CN107725517B - Proportional flow solenoid valve - Google Patents
Proportional flow solenoid valve Download PDFInfo
- Publication number
- CN107725517B CN107725517B CN201710916072.4A CN201710916072A CN107725517B CN 107725517 B CN107725517 B CN 107725517B CN 201710916072 A CN201710916072 A CN 201710916072A CN 107725517 B CN107725517 B CN 107725517B
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- valve core
- control valve
- pressure control
- pressure
- flow control
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Classifications
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- 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
-
- 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
The invention discloses a proportional flow electromagnetic valve which comprises a proportional electromagnet, a pressure control valve core, a flow control valve core, a valve sleeve, a flow control spring and a plug. The electromagnetic force of the electromagnetic valve is not used for directly controlling the flow, but is used for controlling the hydraulic pressure of a pressure containing cavity in the electromagnetic valve, and the position of a valve core is controlled through the balance of the hydraulic pressure in the containing cavity and the spring force, so that the size of the throttling hole is adjusted to control the flow.
Description
Technical Field
The invention relates to a proportional flow electromagnetic valve. The hydraulic drive device is suitable for the field of hydraulic drive.
Background
The existing electromagnetic proportional flow control valve generally controls the position of a valve core through the balance of the electromagnetic force of a proportional electromagnet and the force of a spring so as to adjust the size of a throttling hole to control the size of flow, only a relatively horizontal part of an electromagnetic force air gap curve of the proportional electromagnet can meet the control requirement of the proportional electromagnet, and the relatively horizontal part only has a short air gap interval, so that the valve core of the valve has shorter stroke and lower control precision, and can not meet the requirement of large flow.
Disclosure of Invention
The invention aims to provide a proportional flow solenoid valve, the electromagnetic force of the solenoid valve is not used for directly controlling the flow, but is used for controlling the hydraulic pressure of a pressure cavity in the solenoid valve, and the position of a valve core is controlled by balancing the hydraulic pressure in the cavity and the spring force, so that the size of a throttling hole is adjusted to control the size of the flow.
In order to achieve the technical purpose, the invention adopts the following technical scheme:
a proportional flow electromagnetic valve comprises a proportional electromagnet, a pressure control valve core, a flow control valve core, a valve sleeve, a flow control spring and a plug, wherein one end of the valve sleeve is connected to the proportional electromagnet, a valve core hole with a cylindrical structure is formed in the valve sleeve, the pressure control valve core and the flow control valve core are sequentially arranged in the valve core hole in the axial direction, one end of the pressure control valve core is connected with the proportional electromagnet, and the other end of the pressure control valve core is in transmission connection with the flow control valve core through a pressure feedback cavity;
the valve sleeve is sequentially provided with: an oil return port communicated with the oil return channel, a pressure control port and a flow control port communicated with the hydraulic source, and a load port communicated with a load;
the pressure control valve core is provided with at least two large-diameter valve core sections which are in close fit with the inner wall of the valve core hole, and at least one small-diameter valve core section which is positioned between the two large-diameter valve core sections, a pressure control cavity is formed between the small-diameter valve core section and the inner wall of the valve core hole, and the pressure control cavity is communicated with the pressure feedback cavity through a communication channel;
the other end of the valve sleeve is connected with a plug, and the flow control spring is connected between the plug and the flow control valve core.
The pressure control valve core comprises a first pressure control valve core section, a second pressure control valve core section, a third pressure control valve core section and a fourth valve core section, wherein the diameter of the second pressure control valve core section is the same as that of the fourth pressure control valve core section, and the outer circular surfaces of the second pressure control valve core section and the fourth pressure control valve core section are matched with the inner circular surface of the valve core hole to form a sealing strip; the diameter of the third pressure control valve core section is smaller than that of the second pressure control valve core section and that of the fourth pressure control valve core section, and a pressure control cavity is formed between the outer circular surface of the third pressure control valve core section and the inner circular surface of the valve core hole;
the flow control valve core comprises a first flow control valve core section, a second flow control valve core section, a third flow control valve core section and a fourth flow control valve core section, wherein the diameter of the second flow control valve core section is the same as that of the fourth flow control valve core section, and the outer circular surfaces of the second flow control valve core section and the fourth flow control valve core section are matched with the inner circular surface of the valve core hole to form a sealing belt; the diameter of the third flow control valve core section is smaller than that of the second flow control valve core section and that of the fourth flow control valve core section, and a flow control cavity for communicating the flow control port with the load port is formed between the outer circular surface of the third flow control valve core section and the inner circular surface of the valve core hole;
the end part of a fourth pressure control valve core section on the pressure control valve core is processed with a shaft hole, a first pressure control valve core section on the pressure control valve core section is inserted into the shaft hole and the wall surface of the shaft hole to form the pressure feedback cavity, a first communicating hole is processed on the pressure control valve core along the radial direction, a second communicating hole is processed on the end surface close to the shaft hole along the axial direction of the pressure control valve core, and the two communicating holes are communicated to form the communicating channel.
And the first pressure control valve core section is connected with a pressure control spring, and the pressure control valve core is in abutting connection with an armature iron in the proportional electromagnet under the elastic force of the pressure control spring.
And a limiting boss is processed on the part, close to the plug, of the fourth flow control valve core section and is used for ensuring that the first flow control valve core section is not in contact with the bottom of the pressure feedback cavity during working.
The pressure control port P1 and the flow control port P2 are directly communicated or connected with different hydraulic pressure sources outside the electromagnetic valve.
When the electromagnetic valve is not electrified, a large-diameter valve core section on a pressure control valve core closes a channel between a pressure control port and a pressure control cavity, a channel between an oil return port and the pressure control cavity is opened, hydraulic oil in the pressure control cavity and a pressure feedback cavity flows out through the oil return port, the hydraulic pressure is zero, the channel between a load port and the flow control port is opened to the maximum under the action of a flow control spring by the flow control valve core, and the output flow of the electromagnetic valve is the maximum at the moment;
when the electromagnetic valve inputs a certain current, the electromagnetic force pushes the pressure control valve core to move towards the X direction to open a channel between the pressure control port and the pressure control cavity, and hydraulic oil enters the pressure control cavity and the pressure feedback cavity;
when the hydraulic pressure rises to the state that the resultant force of the hydraulic pressure acting on the pressure control valve core and the pressure control spring is greater than the electromagnetic force, the pressure control valve core moves towards the Y direction to close a channel between the pressure control port and the pressure control cavity and open a channel between the oil return port and the pressure control cavity to enable the hydraulic pressure to drop;
when the hydraulic pressure, the spring force of the pressure control spring and the electromagnetic force are balanced, the pressure control valve element is stabilized near the fixed working point position, passages between the pressure control cavity and the oil return port and between the pressure control cavity and the pressure control port are closed, the hydraulic pressure does not change any more, the hydraulic pressure and the flow control spring act together to control the flow control valve element, the flow control valve element can be stabilized at a fixed position under the action of the fixed hydraulic pressure, the size of the hydraulic pressure in the pressure control cavity and the pressure feedback cavity can be linearly adjusted by controlling the size of the driving current of the electromagnetic valve, the position of the flow control valve element can be linearly adjusted, and the size of the passages of the flow control port and the load port can be controlled by the position of the.
The invention has the beneficial effects that:
the invention relates to a proportional flow electromagnetic valve, wherein a pressure control cavity and a pressure feedback cavity communicated with the pressure control cavity are processed in the electromagnetic valve, hydraulic oil in the pressure feedback cavity can generate a pair of hydraulic pressures which are equal in size and opposite in direction to a pressure control valve core and a pressure control valve core, and the magnitude of the hydraulic pressure is in direct proportion to the hydraulic pressure in the pressure feedback cavity.
The size of the driving current of the electromagnetic valve can be controlled to linearly adjust the hydraulic pressure in the pressure control cavity and the pressure feedback cavity, so that the position of the flow control valve core can be linearly adjusted, and the position of the flow control valve core can control the size of a channel for hydraulic oil to flow into a load, so that the flow rate can be controlled.
The pressure control valve core mainly works near a working point, the required working stroke is small, the characteristics of the proportional electromagnet can well meet the working requirements, the movement of the flow control valve core is not influenced by the electromagnet, the large working stroke can be realized, the flow control precision is improved, and the large flow requirement is met.
Drawings
FIG. 1 is a schematic structural diagram of a proportional flow solenoid valve according to the present invention;
FIG. 2 is a schematic structural view of a pressure control valve cartridge according to the present invention;
fig. 3 is a schematic structural diagram of the flow control valve core of the present invention.
Wherein, 1, proportion electromagnet; 2. a connector assembly; 3. an armature sleeve; 4. a housing; 5. a coil bobbin; 6. a coil; 7. a stationary iron core; 8. a flange; 9. a pressure control valve core; 10. a communication channel; 11. a valve housing; 12. a flow control valve core; 13. a flow control spring; 14. a plug; 15. a top cover; 16. an armature; 17. a clamp spring; 18. a limiting sheet; 19. controlling a pressure spring; 21. a pressure control chamber; 23. a pressure feedback cavity, a T and an oil return port; p1, pressure control port; p2, flow control port; A. a load port; 9-1, a first pressure control valve core section; 9-2, a second pressure control valve core section; 9-3, a third control valve core section; 9-4, a fourth pressure control valve core section; 12-1, a first flow control valve core section; 12-2, a second flow control valve core section; 12-3, a third flow control valve core section; 12-4 and a fourth flow control valve core section.
Detailed Description
The technical solution of the present invention will be further described in detail with reference to the drawings and specific examples.
As shown in fig. 1, a proportional flow electromagnetic valve includes a proportional electromagnet 1, a pressure control valve core 9, a flow control valve core 12, a valve sleeve 11, a flow control spring 13 and a plug 14, wherein one end of the valve sleeve 11 is connected with the proportional electromagnet 1, and the other end of the valve sleeve 11 is fixedly connected with the plug 14; a valve core hole with a cylindrical structure is arranged between the proportional electromagnet and the plug in the valve sleeve 11, a pressure control valve core 9, a flow control valve core 12 and a flow control spring 13 are sequentially arranged in the valve core hole in the axial direction, the pressure control valve core 9 and the flow control valve core 12 can slide along the axial direction of the valve core hole,
the valve sleeve 11 is sequentially provided with: an oil return port T communicated with the oil return channel, a pressure control port P1 and a flow control port P2 communicated with a hydraulic source, and a load port A communicated with a load;
the pressure control valve core comprises a first pressure control valve core section, a second pressure control valve core section, a third pressure control valve core section and a fourth valve core section, wherein the diameter of the second pressure control valve core section is the same as that of the fourth pressure control valve core section, and the outer circular surfaces of the second pressure control valve core section and the fourth pressure control valve core section are matched with the inner circular surface of the valve core hole to form a sealing strip; the diameter of the third pressure control valve core section is smaller than that of the second pressure control valve core section and that of the fourth pressure control valve core section, and a pressure control cavity is formed between the outer circular surface of the third pressure control valve core section and the inner circular surface of the valve core hole;
the flow control valve core comprises a first flow control valve core section, a second flow control valve core section, a third flow control valve core section and a fourth flow control valve core section, wherein the diameter of the second flow control valve core section is the same as that of the fourth flow control valve core section, and the outer circular surfaces of the second flow control valve core section and the fourth flow control valve core section are matched with the inner circular surface of the valve core hole to form a sealing belt; the diameter of the third flow control valve core section is smaller than that of the second flow control valve core section and that of the fourth flow control valve core section, and a flow control cavity for communicating the flow control port with the load port is formed between the outer circular surface of the third flow control valve core section and the inner circular surface of the valve core hole;
the end part of a fourth pressure control valve core section on the pressure control valve core is processed with a shaft hole, a first pressure control valve core section on the pressure control valve core section is inserted into the shaft hole and the wall surface of the shaft hole to form the pressure feedback cavity, a first communicating hole is processed on the pressure control valve core along the radial direction, a second communicating hole is processed on the end surface close to the shaft hole along the axial direction of the pressure control valve core, and the two communicating holes are communicated to form the communicating channel.
One end of the pressure control valve core is connected with the armature iron in the proportional electromagnet in an abutting mode through a flow control spring. The pressure control spring 19 has smaller rigidity and pretightening force and mainly plays a role in returning.
The end part of the flow control valve core close to the plug is provided with a limiting boss, so that the end surface of the other side of the flow control valve core is not contacted with the end surface of the pressure control valve core during working.
The pressure control port P1 and the flow control port P2 are directly communicated or connected with different hydraulic pressure sources outside the electromagnetic valve.
The outer surface of the pressure control valve core 9 is provided with two sections of sealing parts which are respectively matched with the inner surface of the valve sleeve to control the size of a channel between the oil return port T, the pressure control port P1 and the pressure control cavity 21; the outer surface of the flow control valve core 12 has two sections of sealing parts, one section controls the size of a channel between the load port A and the flow control port P2, and the other section prevents hydraulic oil from flowing out along the axial direction of the valve sleeve 11.
The solenoid valve shown in fig. 1 is a normally open type, when the solenoid valve is not powered on, the pressure control valve spool 9 is pressed against the leftmost end of the working stroke by the pressure control spring 19, a passage between the pressure control port P1 and the pressure control cavity 21 is closed, a passage between the oil return port T and the pressure control cavity 21 is opened, hydraulic oil in the pressure control cavity 21 and the pressure feedback cavity 23 flows out through the oil return port T, the hydraulic pressure is zero, the flow control valve spool 12 is pressed against the leftmost end of the working stroke by the flow control spring 13, the passage between the load port a and the flow control port P2 is opened to the maximum, and at this time, the output flow of the solenoid valve is maximum. The pressure control spring 19 has smaller rigidity and pretightening force and mainly plays a role in returning.
When the electromagnetic valve inputs a certain current, the electromagnetic force pushes the pressure control valve core 9 to move rightwards to open a channel between the pressure control port P1 and the pressure control cavity 21, and hydraulic oil enters the pressure control cavity 21 and the pressure feedback cavity 23; when the hydraulic pressure rises to the point that the resultant force of the hydraulic pressure acting on the pressure control valve core 9 and the spring force of the pressure control spring 19 is greater than the electromagnetic force, the pressure control valve core 9 moves leftwards to close a channel between the pressure control port P1 and the pressure control cavity 21 and open a channel between the oil return port T and the pressure control cavity 21 to enable the hydraulic pressure to drop; when the hydraulic pressure, the spring force of the pressure control spring 19 and the electromagnetic force are balanced, the pressure control valve core 9 is stabilized near the fixed working point position, the channels between the pressure control cavity 21 and the oil return port T and between the pressure control cavity and the pressure control port P1 are closed, the hydraulic pressure does not change any more, the hydraulic pressure and the spring force of the flow control spring 13 act together to control the flow control valve core 12, the flow control valve core 12 is stabilized at the fixed position under the action of the fixed hydraulic pressure, the hydraulic pressure in the pressure control cavity 21 and the pressure feedback cavity 23 can be linearly adjusted by controlling the driving current of the electromagnetic valve, the position of the flow control valve core 12 is linearly adjusted, and the position of the flow control valve core 12 can control the size of the channels of the flow control port P2 and the load port A, so. The pressure control valve core 9 mainly works near a working point, the required working stroke is small, the working requirement of the proportional electromagnet 1 can be well met due to the characteristic of the proportional electromagnet 1, the movement of the flow control valve core 12 is not affected by the electromagnet 1, the large working stroke can be realized, the flow control precision is improved, and the large flow requirement is met.
Although preferred embodiments of the present invention have been described in detail hereinabove, it should be clearly understood that modifications and variations of the present invention are possible to those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (5)
1. A proportional flow electromagnetic valve is characterized by comprising a proportional electromagnet, a pressure control valve core, a flow control valve core, a valve sleeve, a flow control spring and a plug, wherein one end of the valve sleeve is connected to the proportional electromagnet, a valve core hole with a cylindrical structure is arranged in the valve sleeve, the pressure control valve core and the flow control valve core are sequentially arranged in the valve core hole in the axial direction, one end of the pressure control valve core is connected with the proportional electromagnet, and the other end of the pressure control valve core is in transmission connection with the flow control valve core through a pressure feedback cavity;
the valve sleeve is sequentially provided with: an oil return port communicated with the oil return channel, a pressure control port and a flow control port communicated with the hydraulic source, and a load port communicated with a load;
the pressure control valve core is provided with at least two large-diameter valve core sections which are in close fit with the inner wall of the valve core hole, and at least one small-diameter valve core section which is positioned between the two large-diameter valve core sections, a pressure control cavity is formed between the small-diameter valve core section and the inner wall of the valve core hole, and the pressure control cavity is communicated with the pressure feedback cavity through a communication channel;
the other end of the valve sleeve is connected with a plug, and the flow control spring is connected between the plug and the flow control valve core;
the pressure control valve core comprises a first pressure control valve core section, a second pressure control valve core section, a third pressure control valve core section and a fourth valve core section, wherein the diameter of the second pressure control valve core section is the same as that of the fourth pressure control valve core section, and the outer circular surfaces of the second pressure control valve core section and the fourth pressure control valve core section are matched with the inner circular surface of the valve core hole to form a sealing strip; the diameter of the third pressure control valve core section is smaller than that of the second pressure control valve core section and that of the fourth pressure control valve core section, and a pressure control cavity is formed between the outer circular surface of the third pressure control valve core section and the inner circular surface of the valve core hole;
the flow control valve core comprises a first flow control valve core section, a second flow control valve core section, a third flow control valve core section and a fourth flow control valve core section, wherein the diameter of the second flow control valve core section is the same as that of the fourth flow control valve core section, and the outer circular surfaces of the second flow control valve core section and the fourth flow control valve core section are matched with the inner circular surface of the valve core hole to form a sealing belt; the diameter of the third flow control valve core section is smaller than that of the second flow control valve core section and that of the fourth flow control valve core section, and a flow control cavity for communicating the flow control port with the load port is formed between the outer circular surface of the third flow control valve core section and the inner circular surface of the valve core hole;
the end part of a fourth pressure control valve core section on the pressure control valve core is processed with a shaft hole, a first pressure control valve core section on the pressure control valve core section is inserted into the shaft hole and the wall surface of the shaft hole to form the pressure feedback cavity, a first communicating hole is processed on the pressure control valve core along the radial direction, a second communicating hole is processed on the end surface close to the shaft hole along the axial direction of the pressure control valve core, and the two communicating holes are communicated to form the communicating channel.
2. The proportional flow solenoid valve of claim 1, wherein the first pressure control valve core segment is connected to a pressure control spring, and the pressure control valve core is in interference connection with an armature of the proportional electromagnet under the elastic force of the pressure control spring.
3. The proportional flow solenoid valve of claim 1, wherein a limiting boss is formed on a portion of the fourth flow control valve core section, which is close to the plug, and the limiting boss is used for ensuring that the first flow control valve core section is not in contact with the bottom of the pressure feedback cavity during operation.
4. The proportional flow solenoid valve of claim 1, wherein the control pressure port (P1) and the control flow port (P2) are directly communicated or connected to different hydraulic pressure sources outside the solenoid valve.
5. A working method of the proportional flow solenoid valve according to claim 1, characterized in that: when the electromagnetic valve is not electrified, a passage between the pressure control port and the pressure control cavity is closed by a large-diameter valve core section on the pressure control valve core, a passage between the oil return port and the pressure control cavity is opened, hydraulic oil in the pressure control cavity and the pressure feedback cavity flows out through the oil return port, the hydraulic pressure is zero, the passage between the load port and the flow control port is opened to the maximum by the flow control valve core under the action of the flow control spring, and the output flow of the electromagnetic valve is maximum at the moment;
when the electromagnetic valve inputs a certain current, the electromagnetic force pushes the pressure control valve core to move towards the X direction to open a channel between the pressure control port and the pressure control cavity, and hydraulic oil enters the pressure control cavity and the pressure feedback cavity;
when the hydraulic pressure rises to the state that the resultant force of the hydraulic pressure acting on the pressure control valve core and the pressure control spring is greater than the electromagnetic force, the pressure control valve core moves towards the Y direction to close a channel between the pressure control port and the pressure control cavity and open a channel between the oil return port and the pressure control cavity to enable the hydraulic pressure to drop;
when the hydraulic pressure, the spring force of the pressure control spring and the electromagnetic force are balanced, the pressure control valve element is stabilized near the fixed working point position, passages between the pressure control cavity and the oil return port and between the pressure control cavity and the pressure control port are closed, the hydraulic pressure does not change any more, the hydraulic pressure and the flow control spring act together to control the flow control valve element, the flow control valve element can be stabilized at a fixed position under the action of the fixed hydraulic pressure, the size of the hydraulic pressure in the pressure control cavity and the pressure feedback cavity can be linearly adjusted by controlling the size of the driving current of the electromagnetic valve, the position of the flow control valve element can be linearly adjusted, and the size of the passages of the flow control port and the load port can be controlled by the position of the.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710916072.4A CN107725517B (en) | 2017-09-30 | 2017-09-30 | Proportional flow solenoid valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710916072.4A CN107725517B (en) | 2017-09-30 | 2017-09-30 | Proportional flow solenoid valve |
Publications (2)
| Publication Number | Publication Date |
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| CN107725517A CN107725517A (en) | 2018-02-23 |
| CN107725517B true CN107725517B (en) | 2019-12-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710916072.4A Active CN107725517B (en) | 2017-09-30 | 2017-09-30 | Proportional flow solenoid valve |
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| CN (1) | CN107725517B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108425906B (en) * | 2018-06-14 | 2019-08-23 | 建湖县八达液压机械有限公司 | Hydraulic control proportional flow control valve |
| CN111306333B (en) * | 2020-03-01 | 2023-05-16 | 浙江人一阀门制造有限公司 | Safety valve |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11218239A (en) * | 1998-02-02 | 1999-08-10 | Kenji Masuda | Proportional solenoid type direction throttle valve |
| JP2001208234A (en) * | 2000-01-26 | 2001-08-03 | Denso Corp | Solenoid valve |
| JP2001280516A (en) * | 2000-03-30 | 2001-10-10 | Denso Corp | Pressure control valve |
| CN1295441C (en) * | 2004-11-05 | 2007-01-17 | 宁波华液机器制造有限公司 | Proportional differential pressure control valve |
| CN100414154C (en) * | 2006-11-08 | 2008-08-27 | 宁波华液机器制造有限公司 | Direct action type proportional pressure-reducing valve |
| US9599245B2 (en) * | 2011-02-28 | 2017-03-21 | Borgwarner Inc. | Two-stage variable force solenoid |
| EP2689141B1 (en) * | 2011-03-22 | 2015-02-18 | Parker-Hannifin Corporation | Electro-proportional pilot operated poppet valve with pressure compensation |
| CN202510814U (en) * | 2012-01-12 | 2012-10-31 | 上海昀锋液压有限公司 | Stacked proportional electromagnetic flow valve |
| CN107023669B (en) * | 2016-12-12 | 2018-11-30 | 中国第一汽车股份有限公司 | A kind of ratio pressure solenoid valve |
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2017
- 2017-09-30 CN CN201710916072.4A patent/CN107725517B/en active Active
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| CN107725517A (en) | 2018-02-23 |
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