致缓冲腔800对阀芯300产生较大的阻力，使得阀口112打开困难。
在一实施例中，如图1和图4所示，阀芯300套设于导向套200的外侧， 阀芯300的外壁与阀腔111的内壁间隙配合，并形成第二流道500，第二流道500的流通面积小于阀口112的流通面积。
第二流道500能够对高压流体进行节流，从而使得阀芯300靠近阀口112的一侧与阀芯300背离阀口112的一侧维持大小合适的压强差，以推动阀芯300朝向靠近导向套200的方向移动，并压缩缓冲腔800内的流体。如此设置，能够避免第二流道500的泄压能力过强，使得阀芯300靠近阀口112的一侧与阀芯300背离阀口112的一侧压强差不足以支撑阀芯，并进一步产生阀芯300移动不稳，甚至回落堵住阀口112的问题。
具体地，第二流道500的流通面积s1，阀口112的流通面积s2，满足，0.8s2≤s1≤0.9s2。例如，可以设置s1＝0.8s2、s1＝0.85s2或者s1＝0.9s2等，以使高压流体能更稳定地支撑阀芯300打开阀口112。具体可根据实际情况确定，在此不一一列举。
更近一步地，在一实施例中，如图5所示，阀芯300的外壁设有多个切面311，每一个上述切面311沿着阀芯300的轴向贯穿阀芯300的两端，并且，多个切面311沿着阀芯300的周均匀分布。
如此，便于高压流体从切面311与阀腔111内壁之间流过，并且，通过设置多个切面311沿着阀芯300的轴向均匀分布，能够使高压流体更加均匀地从阀芯300四周流过，进而避免阀芯300移动过程中发生偏心卡滞的问题。
在一实施例中，如图1所示，泄压阀还包括压缩弹簧600，压缩弹簧600装设于缓冲腔800内，压缩弹簧600一端连接导向套200，另一端连接阀芯300，且压缩弹簧600具有推动阀芯300朝向靠近阀口112的方向移动的趋势。
当阀口112处压强较小时，阀芯300在压缩弹簧600的弹力作用下抵住阀口112，使阀口112处于关闭状态。当阀口112处压强较大时，高压流体需 要克服压缩弹簧600的弹力推动阀芯300上移，以打开阀口112。
在一实施例中，如图1和图2所示，泄压阀还包括调节块700，导向套200远离阀口112的一端连接于调节块700，调节块700的外壁与阀腔111的内壁螺纹配合，以使调节块700能够带动导向套200沿着阀腔111的轴向可移动地安装于阀腔111内。
当调节块700的安装位置沿着阀腔111的轴向朝向靠近阀口112的方向移动时，调节块700带动导向套200下移，并使得导向套200与阀芯300配合增大压缩弹簧600的压缩量，如此，则需要阀口112处产生更大压强以推动阀芯300上移打开阀口112。当调节块700的安装位置沿着阀腔111的轴向朝向远离阀口112的方向移动时，调节块700带动导向套200上移，并使得导向套200与阀芯300配合减小压缩弹簧600的压缩量，如此，阀口112处压强较小即能打开阀口112。
也即，通过设置调节块700，使得能够通过调节块700的安装位置调节开阀需要的压强。
具体地，如图1和图2所示，阀体组件100包括阀管120和安装于阀管120内的阀座110，阀座110外壁设有卡接槽113，阀管120对应卡接槽113设有卡接凸起121，卡接凸起121沿着阀腔111的径向插置于卡接槽113内，使得阀座110与阀管120卡接配合。阀口112设于阀座110的一端，阀座110的另一端设有调节槽720，调节块700螺纹连接于调节槽720的内壁，调节块700设有安装通孔710，导向套200的端部铆接于安装通孔710处。当然，调节块700与导向套200也可以采用其他连接方式，比如卡接，螺纹连接等。
但不限于此，在其他实施例中，调节块700也可以设置成不可调节的形式，如图6-图7所示，调节块700设置成挡板状，且调节块700卡接在阀腔 111的内壁。
在一实施例中，如图1和图6所示，阀芯300包括套筒310、密封头320和密封件330，套筒310与密封头320一体成型设置，套筒310套设于导向套200的外周，密封头320能够伸入或者脱离阀口112，以关闭或者打开阀口112。密封件330套设于套筒310与密封头320的连接处，沿着从套筒310到密封头320的方向，阀口112的横截面积逐渐减小，以使当密封头320伸入阀口112时，阀口112的内壁能够沿着阀腔111的径向挤压密封件330。并且，套筒310的外径大于密封头320的外径，以使套筒310靠近所述密封头的一端连接处形成止挡台阶340，当密封头320伸入阀口112的预设位置时，止挡台阶340能够沿着阀腔111的轴向止挡于阀口112的外周。
需要注意的是，密封件330由易发生弹性形变的材料制成，如橡胶。
当密封头320伸入阀口112时，阀口112的内壁沿着阀腔111的径向挤压密封件330，从而使得阀口112与阀芯300密封更加严密，以避免内漏情况发生。又由于沿着从套筒310到密封头320的方向阀口112的横截面积逐渐减小，因此，随着密封头320逐渐伸入阀口112，阀腔111内壁对密封件330的挤压作用逐渐增大，而通过设置止挡台阶340，当密封头320伸入阀口112的预设位置时，止挡台阶340沿着阀腔111的轴向止挡于阀口112的外周，能够避免密封头320过度伸入阀口112，导致密封件330被过度挤压并降低使用寿命的问题。阀芯300与阀口112的密封形式也是其他情形，在一实施例中，如图7所示，在阀口112处设置环状凸起360，阀芯300朝向阀口112一端设置卡槽350，密封件330固定在卡槽350内，当阀芯300移动至靠近阀口112处时，环状凸起360挤压密封件330使密封件330发生弹性形变，以实现对阀口112的密封。
在另一实施例中，如图8所示，阀芯300靠近阀口112的端部设有球状堵头370，当阀芯300移动至靠近阀口112处时，球状堵头370与阀口112形成线密封，以提高对阀口112的密封精度。
泄压阀的装配过程如下：
首先，将导向套200插入调节块700的安装通孔710，通过铆接设备完成铆接；其次，将阀芯300放入阀座110内，并将压缩弹簧600放入阀芯300的内腔；然后，将带有导向套200的调节块700螺纹连接于阀座110，使阀芯300与导向套200套设形成缓冲腔800；最后，将阀座110放入阀管120中，并通过缩颈工艺使阀管120向卡接槽113内挤压变形形成卡接凸起121，完成阀座110与阀管120的装配。
本申请还提供一种空调系统，该空调系统包括以上任意一个实施例所述的泄压阀。
以上所述实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请的专利保护范围应以所附权利要求为准。

Claims (11)

  1. 一种泄压阀，其特征在于，包括阀体组件、阀芯和导向套，所述阀体组件设有阀腔和连通所述阀腔的阀口，所述阀芯可活动地设于所述阀腔，以打开或者关闭所述阀口；
    所述导向套设于所述阀腔，且所述阀芯和所述导向套中的一者活动套设于另一者，以使所述阀芯远离所述阀口的一端与所述导向套靠近所述阀口的一端配合形成缓冲腔，并且，所述阀芯的侧壁和所述导向套侧壁间隙配合形成第一流道，所述第一流道连通所述阀腔和所述缓冲腔，所述第一流道的流通面积小于所述缓冲腔的流通面积。
  2. 根据权利要求1所述的泄压阀，其中，所述阀芯用于与所述导向套配合的侧壁直径定义为φD1，所述导向套用于与所述阀芯配合的侧壁直径定义为φD2，φD1和φD2满足，△d1＝|φD1-φD2|/2，且△d1≤0.01mm。
  3. 根据权利要求1所述的泄压阀，其中，定义所述阀腔的轴向为第一流道的长度方向，所述第一流道的长度定义为l1，l1满足，l1≥10mm。
  4. 根据权利要求1所述的泄压阀，其中，所述阀芯套设于所述导向套的外侧，所述阀芯的外壁与所述阀腔的内壁间隙配合，并形成第二流道，所述第二流道的流通面积小于所述阀口的流通面积。
  5. 根据权利要求4所述的泄压阀，其中，所述第二流道的流通面积s1，所述阀口的流通面积定义为s2，s1和s2满足，0.8s2≤s1≤0.9s2。
  6. 根据权利要求4所述的泄压阀，其中，所述阀芯的外壁设有多个切面，每一个所述切面均沿着所述阀芯的轴向贯穿所述阀芯的两端，并且，多个所述切面沿着所述阀芯的周向均匀分布。
  7. 根据权利要求1所述的泄压阀，其中，还包括压缩弹簧，所述压缩弹簧装设于所述缓冲腔内，所述压缩弹簧一端连接所述导向套，另一端连接所述阀芯，且所述压缩弹簧具有推动所述阀芯朝向靠近所述阀口的方向移动的趋 势。
  8. 根据权利要求7所述的泄压阀，其中，还包括调节块，所述导向套远离所述阀口的一端连接于所述调节块，所述调节块的外壁与所述阀腔的内壁螺纹配合，以使所述调节块能够带动所述导向套沿着所述阀腔的轴向可移动地安装于所述阀腔内。
  9. 根据权利要求1所述的泄压阀，其特征在于，所述阀芯包括套筒、密封头和密封件，所述套筒套设于所述导向套的外周，所述密封头连接于所述套筒靠近所述阀口的一端，所述密封件套设于所述套筒和所述密封头的连接处，所述密封头能够伸入或者脱离所述阀口，以关闭或者打开所述阀口，且当所述密封头伸入所述阀口时，所述阀口的内壁能够沿着所述阀口的径向挤压所述密封件。
  10. 根据权利要求9所述的泄压阀，其中，沿着从所述套筒到所述密封头的方向，所述阀口的横截面积逐渐减小，所述套筒与所述密封头的连接处设有止挡台阶，当所述密封头伸入所述阀口的预设位置时，所述止挡台阶沿着所述阀腔的轴向止挡于所述阀口的外周。
  11. 一种空调系统，其特征在于包括如权利要求1-权利要求9任意一项所述的泄压阀。
PCT/CN2024/084341 2023-05-31 2024-03-28 泄压阀及空调系统 Ceased WO2024244655A1 (zh)

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CN206268523U (zh) * 2016-12-16 2017-06-20 浙江汇润电气有限公司 一种输送泵及其泄压阀
CN111649160A (zh) * 2020-06-28 2020-09-11 南昌矿山机械有限公司 防冲击磨损式液控单向阀
CN113803314A (zh) * 2021-09-10 2021-12-17 浙江华益精密机械有限公司 直动式减泄压阀
CN114659300A (zh) * 2020-12-23 2022-06-24 浙江三花智能控制股份有限公司 一种节流阀
CN220134706U (zh) * 2023-05-31 2023-12-05 盾安环境技术有限公司 泄压阀及空调系统

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* Cited by examiner, † Cited by third party
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US5341838A (en) * 1993-08-23 1994-08-30 Powell Walter W Direct spring pressure operated valve
CN203730858U (zh) * 2014-02-18 2014-07-23 永一阀门集团有限公司 安全溢流阀
CN206268523U (zh) * 2016-12-16 2017-06-20 浙江汇润电气有限公司 一种输送泵及其泄压阀
CN111649160A (zh) * 2020-06-28 2020-09-11 南昌矿山机械有限公司 防冲击磨损式液控单向阀
CN114659300A (zh) * 2020-12-23 2022-06-24 浙江三花智能控制股份有限公司 一种节流阀
CN113803314A (zh) * 2021-09-10 2021-12-17 浙江华益精密机械有限公司 直动式减泄压阀
CN220134706U (zh) * 2023-05-31 2023-12-05 盾安环境技术有限公司 泄压阀及空调系统

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