CN111608980A - Differential pressure compensation valve with fast and stable main valve opening - Google Patents

Differential pressure compensation valve with fast and stable main valve opening Download PDF

Info

Publication number
CN111608980A
CN111608980A CN202010509316.9A CN202010509316A CN111608980A CN 111608980 A CN111608980 A CN 111608980A CN 202010509316 A CN202010509316 A CN 202010509316A CN 111608980 A CN111608980 A CN 111608980A
Authority
CN
China
Prior art keywords
valve
cavity
pilot valve
main
section
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.)
Withdrawn
Application number
CN202010509316.9A
Other languages
Chinese (zh)
Inventor
杨新超
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to CN202010509316.9A priority Critical patent/CN111608980A/en
Publication of CN111608980A publication Critical patent/CN111608980A/en
Withdrawn legal-status Critical Current

Links

Images

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
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • F16K1/38—Valve members of conical shape
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • 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
    • F16K11/07—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 with cylindrical slides
    • 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
    • F16K17/10—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 with auxiliary valve for fluid operation of the main valve
    • F16K17/105—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 with auxiliary valve for fluid operation of the main valve using choking or throttling means to control the fluid operation of the main valve
    • 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
    • F16K37/00—Special means in or on valves or other cut-off apparatus for indicating or recording operation thereof, or for enabling an alarm to be given

Abstract

The invention provides a differential pressure compensation valve with fast and stable main valve opening, which is used for realizing the compensation of various disturbance factors of the differential pressure compensation valve in a multi-way valve for controlling high flow, and the structural design of a main valve spool is used for fast and stably controlling the front and back pressure of a main valve, reducing pressure fluctuation and reducing noise.

Description

Differential pressure compensation valve with fast and stable main valve opening
Technical Field
The invention relates to the technical field of valves, in particular to a differential pressure compensation valve with a main valve opening degree rapid and stable.
Background
The valve is used as a core component of a hydraulic control system and controls the supply and closing of high-pressure liquid, but the valve is generally of a structure that a valve core opens and closes a control valve port switch to flow liquid, the valve core inevitably causes the fluctuation of liquid pressure in the opening process, and particularly, when the liquid with small flow is controlled, the fluctuation of the pressure caused by the small opening degree of the valve core is more obvious; in addition, when a plurality of valves are in compound action, the flow of the system flows to a low-load actuator, and the problem of poor controllability exists.
In the hydraulic control system of the multi-way valve, the pressure difference compensator is arranged to directly control the pressure difference and the flow rate of the multi-way valve, the control stability of the multi-way valve can be compensated to a certain extent, but the pressure difference compensator is influenced by the spring force and the hydraulic force, and only if the difference between the spring force and the hydraulic force is kept constant, the flow rate of the reversing valve in the flow path control system can be ensured not to be influenced by pressure change.
Disclosure of Invention
Aiming at the defects of the prior art, the invention aims to provide a differential pressure compensation valve with a main valve opening rapid and stable, so as to realize the compensation of various disturbance factors in the differential pressure compensation valve in a large-flow multi-way valve, and by means of the structural design of a valve core of the main valve, the front pressure and the rear pressure of the main valve are rapid and stable, the pressure fluctuation is reduced, and the noise is reduced.
The technical scheme adopted by the invention is as follows: the differential pressure compensation valve with the rapid and stable main valve opening degree is characterized by comprising a differential pressure compensation main valve and a differential pressure compensation pilot valve, wherein the differential pressure compensation main valve comprises a main valve body and a main valve spool, an oil inlet and an oil outlet are arranged on the main valve body, the oil inlet is communicated with an internal main valve cavity through a valve port, the main valve spool is arranged in the main valve cavity, and the oil outlet is communicated with the main valve cavity; the valve port is formed by sequentially connecting a reducing section, a narrow section and an expanding section, a small-aperture opening of the reducing section and a small-aperture opening of the expanding section are respectively communicated with the narrow section, the oil inlet is arranged at a large-aperture opening of the expanding section, the main valve core comprises a main body part, a plugging part, a connecting part, a flow guide part and a curved surface part, the main body part is a cylindrical section, the connecting part is a short cylindrical section with the diameter smaller than that of the main body part, the plugging part is a short conical section which is transited from the main body part to the connecting part, the plugging part is matched with the upper end surface of the reducing section of the valve port to seal the valve port, the flow guide part is a long conical section which is positioned in the valve port and has the diameter gradually reduced from the connecting part to the curved surface part, the curved surface part is connected with the; the rear end face of the main valve spool and the inner surface of the main valve cavity form a main valve control cavity, and a main valve spring is arranged in the main valve control cavity.
The slope of the valve port reducing section is the same as that of the flow guiding part of the main valve core, so that the inflection point phenomenon that the flow increases and suddenly changes from a first linear increasing section to a second linear increasing section along with the increasing speed of the opening degree in the gradual opening process of the main valve core can be eliminated, namely, when the flow guiding part is not arranged on the main valve core or the slope of the flow guiding part is not consistent with that of the valve port reducing section, along with the gradual increase of the opening degree of the main valve core, the flow of the valve port suddenly changes from the first linear increasing section which linearly increases to the second linear increasing section which linearly increases the flow, and under most conditions, the slope of the second linear increasing section is larger than that of the first linear increasing section, the inflection point phenomenon can occur, so that the sudden change of the flow of the main valve can be caused, and the pressure stability can.
The pressure difference compensation pilot valve comprises a pilot valve body and a pilot valve core, wherein the pilot valve body is internally provided with a pilot valve cavity, the pilot valve core is arranged in the pilot valve cavity, the pilot valve core comprises a first column section, a second column section, a third column section and a fourth column section, the first, second and third column sections are connected through a rod body with the diameter smaller than that of any column section, the third column section is connected with the fourth column section or is connected through a connecting body, the connecting body can be a frustum or a rod body, and the diameters of the first, second and fourth column sections are smaller than that of the third column section; the right end face of the fourth column section and the inner surface of the pilot valve cavity form a first control cavity, the right side face of the third column section, the partial peripheral side face of the fourth column section and the inner surface of the pilot valve cavity form a second buffer cavity, the first control cavity and the second buffer cavity are not communicated in the pilot valve cavity, the left side face of the third column section, the right side face of the second column section and the inner surface of the pilot valve cavity form a first buffer cavity, the first buffer cavity and the second buffer cavity are not communicated in the pilot valve cavity, the left side face of the second column section, the right side face of the first column section and the inner surface of the pilot valve cavity form a drain cavity, a pilot valve body at the position corresponding to the drain cavity is provided with a pilot valve oil inlet and a pilot valve oil outlet, the connection and disconnection of the pilot valve oil inlet and the pilot valve oil outlet in the drain cavity can be controlled along with the movement of the pilot valve core, and the, and a pilot valve spring is arranged in the second control cavity, and the pilot valve spring sets the initial state of the pilot valve core to be pressed to the right end so as to disconnect the communication between the pilot valve oil inlet and the pilot valve oil outlet.
The oil inlet of the main valve body is simultaneously communicated with the pilot valve oil inlet and a second buffer cavity through an oil way, a first damping hole is formed in the oil way, the pilot valve oil outlet is communicated with an oil tank, and the second buffer cavity is also simultaneously communicated with the first buffer cavity and the main valve control cavity through a second damping hole; the right end of the differential pressure compensation pilot valve is provided with a proportional electromagnet, the proportional electromagnet is also provided with a first displacement sensor, and the proportional electromagnet is used for detecting the displacement and the speed of the pilot valve core; and a second displacement sensor is arranged at the rear end of the main valve spool and detects the displacement of the main valve spool.
The hydraulic circuit system using the differential pressure compensation valve is characterized by further comprising a main oil circuit, an oil return circuit and a reversing valve, wherein a first oil inlet of the reversing valve is communicated with the main oil circuit, an oil outlet of the reversing valve is communicated with the oil return circuit, a third working oil port of the reversing valve is communicated with an oil inlet of a main valve body and the first control cavity, an oil outlet of the main valve body is communicated with a second oil port of the reversing valve and a load sensitive oil circuit, the load sensitive oil circuit is communicated with the second control cavity, and the first working oil port and the second working oil port of the reversing valve are respectively communicated with two cavities of an actuator.
The invention has the advantages that:
1. the slope of the main valve core flow guiding section of the differential pressure compensation valve is set to be consistent with the slope of the valve port reducing section of the main valve body, so that the phenomenon of flow mutation of the main valve core in the gradual opening process is eliminated, and the stability of the flow and the pressure of the main valve is improved, thereby improving the working stability of the differential pressure compensation valve when the differential pressure of the reversing valve is compensated; the improvement of the valve core structure is applied to the differential pressure compensation valve for the first time, so that the anti-interference performance and the regulation and control stability of the differential pressure compensation valve are enhanced;
2. the pilot valve is provided with two-stage buffer cavities, the pressure stability of the pilot valve is structurally enhanced, and the first damping hole and the second damping hole are arranged in the pipeline, so that the multi-stage buffer effect on the oil pressure in the pipeline is realized, the position of the pilot valve core can be quickly stabilized, the pressure in an oil drainage cavity in the pilot valve is stabilized, the pressure of the main valve control cavity in the main valve is stabilized, and the opening stability of the main valve core is realized;
3. the proportional electromagnet is arranged to regulate and control the displacement of the pilot valve core and the change of the front and rear pressure difference of the pilot valve core in real time, so that the dynamic compensation of disturbance factors is realized, the influence of load pressure change on the valve flow is reduced, and the flow control precision and the control stability of a liquid path system are improved.
Drawings
FIG. 1 is a schematic diagram of the main valve structure of the differential pressure compensating valve of the present invention;
FIG. 2 is a schematic view of a pilot valve structure of the differential pressure compensating valve of the present invention;
FIG. 3 is a schematic view of a differential pressure compensating valve of the present invention;
FIG. 4 is a schematic diagram of the fluid path system of the present invention;
in the figure: 1. the main valve, 2, a pilot valve, 3, a main valve body, 4, a main valve spool, 5, an oil inlet, 6, an oil outlet, 7, a valve port, 8, a main valve spring, 9, a pilot valve body, 10, a pilot valve spool, 11, a pilot valve cavity, 12, a pilot valve oil inlet, 13, a pilot valve oil outlet, 14, a pilot valve spring, 15, a first damping hole, 16, a second damping hole, 17, a first displacement sensor, 18, a second displacement sensor, 19, a main oil way, 20, an oil return way, 21, a reversing valve, 22 and a load sensitive oil way;
4-1, a main body part, 4-2, a plugging part, 4-3, a connecting part, 4-4, a flow guide part, 4-5 and a curved surface part;
7-1, a reducing section, 7-2, a narrow section, 7-3 and an expanding section;
10-1, a first column section, 10-2, a second column section, 10-3, a third column section, 10-4 and a fourth column section;
21-1, a first oil inlet and 21-2 of the reversing valve, an oil outlet and 21-3 of the reversing valve, a third working oil port and 21-4 of the reversing valve, a second oil port and 21-5 of the reversing valve, a first working oil port and 21-6 of the reversing valve and a second working oil port of the reversing valve.
Detailed Description
The invention is described in further detail below with reference to the accompanying examples.
The present invention is described in terms of specific embodiments, and other advantages and benefits of the present invention will become apparent to those skilled in the art from the disclosure herein.
Referring to the drawings, the structures, ratios, sizes, and the like shown in the drawings are only used for matching the disclosure of the present disclosure, so as to be understood and read by those skilled in the art, and are not used to limit the conditions that the present disclosure can be implemented, so that the present disclosure has no technical significance, and any structural modification, ratio relationship change, or size adjustment should still fall within the scope of the disclosure of the present disclosure without affecting the efficacy and the achievable purpose of the present disclosure. Meanwhile, the positional limitation terms used in the present specification are for clarity of description only, and are not intended to limit the scope of the present invention, and changes or modifications of the relative relationship therebetween may be regarded as the scope of the present invention without substantial changes in the technical content.
As shown in fig. 1, which is a schematic diagram of a main valve structure of a differential pressure compensation valve of the present invention, a main valve 1 of the differential pressure compensation valve includes a main valve body 3 and a main valve spool 4, an oil inlet 5 and an oil outlet 6 are disposed on the main valve body 3, the oil inlet 5 is communicated with an internal main valve cavity through a valve port 7, the main valve spool 4 is disposed in the main valve cavity, and the oil outlet 6 is communicated with the main valve cavity; the valve port 7 is formed by sequentially connecting a reduced diameter section 7-1, a narrow diameter section 7-2 and an expanded diameter section 7-3, a small-aperture opening of the reduced diameter section 7-1 and a small-aperture opening of the expanded diameter section 7-3 are respectively communicated with the narrow diameter section 7-2, the oil inlet 5 is arranged at a large-aperture opening of the expanded diameter section 7-3, the main valve core 4 comprises a main body part 4-1, a plugging part 4-2, a connecting part 4-3, a flow guiding part 4-4 and a curved surface part 4-5, the main body part 4-1 is a cylindrical section, the connecting part 4-3 is a short cylindrical section with the diameter smaller than that of the main body part 4-1, the plugging part 4-2 is a short conical section which is transited from the main body part 4-1 to the connecting part 4-3, and the plugging part 4-2 is matched with the upper end face of the reduced diameter section 7-1 to seal the valve, the flow guide part 4-4 is a long conical section which is positioned in the valve port 7 and gradually reduces the diameter from the connecting part 4-3 to the curved surface part 4-5, the curved surface part 4-5 is connected with the flow guide part 4-4, and the curved surface part 4-5 is preferably a partial spherical surface; the rear end face of the main valve spool 4 and the inner surface of the main valve cavity form a main valve control cavity, and a main valve spring 8 is arranged in the main valve control cavity.
Preferably, the main valve spool structure of the present invention is configured such that the slope of the valve port reduced diameter section 7-1 is the same as the slope of the main valve spool guiding portion 4-4, so as to eliminate the inflection phenomenon that the flow rate increases suddenly from the first linear increasing section to the second linear increasing section with the increasing speed of the opening degree when the main valve spool 4 is gradually opened, that is, when the main valve spool is not provided with the guiding portion or the slope of the guiding portion is not consistent with the slope of the valve port reduced diameter section, the valve port flow rate suddenly changes from the first linear increasing section where the flow rate linearly increases to the second linear increasing section where the flow rate linearly increases with the increasing speed of the main valve spool opening degree, and in most cases, the slope of the second linear increasing section is greater than the slope of the first linear increasing section, that is, that the inflection phenomenon occurs, which causes the sudden change of the main valve flow rate, thereby affecting the pressure stability.
Fig. 2 is a schematic view of a pilot valve structure of the differential pressure compensation valve of the present invention, a pilot valve 2 of the differential pressure compensation valve includes a pilot valve body 9 and a pilot valve core 10, a pilot valve cavity 11 is disposed in the pilot valve body, the pilot valve core 10 is disposed in the pilot valve cavity, the pilot valve core 10 includes a first column section 10-1, a second column section 10-2, a third column section 10-3, and a fourth column section 10-4, the first, second, and third column sections are connected by a rod body having a diameter smaller than that of any column section, the third column section 10-3 is connected with the fourth column section 10-4 or connected via a connecting body, the connecting body may be a frustum or a rod body, and the diameters of the first, second, and fourth column sections are smaller than that of the third column section; the right end face of the fourth column section 10-4 and the inner surface of the pilot valve cavity 11 form a first control cavity, the right side face of the third column section 10-3, part of the peripheral side face of the fourth column section 10-4 and the inner surface of the pilot valve cavity 11 form a second buffer cavity, the first control cavity and the second buffer cavity are not communicated in the pilot valve cavity, the left side face of the third column section 10-3, the right side face of the second column section 10-2 and the inner surface of the pilot valve cavity 11 form a first buffer cavity, the first buffer cavity and the second buffer cavity are not communicated in the pilot valve cavity 11, the left side face of the second column section 10-2, the right side face of the first column section 10-1 and the inner surface of the pilot valve cavity 11 form a drain cavity, a pilot valve oil inlet 12 and a pilot valve oil outlet 13 are arranged on the pilot valve body at the position corresponding to the drain cavity, and the on-off of the pilot valve inlet 12 and the pilot valve outlet 13 in the, the left side surface of the first column section 10-1 and the inner surface of the pilot valve cavity 11 form a second control cavity, a pilot valve spring 14 is arranged in the second control cavity, the pilot valve spring 14 sets the initial state of the pilot valve core 10 to be pressed to the right end so as to disconnect the communication between the pilot valve oil inlet 12 and the pilot valve oil outlet 13.
As shown in fig. 3, the structural schematic diagram of the differential pressure compensation valve of the present invention is a schematic diagram, which shows a liquid path connection relationship between a main valve and a pilot valve, wherein an oil inlet 5 of a valve body 3 of the main valve is simultaneously communicated with an oil inlet 12 of the pilot valve and a second buffer chamber through an oil path, a first damping hole 15 is arranged on the oil path, an oil outlet 13 of the pilot valve is communicated with an oil tank, and the second buffer chamber is also simultaneously communicated with the first buffer chamber and the main valve control chamber through a second damping hole 16; the right end of the differential pressure compensation pilot valve is provided with a proportional electromagnet, the proportional electromagnet is also provided with a first displacement sensor 17, and the proportional electromagnet is used for detecting the displacement and the speed of the pilot valve core; the rear end of the main valve spool 4 is provided with a second displacement sensor 18, which detects the displacement of the main valve spool.
FIG. 4 is a schematic structural diagram of a fluid path system of the present invention, the fluid path system using the differential pressure compensation valve further includes a main fluid path 19, a return fluid path 20, and a directional control valve 21, wherein a first oil inlet 21-1 of the directional control valve 21 is communicated with the main fluid path 19, an oil outlet 21-2 of the directional control valve is communicated with the return fluid path 20, a third working fluid port 21-3 of the directional control valve is communicated with an oil inlet 5 of a main valve body and the first control chamber, an oil outlet 6 of the main valve body is communicated with a second oil port 21-4 of the directional control valve and a load sensitive fluid path 22, the load sensitive fluid path 22 is communicated with the second control chamber, and the first working fluid port 21-5 of the directional control valve and the second working fluid port 21-6 of the directional control valve.
The working process of the invention is described below with reference to fig. 1-4 as follows: in the working state, the pressure in the liquid path is supplied by a power source, the pressure in the main oil path 1 is increased, the pressure enters a first control cavity formed by the right end surface of a fourth column section 10-4 of the pilot valve core and the inner surface of a pilot valve cavity 11 through a reversing valve 3, the pressure in the first control cavity is increased, the first control cavity overcomes the spring force of a pilot valve spring 14 on the left side of the pilot valve core to push the pilot valve core 10 to move to the left side, a relief cavity is opened, a pilot valve oil inlet 12 and a pilot valve oil outlet 13 are communicated, meanwhile, the pressure in the main valve control cavity is relieved through a second damping hole 16, the main valve core 4 is in an opening state under the action of the hydraulic pressure overcoming the elasticity of a main valve spring 8, the hydraulic pressure flows to a load sensitive oil path 22 through an oil outlet 6 of the main valve, the pressure in the load sensitive oil path 22, the volumes of the first buffer cavity and the second buffer cavity are changed, and the second damping hole 16 plays a role in buffering in the changing process; meanwhile, under the action of the pilot valve spring 14, the proportional solenoid valve and the pressure of each cavity, the pilot valve core finally reaches a stable state, so that the pressure in the control cavity of the main valve is also stable, and the opening of the valve core of the main valve is kept stable. The valve core of the main valve is fast and stable in opening degree through optimization of the valve core and the valve port structure of the valve port of the main valve and multiple interference compensation effects of the bipolar buffer cavity, the damping hole and the proportional solenoid valve in the pilot valve cavity, and the performance of the differential pressure compensation valve is improved.
Although the embodiments of the present invention have been described with reference to the accompanying drawings, it is not intended to limit the scope of the invention, and it should be understood by those skilled in the art that various modifications and changes in equivalent structure or equivalent flow, or direct or indirect application to other related fields without creative efforts based on the technical solutions of the present invention may be made within the scope of the present invention.

Claims (3)

1. The differential pressure compensation valve with the rapid and stable main valve opening degree is characterized by comprising a differential pressure compensation main valve and a differential pressure compensation pilot valve, wherein the differential pressure compensation main valve comprises a main valve body and a main valve spool, an oil inlet and an oil outlet are arranged on the main valve body, the oil inlet is communicated with an internal main valve cavity through a valve port, the main valve spool is arranged in the main valve cavity, and the oil outlet is communicated with the main valve cavity; the valve port is formed by sequentially connecting a reducing section, a narrow section and a flaring section, a small-aperture opening of the reducing section and a small-aperture opening of the flaring section are respectively communicated with the narrow section, the oil inlet is arranged at a large-aperture opening of the flaring section, the main valve core comprises a main body part, a plugging part, a connecting part, a flow guiding part and a curved surface part, the main body part is a cylindrical section, the connecting part is a short cylindrical section with the diameter smaller than that of the main body part, the plugging part is a short conical section which is transited from the main body part to the connecting part, the plugging part is matched with the upper end surface of the reducing section of the valve port to seal the valve port, the flow guiding part is a long conical section which is positioned in the valve port and has the diameter gradually reduced from the connecting part to the curved surface part; the rear end surface of the main valve core and the inner surface of the main valve cavity also form a main valve control cavity, and a main valve spring is also arranged in the main valve control cavity;
the pressure difference compensation pilot valve comprises a pilot valve body and a pilot valve core, wherein the pilot valve body is internally provided with a pilot valve cavity, the pilot valve core is arranged in the pilot valve cavity, the pilot valve core comprises a first column section, a second column section, a third column section and a fourth column section, the first, second and third column sections are connected through a rod body with the diameter smaller than that of any column section, the third column section is connected with the fourth column section or is connected through a connecting body, the connecting body can be a frustum or a rod body, and the diameters of the first, second and fourth column sections are smaller than that of the third column section; the right end face of the fourth column section and the inner surface of the pilot valve cavity form a first control cavity, the right side face of the third column section, the partial peripheral side face of the fourth column section and the inner surface of the pilot valve cavity form a second buffer cavity, the first control cavity and the second buffer cavity are not communicated in the pilot valve cavity, the left side face of the third column section, the right side face of the second column section and the inner surface of the pilot valve cavity form a first buffer cavity, the first buffer cavity and the second buffer cavity are not communicated in the pilot valve cavity, the left side face of the second column section, the right side face of the first column section and the inner surface of the pilot valve cavity form a drain cavity, a pilot valve body at the position corresponding to the drain cavity is provided with a pilot valve oil inlet and a pilot valve oil outlet, the connection and disconnection of the pilot valve oil inlet and the pilot valve oil outlet in the drain cavity can be controlled along with the movement of the pilot valve core, and the, and a pilot valve spring is arranged in the second control cavity, and the pilot valve spring sets the initial state of the pilot valve core to be pressed to the right end so as to disconnect the communication between the pilot valve oil inlet and the pilot valve oil outlet.
The oil inlet of the main valve body is simultaneously communicated with the pilot valve oil inlet and a second buffer cavity through an oil way, a first damping hole is formed in the oil way, the pilot valve oil outlet is communicated with an oil tank, and the second buffer cavity is also simultaneously communicated with the first buffer cavity and the main valve control cavity through a second damping hole; the right end of the differential pressure compensation pilot valve is provided with a proportional electromagnet, the proportional electromagnet is also provided with a first displacement sensor, and the proportional electromagnet is used for detecting the displacement and the speed of the pilot valve core; and a second displacement sensor is arranged at the rear end of the main valve spool and detects the displacement of the main valve spool.
2. The differential pressure compensation valve with rapid and stable main valve opening according to claim 1, further characterized in that the slope of the valve port reducing section is the same as the slope of the main valve spool guiding portion.
3. A fluid path system, which uses the pressure difference compensation valve according to claim 1 or 2, further comprising a main fluid path, an oil return path, and a directional control valve, wherein a first oil inlet of the directional control valve is communicated with the main fluid path, an oil outlet of the directional control valve is communicated with the oil return path, a third working fluid port of the directional control valve is communicated with an oil inlet of a main valve body and the first control chamber, an oil outlet of the main valve body is communicated with a second fluid port of the directional control valve and a load sensitive fluid path, the load sensitive fluid path is communicated with the second control chamber, and the first working fluid port and the second working fluid port of the directional control valve are respectively communicated with two chambers of the actuator.
CN202010509316.9A 2020-06-07 2020-06-07 Differential pressure compensation valve with fast and stable main valve opening Withdrawn CN111608980A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202010509316.9A CN111608980A (en) 2020-06-07 2020-06-07 Differential pressure compensation valve with fast and stable main valve opening

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202010509316.9A CN111608980A (en) 2020-06-07 2020-06-07 Differential pressure compensation valve with fast and stable main valve opening

Publications (1)

Publication Number Publication Date
CN111608980A true CN111608980A (en) 2020-09-01

Family

ID=72205657

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202010509316.9A Withdrawn CN111608980A (en) 2020-06-07 2020-06-07 Differential pressure compensation valve with fast and stable main valve opening

Country Status (1)

Country Link
CN (1) CN111608980A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112253820A (en) * 2020-10-19 2021-01-22 中国核动力研究设计院 Pilot valve for pilot safety valve and pilot safety valve
CN112555214A (en) * 2020-12-10 2021-03-26 山东泰丰智能控制股份有限公司 Three-port two-way constant pressure difference valve
CN116951043A (en) * 2023-09-21 2023-10-27 四川宁江山川机械有限责任公司 Pilot valve of electromagnetic valve of shock absorber

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112253820A (en) * 2020-10-19 2021-01-22 中国核动力研究设计院 Pilot valve for pilot safety valve and pilot safety valve
CN112555214A (en) * 2020-12-10 2021-03-26 山东泰丰智能控制股份有限公司 Three-port two-way constant pressure difference valve
CN112555214B (en) * 2020-12-10 2021-07-23 山东泰丰智能控制股份有限公司 Three-port two-way constant pressure difference valve
CN116951043A (en) * 2023-09-21 2023-10-27 四川宁江山川机械有限责任公司 Pilot valve of electromagnetic valve of shock absorber

Similar Documents

Publication Publication Date Title
CN111608980A (en) Differential pressure compensation valve with fast and stable main valve opening
US8602321B2 (en) Ball valve with reduced erosion behavior
US4785849A (en) Pressure reducing valve assembly
KR20000052553A (en) Hydraulic damper of damping force adjusting type
CN108223493B (en) Balance valve with variable pilot ratio
CN101655165B (en) Novel three-way pressure reducing valve
CN101275685B (en) Emulsifiable solution medium large flow safety valve
JP2000227102A (en) Relief valve
CN101278132B (en) Hydraulic control device
CN111396391B (en) High-precision large-flow multi-way valve with disturbance compensation
CN202629286U (en) Change-over valve
CN113236623B (en) Electro-hydraulic proportional direction valve with independently controlled valve port
US5038822A (en) Flow rate control valving apparatus
CN2751169Y (en) Hydraulic controlled reversing valve
CN214118617U (en) Variable pump control valve
CN211715438U (en) Electro-hydraulic control valve capable of regulating flow gain
CN204533024U (en) A kind of novel electricity liquid ratio relief valve
CN1300499C (en) Ratio pressure difference control valve
CN111550463A (en) Direct-acting three-way pressure reducing valve for regulating pressure by servo motor
CN220622311U (en) Hydraulic control reversing valve group with adjustable pressure
CN219994027U (en) External damping plug
CN116336024A (en) Electro-hydraulic reversing flow proportional control valve with load flow compensation
CN220365983U (en) Hydraulic reversing valve
CN212202679U (en) Flow control friction-reducing long cone valve structure for multi-way valve
CN113309749B (en) Digital control type hydraulic triode

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
WW01 Invention patent application withdrawn after publication
WW01 Invention patent application withdrawn after publication

Application publication date: 20200901