WO2022001032A1 - 负载保持阀及液压控制系统 - Google Patents

负载保持阀及液压控制系统 Download PDF

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Publication number
WO2022001032A1
WO2022001032A1 PCT/CN2020/138889 CN2020138889W WO2022001032A1 WO 2022001032 A1 WO2022001032 A1 WO 2022001032A1 CN 2020138889 W CN2020138889 W CN 2020138889W WO 2022001032 A1 WO2022001032 A1 WO 2022001032A1
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WIPO (PCT)
Prior art keywords
valve core
pilot
oil
core
port
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Application number
PCT/CN2020/138889
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English (en)
French (fr)
Inventor
任健
鲍玉娟
王志
吴绍泽
董兆胜
刘志政
Original Assignee
潍柴动力股份有限公司
林德液压（中国）有限公司
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Publication date
Application filed by 潍柴动力股份有限公司, 林德液压（中国）有限公司 filed Critical 潍柴动力股份有限公司
Priority to EP20943087.5A priority Critical patent/EP4174349A4/en
Publication of WO2022001032A1 publication Critical patent/WO2022001032A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control 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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
    • F16K31/40—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor
    • F16K31/406—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston
    • F16K31/408—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor with electrically-actuated member in the discharge of the motor acting on a piston the discharge being effected through the piston and being blockable by an electrically-actuated member making contact with the piston
    • 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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/42—Actuating devices; Operating means; Releasing devices actuated by fluid by means of electrically-actuated members in the supply or discharge conduits of the fluid motor
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure

Definitions

  • the present application relates to the technical field of hydraulic control, for example, to a load holding valve and a hydraulic control system.
  • the load holding control valve plays an important role. It needs to be able to meet the ability of two-way flow during normal operation, that is, the oil can directly open the valve port to pass through when it is working in the forward direction, and it needs to be opened by the control pressure when it is working in the reverse direction.
  • the valve port allows the oil to pass; the oil circuit is cut off when it stops working, and the pressure maintenance function behind the valve port is realized.
  • the existing design structure basically adopts the split structure design of the pilot stage and the main stage, because each element needs to work together with each other, it is necessary to design the flow passage connecting the different elements in the design process of the valve body, and the valve body structure design is relatively complicated. , the oil passage is also more complicated.
  • the present application provides a load holding valve and a hydraulic control system, which can handle the complex structure of the valve body and the oil passage.
  • One embodiment provides a load holding valve, comprising:
  • the valve body is provided with an oil return port and a working device oil port that can communicate with each other;
  • the main spool is arranged in the valve body, the first end of the main spool can seal the communication channel between the oil return port and the oil port of the working device, and the second end of the main spool is provided with a hollow space.
  • the main valve core is provided with a first orifice that communicates with the oil return port and the cavity, and a second orifice that communicates with the oil port of the working device and the cavity, and the area of the first orifice is larger than the area of the second orifice;
  • a pilot valve core is arranged in the valve body, and the pilot valve core is at least partially located in the cavity, and the first end of the pilot valve core can seal the first throttle hole;
  • An electromagnetic assembly is connected with the second end of the pilot valve core, and the electromagnetic assembly is configured to control the pilot valve core to seal or open the first throttle hole.
  • An embodiment provides a hydraulic control system including the above-described load holding valve.
  • FIG. 1 is a schematic structural diagram of a load holding valve provided by an embodiment of the present application
  • FIG. 2 is a schematic diagram of the load holding valve provided by the embodiment of the present application when it is working in the forward direction;
  • FIG. 3 is a schematic diagram of the load holding valve provided by the embodiment of the present application when the load holding valve works in reverse and the electromagnetic assembly is energized;
  • FIG. 4 is a schematic diagram when the load holding valve according to the embodiment of the present application works in the reverse direction and the electromagnetic assembly is de-energized.
  • valve body 11, oil return port; 12, working device oil port; 20, main spool; 21, cavity; 22, first throttle hole; 23, second throttle hole; 24, first guide hole; 25, second guide hole; 30, pilot valve core; 41, iron core; 411, limit post; 42, armature; 43, spring; 44, electromagnetic coil.
  • connection should be understood in a broad sense, for example, it may be a fixed connection or a detachable connection, or It can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, and it can be the internal communication between the two elements or the interaction relationship between the two elements.
  • connection may be a fixed connection or a detachable connection, or It can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, and it can be the internal communication between the two elements or the interaction relationship between the two elements.
  • the first feature "on” or “under” the second feature may include direct contact between the first and second features, or may include the first and second features.
  • the two features are not in direct contact but through another feature between them.
  • the first feature being “above”, “over” and “above” the second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is level higher than the second feature.
  • the first feature is “below”, “below” and “below” the second feature includes the first feature being directly below and diagonally below the second feature, or simply means that the first feature has a lower level than the second feature.
  • the terms “upper”, “lower”, “left”, “right”, etc. are based on the orientation or positional relationship shown in the drawings, and are only for convenience of description and simplified operation , rather than indicating or implying that the indicated device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the embodiments of the present application.
  • the terms “first” and “second” are only used for distinction in description, and have no special meaning.
  • an embodiment of the present application provides a load holding valve, which includes a valve body 10 , a main valve core 20 , a pilot valve core 30 and a solenoid assembly.
  • the valve body 10 is provided with an oil return port 11 and a working device oil port 12 that can communicate with each other; the main spool 20 is arranged in the valve body 10, and the first end of the main spool 20 can seal the oil return port 11 and the working device oil.
  • the second end of the main spool 20 is provided with a cavity 21, the main spool 20 is provided with a first throttle hole 22 that communicates with the oil return port 11 and the cavity 21, and an oil port that communicates with the working device 12 and the second orifice 23 of the cavity 21, and the area of the first orifice 22 is larger than the area of the second orifice 23;
  • the pilot valve core 30 is arranged in the valve body 10 and at least partially located in the cavity 21 Inside, the first end of the pilot valve core 30 can seal the first throttle hole 22 ;
  • the solenoid assembly is connected with the second end of the pilot valve core 30 , and the solenoid assembly is configured to control the pilot valve core 30 to seal or open the first throttle hole 22 .
  • the structure is simplified, the number of components is reduced, and the arrangement of oil passages between different components is avoided, thereby reducing the processing cost; cavity 21, and the pilot valve core 30 is arranged in the cavity 21 of the main valve core 20, so that the overall structure is more compact.
  • the first throttle hole 22 is opened, and the oil port 12 of the working device communicates with the oil return port 11 through the second throttle hole 23 and the first throttle hole 22 (see the direction indicated by the arrow B in FIG. 3 ).
  • the main spool 20 moves to the right under the action of the pressure difference, so that the oil port 12 of the working device is directly connected to the oil return port 11 (see The direction indicated by arrow C in FIG. 4 ), so that the oil in the oil port 12 of the working device is returned to the oil through the oil return port 11 .
  • the electromagnetic assembly When the load holding valve is static, the electromagnetic assembly is not energized, the pilot spool 30 is in a position to seal the first orifice 22 , and the oil in the oil port 12 of the working device flows into the cavity of the main spool 20 through the second orifice 23 21.
  • the main spool 20 is in the position of sealing the oil return port 11 and the oil port 12 of the working device under the action of the oil, so that the oil in the oil port 12 of the working device cannot return to the oil through the oil return port 11, so that the pressure can be maintained. effect, see Figure 1.
  • the electromagnetic assembly includes an electromagnetic coil 44, an iron core 41, an armature 42 and a spring 43.
  • the iron core 41 is arranged in the electromagnetic coil 44, the armature 42 is slidably arranged in the iron core 41, and the first end of the armature 42 is connected with the pilot valve core 30,
  • the spring 43 is provided between the second end of the armature 42 and the iron core 41 .
  • the generated magnetic field drives the pilot spool 30 to move to the right through the armature 42, and at the same time the armature 42 compresses the spring 43, the pilot spool 30 opens the first throttle hole 22, the oil return port 11 and the main spool 20
  • the electromagnetic coil 41 is de-energized, the magnetic field adsorbing the armature 42 disappears, the armature 42 moves to the left with the pilot spool 30 under the action of the restoring force of the spring 43, and the pilot spool 30 closes the first throttle hole 22.
  • the limit post 411 there is a limit post 411 in the iron core 41 , and when the electromagnetic coil 41 is energized to move the armature 42 to the right, the limit post 411 can limit the stroke of the armature 42 to move to the right.
  • the spring 43 is sleeved on the limiting post 411 , so that the armature 42 is limited and the installation of the spring 43 is also facilitated.
  • the main valve core 20, the first orifice 22 and the pilot valve core 30 are coaxially arranged, so that the structure arrangement is more compact and reasonable.
  • the first end surface of the main valve core 20 is a tapered surface
  • the first end surface of the pilot valve core 30 is also a tapered surface, which improves the sealing performance of the main valve core 20 and the pilot valve core 30 .
  • the main valve core 20 is provided with a first guide hole 24 that communicates with the first throttle hole 22 .
  • the diameter of the first guide hole 24 is larger than the diameter of the first throttle hole 22 , and the first guide hole 24 is arranged in the first section.
  • the flow hole 22 is close to the side of the oil return port 11 .
  • the main valve core 20 is provided with a second guide hole 25 that communicates with the second throttle hole 23.
  • the diameter of the second guide hole 25 is larger than the diameter of the second throttle hole 23.
  • the second guide hole 25 is arranged in the second throttle hole 23.
  • the hole 23 is close to the side of the oil port 12 of the work equipment.
  • the first orifice 22 and the second orifice 23 can not only achieve the purpose of throttling, but also ensure that the oil can flow smoothly.
  • a hydraulic control system includes the load holding valve in the above solution, which simplifies the structure of the hydraulic control system and the arrangement of oil passages.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

公开了一种负载保持阀，包括阀体（10），其上设置有能够相互连通的回油口（11）以及工作装置油口（12）；主阀芯（20），设置在阀体（10）内，主阀芯（20）的第一端能够密封回油口（11）与工作装置油口（12）的连通通道，主阀芯（20）的第二端开设有空腔（21），主阀芯（20）上设置有连通回油口（11）与空腔（21）的第一节流孔（22），以及连通工作装置油口（12）与空腔（21）的第二节流孔（23），且第一节流孔（22）的面积大于第二节流孔（23）的面积；先导阀芯（30），设置在阀体（10）内，且至少部分位于空腔（21）内，先导阀芯（30）的第一端能够密封第一节流孔（22）；电磁组件（41，42，43，44），与先导阀芯（30）的第二端连接，且设置为控制先导阀芯（30）密封或打开第一节流孔（22）。还公开了包括负载保持阀的液压控制系统。

Description

负载保持阀及液压控制系统
本申请要求申请日为2020年6月30日、申请号为202010617548.6的中国专利申请的优先权，该申请的全部内容通过引用结合在本申请中。
技术领域
本申请涉及液压控制技术领域，例如涉及一种负载保持阀及液压控制系统。
背景技术
在工程机械领域，负载保持控制阀具有重要的作用，正常工作时需能满足双向通流的能力，即正向工作时油液能够直接打开阀口通过，而反向工作时需通过控制压力打开阀口使油液通过；停止工作时油路截止，实现阀口后的压力保持功能。现有设计结构基本上先导级和主级都是采用分体式结构设计，因为各个元件需要相互协同工作，需要在阀体的设计过程中设计连通不同元件的流经通道，阀体结构设计相对复杂，油道也较为复杂。
发明内容
本申请提供了一种负载保持阀及液压控制系统，能够处理阀体结构及油道复杂的情况。
一是实施例提供一种负载保持阀，包括：
阀体，其上设置有能够相互连通的回油口以及工作装置油口；
主阀芯，设置在所述阀体内，所述主阀芯的第一端能够密封所述回油口与所述工作装置油口的连通通道，所述主阀芯的第二端开设有空腔，所述主阀芯上设置有连通所述回油口与所述空腔的第一节流孔，以及连通所述工作装置油口与所述空腔的第二节流孔，且所述第一节流孔的面积大于所述第二节流孔的面积；
先导阀芯，设置在所述阀体内，且所述先导阀芯至少部分位于所述空腔内，所述先导阀芯的第一端能够密封所述第一节流孔；
电磁组件，与所述先导阀芯的第二端连接，所述电磁组件设置为控制所述先导阀芯密封或打开所述第一节流孔。
一实施例提供一种液压控制系统，包括上述的负载保持阀。
附图说明
图1是本申请实施例提供的负载保持阀的结构示意图；
图2是本申请实施例提供的负载保持阀正向工作时的示意图；
图3是本申请实施例提供的负载保持阀反向工作且电磁组件得电时的示意图；
图4是本申请实施例提供的负载保持阀反向工作且电磁组件失电时的示意图。
图中：
10、阀体；11、回油口；12、工作装置油口；20、主阀芯；21、空腔；22、第一节流孔；23、第二节流孔；24、第一导向孔；25、第二导向孔；30、先导阀芯；41、铁芯；411、限位柱；42、衔铁；43、弹簧；44、电磁线圈。
具体实施方式
在本申请实施例的描述中，除非另有明确的规定和限定，术语“相连”、“连接”、“固定”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本申请实施例中的具体含义。
在本申请实施例中，除非另有明确的规定和限定，第一特征在第二特征之“上”或之“下”可以包括第一和第二特征直接接触，也可以包括第一和第二特征不是直接接触而是通过它们之间的另外的特征接触。而且，第一特征在第二特征“之上”、“上方”和“上面”包括第一特征在第二特征正上方和斜上方，或仅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”包括第一特征在第二特征正下方和斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本实施例的描述中，术语“上”、“下”、“左”、“右”、等方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述和简化操作，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，因此不能理解为对本申请实施例的限制。此外，术语“第一”、“第二”仅仅用于在描述上加以区分，并没有特殊的含义。
如图1所示，本申请实施例提供一种负载保持阀，包括阀体10、主阀芯20、先导阀芯30以及电磁组件。阀体10上设置有能够相互连通的回油口11以及工作装置油口12；主阀芯20设置在阀体10内，主阀芯20的第一端能够密封回油口11与工作装置油口12的连通通道，主阀芯20的第二端开设有空腔21，主阀芯20上设置有连通回油口11与空腔21的第一节流孔22，以及连通工作装置油口12与空腔21的第二节流孔23，且第一节流孔22的面积大于第二节流孔23的面积；先导阀芯30设置在阀体10内，且至少部分位于空腔21内，先导阀芯30的第一端能够密封第一节流孔22；电磁组件与先导阀芯30的第二端连接，电磁组件设置为控制先导阀芯30密封或打开第一节流孔22。通过将主阀芯20和先导阀芯30集成设置，简化了结构，减少了元件数量并避免了不同元件之间油道的布置，进而降低了加工成本；并且通过在主阀芯20上开设空腔21，并将先导阀芯30设置于主阀芯20的空腔21内，使得整体结构更加紧凑。
参见图2，当负载保持阀正向工作时，回油口11与进油连通，回油口11的高压油直接推动主阀芯20右移打开回油口11与工作装置油口12的连通通道，使得油液进入工作装置油口12后通向工作装置，图2中箭头A所示为油液流动方向。当负载保持阀反向工作时，工作装置在重力作用下使得油液需由工作装置油口12流向回油口11，此时回油口11与回油连通，电磁组件得电，先导阀芯30在电磁组件的作用下打开第一节流孔22，工作装置油口12通过第二节流孔23和第一节流孔22连通回油口11(参见图3中箭头B所指的方向)，由于第一节流孔22的面积大于第二节流孔23的面积，使得主阀芯20在压差的作用下右移，从而工作装置油口12与回油口11直接连通(参见图4中箭头C所指的方向)，从而使得工作装置油口12的油液通过回油口11回油。当负载保持阀静止时，电磁组件不得电，先导阀芯30处于密封第一节流孔22的位置，工作装置油口12的油液通过第二节流孔23流入主阀芯20的空腔21，主阀芯20在油液的作用下处于密封回油口11与工作装置油口12的位置，从而使得工作装置油口12的油液无法通过回油口11回油，达到压力保持的效果，参见图1。
电磁组件包括电磁线圈44、铁芯41、衔铁42和弹簧43，铁芯41设置于电磁线圈44内，衔铁42滑动设置在铁芯41内，衔铁42的第一端与先导阀芯30连接，弹簧43设置在衔铁42的第二端与铁芯41之间。当电磁线圈41得电时，产生的磁场通过衔铁42驱动先导阀芯30右移，同时衔铁42压缩弹簧43，先导阀芯30打开第一节流孔22，回油口11与主阀芯20的空腔21连通；当电磁线 圈41失电时，吸附衔铁42的磁场消失，衔铁42在弹簧43的回复力的作用下带着先导阀芯30左移，先导阀芯30关闭第一节流孔22。可选地，在铁芯41内有限位柱411，当电磁线圈41得电使衔铁42右移时，限位柱411能够限制衔铁42右移的行程。可选地，弹簧43套设于限位柱411上，使得对衔铁42进行限位的同时也能便于弹簧43的安装。
主阀芯20、第一节流孔22以及先导阀芯30同轴设置，使得结构布置更加紧凑合理。
主阀芯20的第一端面为锥面，先导阀芯30的第一端面也为锥面，提高了主阀芯20以及先导阀芯30的密封性能。
主阀芯20上设置有与第一节流孔22相连通的第一导向孔24，第一导向孔24的直径大于第一节流孔22的直径，第一导向孔24设置于第一节流孔22靠近回油口11的一侧。主阀芯20上设置有与第二节流孔23连通的第二导向孔25，第二导向孔25的直径大于第二节流孔23的直径，第二导向孔25设置于第二节流孔23靠近工作装置油口12的一侧。使得第一节流孔22和第二节流孔23既能达到节流的目的，又能保证油液能顺利流过。
一种液压控制系统，包括上述方案中的负载保持阀，简化了液压控制系统的结构以及油道布置。

Claims (10)

  1. 一种负载保持阀，包括：
    阀体(10)，其上设置有能够相互连通的回油口(11)以及工作装置油口(12)；
    主阀芯(20)，设置在所述阀体(10)内，所述主阀芯(20)的第一端能够密封所述回油口(11)与所述工作装置油口(12)的连通通道，所述主阀芯(20)的第二端开设有空腔(21)，所述主阀芯(20)上设置有连通所述回油口(11)与所述空腔(21)的第一节流孔(22)，以及连通所述工作装置油口(12)与所述空腔(21)的第二节流孔(23)，且所述第一节流孔(22)的面积大于所述第二节流孔(23)的面积；
    先导阀芯(30)，设置在所述阀体(10)内，且所述先导阀芯(30)至少部分位于所述空腔(21)内，所述先导阀芯(30)的第一端能够密封所述第一节流孔(22)；
    电磁组件(41,42,43,44)，与所述先导阀芯(30)的第二端连接，所述电磁组件(41,42,43,44)设置为控制所述先导阀芯(30)密封或打开所述第一节流孔(22)。
  2. 根据权利要求1所述的负载保持阀，其中，所述主阀芯(20)的第一端面为锥面。
  3. 根据权利要求1所述的负载保持阀，其中，所述先导阀芯(30)的第一端面为锥面。
  4. 根据权利要求1所述的负载保持阀，其中，所述主阀芯(20)上设置有与所述第一节流孔(22)相连通的第一导向孔(24)，所述第一导向孔(24)的直径大于所述第一节流孔(22)的直径，所述第一导向孔(24)设置于所述第一节流孔(22)靠近所述回油口(11)的一侧。
  5. 根据权利要求1所述的负载保持阀，其中，所述主阀芯(20)上设置有与所述第二节流孔(23)连通的第二导向孔(25)，所述第二导向孔(25)的直径大于所述第二节流孔(23)的直径，所述第二导向孔(25)设置于所述第二节流孔(23)靠近所述工作装置油口(12)的一侧。
  6. 根据权利要求1所述的负载保持阀，其中，所述主阀芯(20)、所述第一节流孔(22)以及所述先导阀芯(30)同轴设置。
  7. 根据权利要求1-6任一项所述的负载保持阀，其中，所述电磁组件(41,42,43,44)包括电磁线圈(44)、铁芯(41)、衔铁(42)和弹簧(43)，所述铁芯(41)设置于所述电磁线圈(44)内，所述衔铁(42)滑动设置在所述铁芯(41)内，所述衔铁(42)的第一端与所述先导阀芯(30)连接，所述弹簧(43)设置在所述衔铁(42)的第二端与所述铁芯(41)之间。
  8. 根据权利要求7所述的负载保持阀，其中，所述铁芯(41)内设置有限 位柱(411)，所述限位柱(411)设置为限制所述衔铁(42)带动所述先导阀芯(30)回退的行程。
  9. 根据权利要求8所述的负载保持阀，其中，所述弹簧(43)套设于所述限位柱(411)。
  10. 一种液压控制系统，包括如权利要求1-9任一项所述的负载保持阀。
PCT/CN2020/138889 2020-06-30 2020-12-24 负载保持阀及液压控制系统 WO2022001032A1 (zh)

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5738142A (en) * 1996-08-09 1998-04-14 Case Corporation Pressure holding directional control valve
CH690191A5 (de) * 1998-07-29 2000-05-31 Beringer Hydraulik Ag Steuerbares hydraulisches Druckbegrenzungsventil.
US7921880B2 (en) * 2007-08-20 2011-04-12 Hydraforce, Inc. Three-way poppet valve with intermediate pilot port
CN204186666U (zh) * 2014-10-15 2015-03-04 浙江华益机械有限公司 一种插装式负载保持阀及液压负载保持控制系统
CN107631064A (zh) * 2017-11-10 2018-01-26 宁波文泽机电技术开发有限公司 可用于低负载的比例单向流量阀
CN111720382A (zh) * 2020-06-30 2020-09-29 潍柴动力股份有限公司 一种负载保持阀及液压控制系统

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3339573A (en) * 1965-03-15 1967-09-05 Weatherhead Co Flow control valve
US4623118A (en) * 1982-08-05 1986-11-18 Deere & Company Proportional control valve
DE4030952C2 (de) * 1990-09-29 1994-01-27 Bosch Gmbh Robert Steuervorrichtung für einen hydraulischen Arbeitszylinder
WO1996012111A1 (de) * 1994-10-15 1996-04-25 Mannesmann Rexroth Gmbh Verfahren zum betreiben eines vorgesteuerten 2/2-wege-sitzventils und vorgesteuertes 2/2-wege-sitzventil zur durchführung des verfahrens
EP0963518A1 (de) * 1997-02-27 1999-12-15 Mannesmann Rexroth AG Vorgesteuertes sperrventil
CN101929482B (zh) * 2010-08-25 2013-04-03 太原理工大学 一种先导流量闭环控制的比例流量阀
CN206280319U (zh) * 2016-11-24 2017-06-27 浙江华益精密机械股份有限公司 无泄漏压力补偿电比例节流阀
CN107725842B (zh) * 2017-11-08 2019-05-28 扬州市苏高阀门控制有限公司 双向控制的比例单向流量阀
CN107631040B (zh) * 2017-11-08 2019-03-15 立信阀门集团有限公司 一种比例流量截止阀
CN107882794A (zh) * 2017-11-10 2018-04-06 宁波文泽机电技术开发有限公司 双向控制电磁比例阀
CN108980129B (zh) * 2018-07-24 2020-04-07 中国航空工业集团公司西安飞行自动控制研究所 一种负载保持控制阀
CN210196504U (zh) * 2019-07-10 2020-03-27 上海欧联流体控制技术有限公司 一种高压电磁水阀
CN110748518B (zh) * 2019-11-05 2021-04-06 山东金利液压科技有限公司 一种挖掘机负载保持阀

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5738142A (en) * 1996-08-09 1998-04-14 Case Corporation Pressure holding directional control valve
CH690191A5 (de) * 1998-07-29 2000-05-31 Beringer Hydraulik Ag Steuerbares hydraulisches Druckbegrenzungsventil.
US7921880B2 (en) * 2007-08-20 2011-04-12 Hydraforce, Inc. Three-way poppet valve with intermediate pilot port
CN204186666U (zh) * 2014-10-15 2015-03-04 浙江华益机械有限公司 一种插装式负载保持阀及液压负载保持控制系统
CN107631064A (zh) * 2017-11-10 2018-01-26 宁波文泽机电技术开发有限公司 可用于低负载的比例单向流量阀
CN111720382A (zh) * 2020-06-30 2020-09-29 潍柴动力股份有限公司 一种负载保持阀及液压控制系统

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP4174349A4

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