WO2022068046A1 - 先导式电比例高压溢流阀 - Google Patents

先导式电比例高压溢流阀 Download PDF

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Publication number
WO2022068046A1
WO2022068046A1 PCT/CN2020/134210 CN2020134210W WO2022068046A1 WO 2022068046 A1 WO2022068046 A1 WO 2022068046A1 CN 2020134210 W CN2020134210 W CN 2020134210W WO 2022068046 A1 WO2022068046 A1 WO 2022068046A1
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WO
WIPO (PCT)
Prior art keywords
pilot
sleeve
valve core
main valve
accommodating cavity
Prior art date
Application number
PCT/CN2020/134210
Other languages
English (en)
French (fr)
Inventor
吴绍泽
任健
董兆胜
Original Assignee
潍柴动力股份有限公司
林德液压（中国）有限公司
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 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 EP20956063.0A priority Critical patent/EP4224045A1/en
Publication of WO2022068046A1 publication Critical patent/WO2022068046A1/zh

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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
    • 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
    • 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
    • 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
    • F16K11/065—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 linearly sliding closure members
    • 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
    • F16K31/0603—Multiple-way valves
    • F16K31/0624—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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/01—Damping of valve members
    • F16K47/011—Damping of valve members by means of a dashpot
    • F16K47/0111—Damping of valve members by means of a dashpot the valve members comprising a plunger sliding within a fixed dashpot

Definitions

  • the present application relates to the technical field of hydraulic valves, for example, to a pilot-operated electric proportional high-pressure relief valve.
  • the electric proportional relief valve is a hydraulic valve that adjusts the inlet pressure by controlling the displacement of the spool through a proportional electromagnet (a force and current conversion element whose output force and input current have a linear relationship).
  • the present application provides a pilot-operated electro-proportional high-pressure relief valve, which can handle the situation that the electric-proportional relief valve cannot achieve high pressure and precise control.
  • An embodiment provides a pilot-operated electric proportional high-pressure relief valve, including:
  • a main valve, a pilot valve and a proportional electromagnet assembly are connected in sequence, the main valve includes a main valve sleeve and a main valve core sleeved in the main valve sleeve, the first end of the main valve sleeve has a main valve sleeve formed by the main valve sleeve. an oil inlet selectively blocked by the valve core, and an overflow port is provided on the side of the main valve sleeve;
  • the pilot valve comprises a first transition sleeve, a pilot valve core and a pilot screw plug, the first transition sleeve is sealingly mounted on the second end of the main valve, and the first transition sleeve has a stepped countersunk hole,
  • the pilot valve core and the pilot screw plug are sequentially installed in the counterbore hole, the counterbore hole has a first accommodating cavity and a second accommodating cavity that communicate with each other, and the first end of the pilot valve core can be Abutting against the stepped ring edge of the countersunk hole and separating the first accommodating cavity and the second accommodating cavity, the second end of the pilot valve core is sealed and inserted into the installation groove of the pilot screw plug Inside, the second end of the pilot valve core and the inner wall of the installation groove are surrounded to form a third accommodating cavity;
  • the first end of the first transition sleeve is provided with a first damping hole communicating with the oil inlet and the first accommodating cavity
  • the pilot valve core is provided with a first damping hole communicating with the first accommodating cavity and the first accommodating cavity.
  • the second damping hole of the three accommodating chambers, the side wall of the first transition sleeve is provided with an oil drain hole that communicates with the second accommodating chamber and the oil tank, and the hydraulic oil in the first accommodating chamber has an effect on the leakage of the pilot valve core.
  • the first axial action area of the first end is larger than the second axial action area of the hydraulic oil in the third accommodating cavity to the second end of the pilot valve core;
  • the proportional electromagnet assembly includes an electromagnetic coil and a moving iron arranged in the electromagnetic coil, the first end of the moving iron is in contact with the end of the second end of the pilot valve core, and the electromagnetic coil is opposite to the The moving iron generates electromagnetic force to press the pilot valve core against the stepped ring edge.
  • FIG. 1 is a schematic structural diagram of a pilot-operated electric proportional high-pressure relief valve provided by an embodiment of the present application
  • FIG. 2 is an enlarged view of a pilot valve core of a pilot-operated electro-proportional high-pressure relief valve provided in an embodiment of the present application.
  • Main valve 11. Main valve sleeve; 111. Oil inlet; 112. Overflow port; 12. Main spool; 121. Third damping hole; 2. Pilot valve; 21. First transition sleeve; 211, The first damping hole; 212, the oil drain hole; 213, the stepped ring edge; 22, the pilot valve core; 221, the second damping hole; 222, the conical sealing surface; 23, the pilot screw plug; Large diameter groove section; 2312, small diameter groove section; 3, proportional electromagnet assembly; 31, electromagnetic coil; 32, moving iron; 321, guide rod part; 322, sliding part; 33, second transition sleeve; 34, shell ;35, guide sleeve; 36, electromagnet plug; 37, buffer sheet; 38, control plug; 4, first return spring; 5, second return spring; 6, first sealing ring; 7, first retaining ring ; 8. The second sealing ring; 9. The second retaining ring; 10. The third sealing ring;
  • a 1 the first axial action area
  • a 2 the second axial action area
  • a 3 the third axial action area
  • a 4 the fourth axial action area.
  • connection should be understood in a broad sense, for example, it may be a fixed connection, a detachable connection, or an integrated ; 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 connection of two elements or the interaction relationship between the two elements.
  • connection may be a fixed connection, a detachable connection, or an integrated ; 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 connection of two elements or the interaction relationship between the two elements.
  • a first feature "on” or “under” a second feature may include direct contact between the first and second features, or may include the first and second features Not directly but through additional features 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.
  • an embodiment of the present application provides a pilot type electric proportional high pressure relief valve, which can be used for pressure maintenance and back pressure of a hydraulic system to ensure the safety of the hydraulic system.
  • the pilot-operated electro-proportional high-pressure relief valve includes a main valve 1, a pilot valve 2 and a proportional solenoid assembly 3 that are sealed and connected in sequence.
  • the main valve 1 includes a main valve sleeve 11 and a main valve core 12 sleeved in the main valve sleeve 11.
  • the first end of the main valve sleeve 11 has an oil inlet 111
  • the side surface of the main valve sleeve 11 has an overflow port 112 .
  • the pilot valve 2 is sealingly mounted on the second end of the main valve sleeve 11.
  • the pilot valve 2 includes a first transition sleeve 21, a pilot valve core 22 and a pilot screw plug 23.
  • the first transition sleeve 21 has a stepped countersunk hole.
  • the pilot valve The core 22 and the pilot plug 23 are sequentially installed in the countersunk hole, the first end of the pilot valve core 22 abuts against the stepped ring edge 213 of the countersunk hole and divides the countersunk hole into the first accommodating cavity 100 and the second accommodating cavity In the cavity 200, the second end of the pilot valve core 22 is sealed and inserted into the installation groove 231 of the pilot plug 23, the diameter of the second end of the pilot valve core 22 is smaller than the diameter of the installation groove 231, and the second end of the pilot valve core 22 is the same as the diameter of the installation groove 231.
  • a third accommodating cavity 300 is formed around the inner wall of the installation groove 231 .
  • the main valve core 12 is provided with a third damping hole 121
  • the first transition sleeve 21 is provided with a first damping hole 211
  • the pilot valve core 22 is provided with a second damping hole 221
  • the third damping hole 121, the first damping hole 211 and the second damping hole 221 connect the oil inlet 111 , the first accommodating cavity 100 and the third accommodating cavity 300 in sequence.
  • the first axial action area A1 of the hydraulic oil in the first accommodating chamber 100 to the first end of the pilot spool 22 is greater than the second axial action area A1 of the hydraulic oil in the third accommodating chamber 300 to the second end of the pilot spool 22 A 2 .
  • the proportional electromagnet assembly 3 includes an electromagnetic coil 31 and a moving iron 32 arranged in the electromagnetic coil 31 .
  • the first end of the moving iron 32 is in contact with the end of the second end of the pilot valve core 22 , and the electromagnetic coil 31 is energized to apply power to the moving iron 32 .
  • Electromagnetic force the moving iron 32 is forced to press the pilot valve core 22 on the stepped ring edge 213 .
  • the force on the first end of the pilot valve core 22 is less than or equal to the force on the second end, and the first end of the pilot valve core 22 is in close contact with the stepped ring edge 213 superior.
  • the force on the first end of the pilot spool 22 is greater than the force on the second end of the pilot spool 22, and the pilot spool 22 moves to the right (moves to the right in FIG. 2, and moves upward in FIG. 1).
  • the first accommodating chamber 100 communicates with the second accommodating chamber 200, the hydraulic oil is unloaded from the oil drain hole 212 that communicates with the second accommodating chamber 200, and the main spool 12 moves to the right under the action of the oil inlet pressure, so that the overflow port 112 opens , to achieve overflow.
  • F m is the pressure of the moving iron 32 on the second end of the pilot spool 22
  • P is the pressure of the main valve, that is, the pressure of the hydraulic oil at the oil inlet 111
  • a 1 and A 2 are the first end of the pilot spool 22 and A 2 respectively The acting area of the hydraulic oil on the second end.
  • the specific structure of the main valve 1 is shown in Figure 1.
  • the oil inlet 111 of the main valve 1 is generally bypassed on the main oil inlet pipeline of the hydraulic system.
  • the main valve core 12 is opposite to the main valve.
  • the sleeve 11 moves to the right, so that the oil inlet 111 of the main valve 1 communicates with the overflow port 112 to realize the overflow and pressure relief.
  • the main valve core 12 is slidably installed in the main valve sleeve 11 , the inner wall of the main valve sleeve 11 is provided with a main sealing ring at one end close to the oil inlet 111 , and the front end of the main valve core 12 has an inclined main sealing surface.
  • the main sealing surface abuts on the edge of the main sealing ring, and when it overflows, the main sealing surface is separated from the edge of the main sealing ring, and the oil inlet 111 and the overflow port 112 communicate with each other.
  • An annular groove is provided on the outer wall of the main valve sleeve 11 , and a first sealing ring 6 and a first retaining ring 7 are sequentially sleeved in the annular groove.
  • the first sealing ring 6 and the first retaining ring 7 are arranged to realize the main valve sleeve 11 Sealed connection on valve seat or other fixed structure.
  • the main valve sleeve 11 has a structure whose diameter gradually expands from one side of the oil inlet 111 to the other side.
  • the inner diameter of the main valve sleeve 11 near the oil inlet 111 is smaller than the inner diameter of the main valve sleeve 11 away from the oil inlet 111 , that is, the inner diameter of the first end of the main valve sleeve 11 is smaller than the inner diameter of the second end of the main valve sleeve 11 .
  • a first transition sleeve 21 is provided on the sealing sleeve at the second end of the main valve sleeve 11, an annular groove is formed on the outer wall of the first transition sleeve 21, and a second sealing ring 8 and a second retaining ring are sleeved in the above annular groove in sequence.
  • the second sealing ring 8 and the second retaining ring 9 are arranged to achieve sealing and fixing between the main valve sleeve 11 and the first transition sleeve 21 .
  • the main valve core 12 and the first transition sleeve 21 are arranged at intervals in the main valve sleeve 11, and the second end of the main valve core 12, the first end of the first transition sleeve 21 and the inner wall of the main valve sleeve 11 are enclosed to form a fourth accommodation.
  • the third damping hole 121 provided in the main spool 12 connects the oil inlet 111 and the fourth accommodating cavity 400, so that both ends of the main spool 12 are subject to the force of hydraulic oil and slide stably.
  • a first return spring 4 is installed between the main valve core 12 and the first transition sleeve 21 , and the first return spring 4 is configured to apply a spring force to the second end of the main valve core 12 to ensure the sealing effect of the main valve core 12 At the same time, the first return spring 4 is set to realize the reset of the main spool 12 after overflow.
  • the third axial action area A 3 of the hydraulic oil at the oil inlet 111 to the first end of the main spool 12 is less than or equal to the third axial action area A 3 of the hydraulic oil in the fourth accommodating cavity 400 to the main spool 12 .
  • the fourth axial acting area A 4 at the two ends enables the two ends of the main spool 12 to maintain a pressure difference to achieve sealing.
  • the force on both ends of the main spool 12 is as follows:
  • Fr is the force of the first return spring 4 on the second end of the main spool 12
  • P is the pressure of the main valve
  • a 3 and A 4 are the pressure areas of the first and second ends of the main spool 12 , respectively.
  • the specific structure of the pilot valve 2 is shown in FIG. 2 , the first transition sleeve 21 of the pilot valve 2 is provided with a stepped counterbore hole inside, and the pilot valve core 22 abuts on the stepped ring edge 213 of the counterbore hole to sink the counterbore.
  • the head hole is divided into a first accommodating cavity 100 and a second accommodating cavity 200 , and a first damping hole 211 provided in the first transition sleeve 21 communicates the first accommodating cavity 100 and the fourth accommodating cavity 400 .
  • the side part of the first transition sleeve 21 is provided with an oil drain hole 212 penetrating through it, an oil drain port is provided on the main valve sleeve 11 at a position corresponding to the oil drain hole 212 , and the first end of the oil drain hole 212 is connected to the second accommodating cavity. 200 is connected, and the second end of the oil drain hole 212 is connected to the oil tank through the oil drain port.
  • the pilot valve core 22 is separated from the stepped ring edge 213 , the first accommodating cavity 100 is communicated with the second accommodating cavity 200 , and the hydraulic oil flows back into the oil tank through the oil drain hole 212 and the oil drain port.
  • the outer wall of the first transition sleeve 21 located outside the main valve sleeve 11 is provided with an annular groove, and a third sealing ring 10 is installed in the annular groove.
  • the third sealing ring is arranged to realize the connection between the first transition sleeve 21 and the valve seat or other fixed structures. seal between.
  • the first end of the pilot valve core 22 has a conical sealing surface 222, and the conical sealing surface 222 is arranged to abut against the stepped ring edge 213 to ensure the sealing effect.
  • the sealing structure of the pilot valve core 22 and the first transition sleeve 21 may also adopt other forms.
  • the first end of the pilot valve core 22 may also be set to be spherical, and the sealing is performed by the spherical sealing surface, or the first
  • the stepped ring edge 213 of a transition sleeve 21 can also be configured as a conical surface, so as to expand the sealing contact area and achieve better sealing effect.
  • the structure that can achieve effective sealing between the pilot valve core 22 and the first transition sleeve 21 falls within the scope of protection of the present application, which is not limited herein.
  • the second end of the pilot valve core 22 is inserted into the installation groove 231 in the pilot plug 23 .
  • the second end of the pilot valve core 22 has a stepped column structure, which includes a large diameter shaft section and a small diameter shaft section.
  • the installation groove 231 in the pilot plug 23 is a through stepped groove, and the stepped groove includes a large diameter groove section 2311 and a small diameter groove.
  • Section 2312, the large diameter shaft section is sealed and slidably installed in the large diameter groove section 2311, the small diameter shaft section is sealed and slidably installed in the small diameter groove section 2312 and penetrates the small diameter groove section 2312, and the end of the small diameter groove section 2312 abuts the moving iron 32.
  • One end of the small-diameter shaft section extends into the large-diameter groove section 2311, and the diameter of the small-diameter shaft section is smaller than the inner diameter of the large-diameter groove section 2311, and a third accommodating cavity 300 is formed between the small-diameter shaft section and the large-diameter groove section 2311,
  • a second damping hole 221 is provided inside the pilot valve core 22 , and the second damping hole 221 communicates the first accommodating cavity 100 with the third accommodating cavity 300 .
  • the first axial action area A1 of the hydraulic oil in the first accommodating cavity 100 to the pilot spool 22 and the second axial action area A of the hydraulic oil in the third accommodating cavity 300 to the pilot spool 22 The size relationship of 2 is generally set as 1.05 ⁇ A 1 :A 2 ⁇ 1.3.
  • the specific size relationship between A 1 and A 2 can be determined according to the pressure holding requirement of the hydraulic system and the model of the proportional electromagnet 3 , which is not set in this embodiment of the present application.
  • the outer wall of the pilot screw plug 23 is provided with an external thread, and the inner wall of the second end of the counterbore hole is provided with an inner thread, and the pilot screw plug 23 is fixed in the countersunk head hole through the thread.
  • the proportional solenoid assembly 3 is installed on the second end of the pilot valve 2 , and is configured to exert a force on the pilot valve core 2 , so that the pilot valve core 2 abuts against the stepped ring edge 213 .
  • the proportional electromagnet assembly 3 also includes a second transition sleeve 33 , a housing 34 and a guide sleeve 35 .
  • the second transition sleeve 33 is configured to connect the pilot valve 2 and other components of the proportional electromagnet assembly 3.
  • the second transition sleeve 33 includes a first installation section, a second installation section and a third installation section. The first installation section is sleeved over the first installation section.
  • the shell 34 is sleeved outside the second installation section, the guide sleeve 35 is sleeved outside the third installation section, the electromagnetic coil 31 is arranged between the shell 34 and the guide sleeve 35, and the moving iron 32 slides Set in the guide sleeve 35 .
  • a cylindrical moving iron installation space is formed inside the guide sleeve 35 , and the moving iron 32 is slid in the moving iron installation space by the electromagnetic force of the electromagnetic coil 31 .
  • the moving iron 32 includes a guide rod portion 321 at the first end and a sliding portion 322 at the second end.
  • the outer diameter of the guide rod portion 321 is smaller than the outer diameter of the sliding portion 322 .
  • the guide rod portion 321 is provided to be in contact with the pilot valve body 22 , and the sliding portion 322 is provided to receive force and slide in the movable iron installation space.
  • a through hole is provided in the second transition sleeve 33, and the guide rod portion 321 passes through the through hole and abuts against the second end of the pilot valve body 22. As shown in FIG.
  • a buffer sheet 37 is provided between the second transition sleeve 33 and the sliding portion 322, the buffer sheet 37 is sleeved on the guide rod portion 321 and bonded with the second transition sleeve 33, and the buffer sheet 37 is made of soft materials such as It is made of rubber material and is arranged to prevent frictional interference between the second transition sleeve 33 and the sliding part 322 .
  • the proportional electromagnet assembly 3 further includes an electromagnet plug 36 , and the electromagnet plug 36 is arranged to limit the moving stroke of the moving iron 32 .
  • the electromagnet plug 36 is installed on the second end of the casing 34 , and a threaded hole is opened at the second end of the casing 34 , and the electromagnet plug 36 is installed in the casing 34 through a thread.
  • the electromagnet screw plug 36 and the sliding part 322 of the moving iron 32 are arranged at intervals, and a second return spring 5 is arranged between the electromagnet screw plug 36 and the sliding part 322, and the second return spring 5 is arranged to realize the movement of the moving iron 32. reset, so that the pilot spool 22 is reset in time.
  • the proportional electromagnet assembly 3 further includes a control plug 38, the control plug 38 is inserted into the housing 34, the control plug 38 is electrically connected to the electromagnetic coil 31, and is configured to supply power to the electromagnetic coil 31, so that the electromagnetic coil 31 generates an electromagnetic field to respond to the electromagnetic coil 31.
  • the moving iron 32 generates electromagnetic force.
  • the electromagnetic coil 31 in this embodiment is a proportional electromagnetic coil 31 , and the electromagnetic force generated on the moving iron 32 is linearly related to the supply current. Due to the structural design of the different force-bearing areas at both ends of the pilot valve core 22 in this embodiment, the electromagnetic coil 31 can adjust the larger overflow pressure with a small electromagnetic force, so that a smaller electromagnetic coil 31 can be used. And the moving iron 32, reduce the volume of the proportional electromagnet assembly 3 and the entire relief valve.
  • the main valve pressure P acts on the first end of the main valve core 12 and flows into the fourth accommodating chamber 400 , the first accommodating chamber 100 and the third accommodating chamber 400 through the third orifice 121 , the first orifice 211 and the second orifice 221 in sequence in the accommodating cavity 300 .
  • the opening condition of the pilot spool 22 is not satisfied, that is, the force on the first end of the pilot spool 22 is less than the force on the second end of the pilot spool 22, and the hydraulic oil in the multiple accommodating chambers is static at this time, the pilot spool 22 is in a closed state, and at the same time The first end of the main spool 12 is in contact with the edge of the main sealing ring, and the main spool 12 is in a closed state, which is the pressure-holding state of the pilot-operated electro-proportional high-pressure relief valve.
  • the oil pressure will be transmitted to the corresponding accommodating chamber through a plurality of damping holes.
  • the force on the first end of the pilot spool 22 is greater than that on the second end of the pilot spool 22 .
  • the pilot spool 22 of the pilot type electro-proportional high pressure relief valve provided by the present application has different pressure-receiving areas at both ends.
  • the adjustment of the larger overflow pressure reduces the demand for the output force value and withstand voltage level of the comparative electromagnet, and it is easier to realize the matching design of the proportional electromagnet, reducing the design difficulty and cost; for the same proportional electromagnet, the control current can be reduced. size and power consumption; according to different main valve pressure and output force of proportional electromagnet assembly 3, according to different working conditions, the size relationship between the pressure areas at both ends of the pilot spool 22 can be specifically set, so that the pressure on the main valve can be realized. precise control.

Abstract

一种先导式电比例高压溢流阀，包括：依次连接的主阀（1）、先导阀（2）和比例电磁铁组件（3），主阀（1）具有进油口（111）和溢流口（112）；先导阀（2）包括第一过渡套（21）和套装在第一过渡套（21）内的先导阀芯（22）和先导螺堵（23），先导阀芯（22）抵接于第一过渡阀套（21）内的阶梯环边（213）上并与第一过渡套（21）围设形成第一容纳腔（100）和第二容纳腔（200），先导阀芯（22）和先导螺堵（23）围设形成第三容纳腔（300），第一容纳腔（100）内液压油的对先导阀芯（22）的第一轴向作用面积（A 1）大于第三容纳腔（300）内液压油对先导阀芯（22）的第二轴向作用面积（A 2）；比例电磁铁组件（3）设置为对先导阀芯（22）产生推力以使先导阀芯（22）抵接于阶梯环边（213）。

Description

先导式电比例高压溢流阀
本申请要求申请日为2020年9月30日、申请号为202011062690.5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
本申请涉及液压阀技术领域，例如涉及一种先导式电比例高压溢流阀。
背景技术
电比例溢流阀是通过比例电磁铁(一种力和电流转换元件，其输出力和输入电流呈线性关系)控制阀芯的位移，以实现调节入口压力的液压阀。
相关技术中，电比例溢流阀较多，但是多为直动式，即通过比例电磁铁直接控制主阀芯的位移以控制溢流压力。对于少部分先导式电比例溢流阀，由于其受先导阀芯结构限制，对比例电磁铁输出力要求较大，因此常规输出力值较小的电磁铁无法满足要求，这为先导式电比例溢流阀的高压化和控制精确化的实现带来了较大困难。
发明内容
本申请提供了一种先导式电比例高压溢流阀，能够处理电比例溢流阀存在的无法实现高压和精确控制的情况。
一实施例提供一种先导式电比例高压溢流阀，包括：
依次连接的主阀、先导阀和比例电磁铁组件，所述主阀包括主阀套和套装在所述主阀套内的主阀芯，所述主阀套的第一端具有由所述主阀芯选择性封堵的进油口，所述主阀套的侧面具有溢流口；
所述先导阀包括第一过渡套、先导阀芯和先导螺堵，所述第一过渡套密封安装于所述主阀的第二端，所述第一过渡套具有阶梯状的沉头孔，所述先导阀芯和所述先导螺堵依次安装于所述沉头孔内，所述沉头孔具有相互连通的第一容纳腔和第二容纳腔，所述先导阀芯的第一端能够抵接于所述沉头孔的阶梯环边并将所述第一容纳腔和所述第二容纳腔分隔，所述先导阀芯的第二端密封插接于所述先导螺堵的安装槽内，所述先导阀芯的第二端与所述安装槽的内壁围设形成第三容纳腔；
所述第一过渡套的第一端设置有连通所述进油口和所述第一容纳腔的第一阻尼孔，所述先导阀芯内设置有连通所述第一容纳腔和所述第三容纳腔的第二阻尼孔，所述第一过渡套的侧壁设置有连通所述第二容纳腔和油箱的泄油孔，所述第一容纳腔内液压油对所述先导阀芯的第一端的第一轴向作用面积大于所述第三容纳腔内液压油对所述先导阀芯的第二端的第二轴向作用面积；
所述比例电磁铁组件包括电磁线圈和设置于所述电磁线圈内的动铁，所述动铁的第一端抵接于所述先导阀芯的第二端的末端，所述电磁线圈对所述动铁产生电磁力以将所述先导阀芯压紧于所述阶梯环边。
附图说明
图1是本申请实施例提供的先导式电比例高压溢流阀的结构示意图；
图2是本申请实施例提供的先导式电比例高压溢流阀的先导阀芯的放大图。
图中标示如下：
1、主阀；11、主阀套；111、进油口；112、溢流口；12、主阀芯；121、第三阻尼孔；2、先导阀；21、第一过渡套；211、第一阻尼孔；212、泄油孔；213、阶梯环边；22、先导阀芯；221、第二阻尼孔；222、锥形密封面；23、先导螺堵；231、安装槽；2311、大径槽段；2312、小径槽段；3、比例电磁铁组件；31、电磁线圈；32、动铁；321、导杆部；322、滑动部；33、第二过渡套；34、壳体；35、导套；36、电磁铁螺堵；37、缓冲片；38、控制插头；4、第一复位弹簧；5、第二复位弹簧；6、第一密封圈；7、第一挡圈；8、第二密封圈；9、第二挡圈；10、第三密封圈；
100、第一容纳腔；200、第二容纳腔；300、第三容纳腔；400、第四容纳腔；
A 1、第一轴向作用面积；A 2、第二轴向作用面积；A 3、第三轴向作用面积；A 4、第四轴向作用面积。
具体实施方式
在本申请的描述中，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，可以根据具体情况理解上述术语在本申请中的具体含义。
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”、“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和图2所示，本申请实施例提供一种先导式电比例高压溢流阀，可用于液压系统的保压及背压，以保证液压系统的安全。该先导式电比例高压溢流阀包括依次密封连接的主阀1、先导阀2和比例电磁铁组件3，主阀1包括主阀套11和套装在主阀套11内的主阀芯12，主阀套11的第一端具有进油口111，主阀套11的侧面具有溢流口112。
先导阀2密封安装于主阀套11的第二端，先导阀2包括第一过渡套21、先导阀芯22和先导螺堵23，第一过渡套21具有阶梯状的沉头孔，先导阀芯22和先导螺堵23依次安装于沉头孔内，先导阀芯22的第一端抵接于沉头孔的阶梯环边213并将沉头孔分隔成第一容纳腔100和第二容纳腔200，先导阀芯22的第二端密封插接于先导螺堵23的安装槽231内，先导阀芯22的第二端的直径小于安装槽231的直径，先导阀芯22的第二端与安装槽231的内壁围设形成第三容纳腔300。
主阀芯12内设置有第三阻尼孔121，第一过渡套21内设置有第一阻尼孔211，先导阀芯22内设置有第二阻尼孔221，第三阻尼孔121、第一阻尼孔211和第二阻尼孔221将进油口111、第一容纳腔100和第三容纳腔300依次连通起来。第一容纳腔100内液压油对先导阀芯22的第一端的第一轴向作用面积A 1大于第三容纳腔300内液压油对先导阀芯22的第二端的第二轴向作用面积A 2。
比例电磁铁组件3包括电磁线圈31和设置于电磁线圈31内的动铁32，动铁32的第一端抵接于先导阀芯22的第二端的末端，电磁线圈31通电对动铁32 施加电磁力，动铁32受力将先导阀芯22压紧于阶梯环边213上。
在本实施例中，在正常保压状态时，先导阀芯22的第一端的受力小于或等于其第二端的受力，先导阀芯22的第一端紧密抵接于阶梯环边213上。在溢流状态时，先导阀芯22的第一端的受力大于其第二端的受力，先导阀芯22向右移动(图2中为向右移动，图1中为向上移动)，第一容纳腔100和第二容纳腔200连通，液压油从连通第二容纳腔200的泄油孔212中卸载，主阀芯12在进油压力的作用下向右移动，使得溢流口112打开，实现溢流。
先导阀芯22要实现开启所应满足的条件如下：
P(A 1-A 2)＞F m
其中，F m为动铁32对先导阀芯22第二端的压力，P为主阀压强，即进油口111处液压油的压强，A 1和A 2分别为先导阀芯22第一端和第二端所受液压油的作用面积。
由上式可知，通过改变A 1和A 2的差值，可使得在P较大时，较小的F m也能满足溢流控制要求，可以降低对比例电磁铁组件3输出力的要求，扩大调压范围。根据不同的主阀压强P和比例电磁铁组件3的输出力F m，通过灵活调节A 1和A 2的大小关系，可以实现对主阀压力的精确控制。
主阀1的具体结构如图1所示，主阀1的进油口111一般旁接于液压系统的主进油管路上，当主进油管路内压力超过限定压力时，主阀芯12相对主阀套11向右移动，使主阀1的进油口111和溢流口112连通，实现溢流泄压。主阀芯12滑动安装于主阀套11中，主阀套11的内壁靠近进油口111的一端设置有主密封环边，主阀芯12的前端具有倾斜的主密封面。在正常保压时，主密封面抵接于主密封环边上，当溢流时，主密封面与主密封环边分离，进油口111和溢流口112连通。在主阀套11的外壁上设置有环形槽，环形槽内依次套设有第一密封圈6和第一挡圈7，第一密封圈6和第一挡圈7设置为实现主阀套11在阀座或其他固定结构上的密封连接。
主阀套11呈从进油口111的一侧向另一侧直径逐渐扩大的结构，主阀套11靠近进油口111一侧的内径小于主阀套11远离进油口111一侧的内径，即主阀套11第一端的内径小于主阀套11第二端的内径。在主阀套11的第二端密封套设有第一过渡套21，第一过渡套21的外壁设置有环形槽，在上述环形槽中依次套设有第二密封圈8和第二挡圈9，第二密封圈8和第二挡圈9设置为实现主阀套11和第一过渡套21之间的密封固定。
主阀芯12和第一过渡套21在主阀套11内间隔设置，主阀芯12的第二端、第一过渡套21的第一端和主阀套11的内壁围设形成第四容纳腔400，主阀芯12内设置的第三阻尼孔121将进油口111和第四容纳腔400连通起来，使得主阀芯12的两端均受液压油的作用力，滑动稳定。在主阀芯12和第一过渡套21之间安装有第一复位弹簧4，第一复位弹簧4设置为对主阀芯12的第二端施加弹簧力，以保证主阀芯12的密封作用，同时第一复位弹簧4设置为实现溢流后主阀芯12的复位。
示例性地，本实施例中进油口111处液压油对主阀芯12第一端的第三轴向作用面积A 3小于或等于第四容纳腔400内液压油对主阀芯12的第二端的第四轴向作用面积A 4，以使主阀芯12的两端维持压力差，以实现密封。在正常保压时，主阀芯12的两端的受力情况如下式：
PA 3<PA 4+F r
式中F r为第一复位弹簧4对主阀芯12第二端的作用力，P为主阀压强，A 3和A 4分别为主阀芯12的第一端和第二端的受压面积。
在溢流阀溢流时，第四容纳腔400内的压力油经先导阀2泄流，主阀芯12的第二端所受液压力为零，此时主阀芯12的受力情况如下式：
PA 3>F r
从该式可知，主阀芯12第一端受力大于第二端受力，主阀芯12朝向第二端移动，进油口111和溢流口112连通，实现溢流。
先导阀2的具体结构如图2所示，先导阀2的第一过渡套21的内部设置有阶梯状的沉头孔，先导阀芯22抵接于沉头孔的阶梯环边213上将沉头孔分隔成第一容纳腔100和第二容纳腔200，第一过渡套21内设置的第一阻尼孔211将第一容纳腔100和第四容纳腔400连通。第一过渡套21的侧部设置有贯穿的泄油孔212，主阀套11上与泄油孔212相对应的位置设置有泄油口，泄油孔212的第一端与第二容纳腔200连通，泄油孔212的第二端通过泄油口连通于油箱。在溢流时，先导阀芯22与阶梯环边213分离，第一容纳腔100与第二容纳腔200连通，液压油通过泄油孔212与泄油口回流入油箱。
第一过渡套21位于主阀套11外部的外壁设置有环形槽，在环形槽内安装有第三密封圈10，第三密封圈设置为实现第一过渡套21与阀座或其他固定结构之间的密封。
本实施例中先导阀芯22的第一端具有锥形密封面222，锥形密封面222设 置为与阶梯环边213抵接，以保证密封效果。在其他实施例中，先导阀芯22与第一过渡套21的密封结构还可以采用其他的形式，如先导阀芯22的第一端还可以设置成球形，通过球形密封面进行密封，或者第一过渡套21的阶梯环边213还可以设置成锥形面，以扩大密封接触面积，实现更好的密封效果。能够实现先导阀芯22与第一过渡套21有效密封的结构均落在本申请的保护范围内，本申请在此不做限定。
先导阀芯22的第二端插接于先导螺堵23内的安装槽231中。先导阀芯22的第二端呈阶梯柱状结构，其包括大径轴段和小径轴段，先导螺堵23内的安装槽231为贯通的阶梯槽，阶梯槽包括大径槽段2311和小径槽段2312，大径轴段密封滑动安装于大径槽段2311内，小径轴段密封滑动安装于小径槽段2312内并贯穿小径槽段2312，小径槽段2312的末端抵接有动铁32。小径轴段的一端伸入到大径槽段2311内，且小径轴段的直径小于大径槽段2311的内径，小径轴段与大径槽段2311之间围设形成第三容纳腔300，在先导阀芯22的内部设置有第二阻尼孔221，第二阻尼孔221将第一容纳腔100与第三容纳腔300连通。
在本实施例中，第一容纳腔100内液压油对先导阀芯22的第一轴向作用面积A 1与第三容纳腔300内液压油对先导阀芯22的第二轴向作用面积A 2的大小关系一般设定为1.05<A 1:A 2<1.3。A 1和A 2的具体大小关系可根据液压系统的保压要求及比例电磁铁3的型号进行确定，本申请实施例在此不做设定。
在本申请实施例中，先导螺堵23的外壁设置有外螺纹，在沉头孔第二端的内壁设置有内螺纹，先导螺堵23通过螺纹固定于沉头孔内。
比例电磁铁组件3安装于先导阀2的第二端，且设置为对先导阀芯2施加作用力，使先导阀芯2抵接于阶梯环边213。比例电磁铁组件3除包括电磁线圈31和动铁32外，还包括第二过渡套33、壳体34和导套35。第二过渡套33设置为连接先导阀2和比例电磁铁组件3的其他部件，第二过渡套33包括第一安装段、第二安装段和第三安装段，第一安装段套装于第一过渡套21的第二端内，壳体34套装于第二安装段外，导套35套装于第三安装段外，电磁线圈31设置在壳体34和导套35之间，动铁32滑动套装在导套35内。
导套35内部形成筒状的动铁安装空间，动铁32受到电磁线圈31的电磁力在动铁安装空间内滑动。动铁32包括第一端的导杆部321和第二端的滑动部322，导杆部321的外径小于滑动部322的外径。导杆部321设置为与先导阀芯22抵接，滑动部322设置为受力并在动铁安装空间内滑动。在第二过渡套33内设置 有贯通的通孔，导杆部321穿过上述通孔并与先导阀芯22的第二端抵接。可选地，在第二过渡套33和滑动部322之间设置有缓冲片37，缓冲片37套装于导杆部321上并与第二过渡套33粘接，缓冲片37由软质材料如橡胶材料制成，且设置为防止第二过渡套33与滑动部322之间产生摩擦干涉。
比例电磁铁组件3还包括电磁铁螺堵36，电磁铁螺堵36设置为限制动铁32的移动行程。电磁铁螺堵36安装于壳体34的第二端，在壳体34的第二端开设有螺纹孔，电磁铁螺堵36通过螺纹安装于壳体34内。电磁铁螺堵36和动铁32的滑动部322间隔设置，在电磁铁螺堵36和滑动部322之间设置有第二复位弹簧5，第二复位弹簧5设置为实现动铁32移动后的复位，以使先导阀芯22及时复位。
比例电磁铁组件3还包括控制插头38，控制插头38插装于壳体34上，控制插头38与电磁线圈31电连接，且设置为为电磁线圈31供电，以使电磁线圈31产生电磁场以对动铁32产生电磁力。本实施例中的电磁线圈31为比例电磁线圈31，其对动铁32产生的电磁力与供电电流呈线性关系。由于本实施例中先导阀芯22两端受力面积不同的结构设计，使得电磁线圈31以较小的电磁力就能实现对较大溢流压力的调节，从而可以采用更小的电磁线圈31和动铁32，减小比例电磁铁组件3及整个溢流阀的体积。
本申请实施例提供的先导式电比例高压溢流阀的装配过程如下：
对于液压结构部分的装配：将第二密封圈8和第二挡圈9套入第一过渡套21外壁的环形槽内，将第一密封圈6、第一挡圈7以及第三密封圈10依次装入主阀套11外壁相应的环形槽内；将主阀芯12、第一复位弹簧4、第一过渡套21依次装入主阀套11内，将主阀套11装入外部的阀座或其他机构上；将先导阀芯22和先导螺堵23依次装入第一过渡套21的沉头孔中，并拧紧先导螺堵23。至此液压结构部分装配完成。
比例电磁铁组件部分的装配：将缓冲片37粘接于第二过渡套33的第二端，将动铁32插接于第二过渡套33内的通孔内；将导套35、电磁线圈31和壳体34从内向外依次套装于第二过渡套33的第三安装段；将第二复位弹簧5装入导套35内的动铁安装空间内，将电磁铁螺堵36装入壳体34的第二端，并拧紧电磁铁螺堵36，使第二复位弹簧5的两端分别与动铁32和电磁铁螺堵36抵接；将控制插头38插接于壳体34的相应插槽内。至此，比例电磁铁组件3装配完成。
本申请实施例提供的先导式电比例高压溢流阀的工作过程如下：
主阀压强P作用于主阀芯12的第一端并通过第三阻尼孔121、第一阻尼孔211和第二阻尼孔221依次流入到第四容纳腔400、第一容纳腔100和第三容纳腔300内。若先导阀芯22的开启条件未满足，即先导阀芯22第一端的受力小于其第二端的受力，此时多个容纳腔内液压油静止，先导阀芯22呈关闭状态，同时主阀芯12的第一端抵接于主密封环边，主阀芯12呈关闭状态，此时为该先导式电比例高压溢流阀的保压状态。
若主阀压强P高于设定油压，油压通过多个阻尼孔传递至对应的容纳腔，此时先导阀芯22的第一端受力大于其第二端受力，先导阀芯22满足开启条件，第一容纳腔100和第二容纳腔200连通，进油口111处的液压油依次流经第三阻尼孔121、第四容纳腔400、第一阻尼孔211、第一容纳腔100、第二容纳腔200和泄油孔212回流至油箱。由于液压油液的流动，主阀芯12第一端和第二端产生压力差，主阀芯12开启，进油口111与溢流口112连通，超过限定压力的液压油通过溢流口112溢流。
主阀压强P回归到限定压强以下时，先导阀芯22首先关闭，之后主阀芯12关闭，本实施例提供的先导式电比例高压溢流阀回复到保压状态。
本申请的有益效果为：
本申请提供的先导式电比例高压溢流阀的先导阀芯22的两端的受压面积不同，通过设定其两端受压面积的差值，可以实现以较小的电磁线圈输出力完成对较大溢流压力的调节，降低对比例电磁铁输出力值和耐压等级的需求，且更容易实现比例电磁铁匹配设计，降低设计难度和成本；对于相同的比例电磁铁，可以降低控制电流大小和功率消耗；根据不同的主阀压强和比例电磁铁组件3的输出力，根据不同的工况具体设定先导阀芯22两端的受压面积之间的大小关系，可以实现对主阀压力的精确控制。

Claims (10)

  1. 一种先导式电比例高压溢流阀，包括：
    依次连接的主阀(1)、先导阀(2)和比例电磁铁组件(3)，所述主阀(1)包括主阀套(11)和套装在所述主阀套(11)内的主阀芯(12)，所述主阀套(11)的第一端具有由所述主阀芯(12)选择性封堵的进油口(111)，所述主阀套(11)的侧面具有溢流口(112)；
    所述先导阀(2)包括第一过渡套(21)、先导阀芯(22)和先导螺堵(23)，所述第一过渡套(21)密封安装于所述主阀(1)的第二端，所述第一过渡套(21)具有阶梯状的沉头孔，所述先导阀芯(22)和所述先导螺堵(23)依次安装于所述沉头孔内，所述沉头孔具有相互连通的第一容纳腔(100)和第二容纳腔(200)，所述先导阀芯(22)的第一端能够抵接于所述沉头孔的阶梯环边(213)并将所述第一容纳腔(100)和所述第二容纳腔(200)分隔，所述先导阀芯(22)的第二端密封插接于所述先导螺堵(23)的安装槽(231)内，所述先导阀芯(22)的第二端与所述安装槽(231)的内壁围设形成第三容纳腔(300)；
    所述第一过渡套(21)的第一端设置有连通所述进油口(111)和所述第一容纳腔(100)的第一阻尼孔(211)，所述先导阀芯(22)内设置有连通所述第一容纳腔(100)和所述第三容纳腔(300)的第二阻尼孔(221)，所述第一过渡套(21)的侧壁设置有连通所述第二容纳腔(200)和油箱的泄油孔(212)，所述第一容纳腔(100)内液压油对所述先导阀芯(22)的第一端的第一轴向作用面积(A 1)大于所述第三容纳腔(300)内液压油对所述先导阀芯(22)的第二端的第二轴向作用面积(A 2)；
    所述比例电磁铁组件(3)包括电磁线圈(31)和设置于所述电磁线圈(31)内的动铁(32)，所述动铁(32)的第一端抵接于所述先导阀芯(22)的第二端的末端，所述电磁线圈(31)对所述动铁(32)产生电磁力以将所述先导阀芯(22)压紧于所述阶梯环边(213)。
  2. 根据权利要求1所述的先导式电比例高压溢流阀，其中，所述第一轴向作用面积(A 1)与所述第二轴向作用面积(A 2)的比值大于1.05且小于<1.3。
  3. 根据权利要求1所述的先导式电比例高压溢流阀，其中，所述先导阀芯(22)的第一端具有锥形密封面(222)，所述锥形密封面(222)能够抵接于所述阶梯环边(213)以将所述第一容纳腔(100)和所述第二容纳腔(200)分隔。
  4. 根据权利要求1所述的先导式电比例高压溢流阀，其中，所述安装槽 (231)为阶梯槽，所述阶梯槽包括大径槽段(2311)和小径槽段(2312)，所述先导阀芯(22)的中间部分滑动安装于所述大径槽段(2311)，所述先导阀芯(22)的第二端滑动安装于所述小径槽段(2312)且贯穿所述小径槽段(2312)。
  5. 根据权利要求1所述的先导式电比例高压溢流阀，其中，所述第一过渡套(21)的第一端套装于所述主阀套(11)内，所述主阀套(11)的内壁、所述主阀芯(12)和所述第一过渡套(21)围设形成第四容纳腔(400)，所述第一阻尼孔(211)连通所述第一容纳腔(100)和所述第四容纳腔(400)，所述主阀芯(12)内设置有第三阻尼孔(121)，所述第三阻尼孔(121)连通所述进油口(111)和所述第四容纳腔(400)。
  6. 根据权利要求5所述的先导式电比例高压溢流阀，其中，所述进油口(111)处液压油对所述主阀芯(12)第一端的第三轴向作用面积(A 3)小于或等于所述第四容纳腔(400)内液压油对所述主阀芯(12)第二端的第四轴向作用面积(A 4)。
  7. 根据权利要求5所述的先导式电比例高压溢流阀，其中，所述主阀芯(12)和所述第一过渡套(21)之间安装有第一复位弹簧(4)。
  8. 根据权利要求1所述的先导式电比例高压溢流阀，其中，所述比例电磁铁组件(3)还包括第二过渡套(33)和导套(35)，所述第二过渡套(33)的第一端套装于所述第一过渡套(21)内，所述导套(35)套装于所述第二过渡套(33)的第二端，所述电磁线圈(31)套装于所述导套(35)外，所述动铁(32)套装于所述导套(35)内；
    所述第二过渡套(33)内设置有贯通的通孔，所述动铁(32)的第一端穿设于所述通孔中且与所述先导阀芯(22)的第二端抵接。
  9. 根据权利要求8所述的先导式电比例高压溢流阀，其中，所述比例电磁铁组件(3)还包括电磁铁螺堵(36)，所述电磁铁螺堵(36)设置于所述导套(35)的第二端，所述电磁铁螺堵(36)和所述动铁(32)之间安装有第二复位弹簧(5)。
  10. 根据权利要求8所述的先导式电比例高压溢流阀，其中，所述比例电磁铁组件(3)还包括控制插头(38)，所述控制插头(38)与所述电磁线圈(31)电连接，所述控制插头(38)设置为控制所述电磁线圈(31)的磁场强度。
PCT/CN2020/134210 2020-09-30 2020-12-07 先导式电比例高压溢流阀 WO2022068046A1 (zh)

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