CN111022403B - Pressure compensation valve capable of being integrated in cartridge valve hydraulic system and working method - Google Patents
Pressure compensation valve capable of being integrated in cartridge valve hydraulic system and working method Download PDFInfo
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- CN111022403B CN111022403B CN201911288679.8A CN201911288679A CN111022403B CN 111022403 B CN111022403 B CN 111022403B CN 201911288679 A CN201911288679 A CN 201911288679A CN 111022403 B CN111022403 B CN 111022403B
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- 238000000034 method Methods 0.000 title claims abstract description 8
- 229910000831 Steel Inorganic materials 0.000 claims description 11
- 239000010959 steel Substances 0.000 claims description 11
- 238000010586 diagram Methods 0.000 description 2
- 230000010354 integration Effects 0.000 description 2
- 238000005266 casting Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
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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
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- 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
- F16K11/0716—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 with fluid passages through the valve member
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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
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
- F15B2013/004—Cartridge valves
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Safety Valves (AREA)
- Fluid-Pressure Circuits (AREA)
- Multiple-Way Valves (AREA)
Abstract
The invention relates to a pressure compensation valve capable of being integrated in a cartridge valve hydraulic system and a working method. The invention has the advantages of plug-in design, compact structure, low processing cost and capability of realizing the pressure compensation function.
Description
Technical Field
The invention belongs to the technical field of valves, and particularly relates to a pressure compensation valve capable of being integrated in a cartridge valve hydraulic system and a working method.
Background
Pressure compensation techniques are very widely used in hydraulic systems. In the use process, the main oil way is connected with an oil inlet of the pressure compensation valve, an oil outlet of the pressure compensation valve is connected with an oil inlet of the proportional reversing valve, the highest pressure of two working oil ports of the proportional reversing valve is introduced into a spring cavity of the pressure compensation valve, and the pressure difference between the oil inlet and the working oil ports of the proportional reversing valve is adjusted through the pressure compensation valve, so that the flow output by the working oil ports of the proportional reversing valve is constant and is irrelevant to the working load change. However, the pressure compensation valves on the market at present are pressure compensation valves which are combined with a multi-way reversing valve in a casting form and are composed of a plurality of scattered parts, or pressure compensation valves in a single plate type connection or superposition type, and the pressure compensation valves in the above forms have the defects of inconvenience in cartridge type integration, overlarge volume, heavy weight and the like, and are not suitable for being applied to hydraulic systems integrated by cartridge valves.
Disclosure of Invention
The present invention is directed to provide a cartridge type pressure compensating valve that has a simple structure and a low manufacturing cost, and can be integrated in a cartridge type hydraulic system, in view of the above-mentioned current state of the art.
The technical scheme adopted by the invention for solving the technical problems is as follows: a plug-in type pressure compensation valve comprises a valve body, wherein a first mounting cavity and a second mounting cavity are axially arranged in the valve body, a first pressure oil port and a second pressure oil port which are communicated with the first mounting cavity are formed in the side wall of the valve body, and a first through hole which is communicated with the first mounting cavity and the second mounting cavity is further formed in the valve body; the shuttle valve assembly is arranged in the first mounting cavity and divides the first mounting cavity into a first through flow cavity communicated with the first pressure oil port, a second through flow cavity communicated with the second pressure oil port and a third through flow cavity communicated with the first through flow hole, and the shuttle valve assembly is provided with a first oil inlet communicated with the first through flow cavity, a second oil inlet communicated with the second through flow cavity and an oil outlet communicated with the third through flow cavity; one end of the valve sleeve extends into the second mounting cavity and is fixedly connected with the valve body through the retaining ring, a third pressure oil port is formed in the side wall of the middle of the valve sleeve, and a fourth pressure oil port is further formed in the other end of the valve sleeve along the axial direction; the valve core is arranged in the inner hole of the valve sleeve in a sliding mode, a second through flow hole communicated with the fourth pressure oil port is formed in the valve core along the axial direction, an annular first through flow groove communicated with the third pressure oil port is formed in the side wall of the valve core, a third through flow hole communicated with the first through flow groove and the second through flow hole is further formed in the valve core along the radial direction, and the communicating area of the first through flow groove and the third pressure oil port can be controlled by the left-right sliding of the valve core; the spring seat is arranged in the second mounting cavity, and one end of the spring seat is abutted against one end of the valve core; the spring is arranged in the second mounting cavity, one end of the spring abuts against the other end of the spring seat, and the other end of the spring abuts against the bottom surface of the second mounting cavity; and the plug is in threaded connection with the valve body so as to plug the opening of the first mounting cavity.
Preferably, the shuttle valve assembly comprises a first valve seat, a second valve seat and a steel ball, wherein an axial third mounting cavity, a radial second oil inlet, a fourth through hole for communicating the third mounting cavity with the second oil inlet and an oil outlet communicated with the third mounting cavity are arranged in the second valve seat; the first valve seat is fixedly arranged in the third mounting cavity, and a first oil inlet, a fifth through flow hole communicated with the third mounting cavity and a sixth through flow hole communicated with the first oil inlet and the fifth through flow hole are formed in the first valve seat; the steel ball is arranged in the sixth through-flow hole in a sliding mode, and the first oil inlet and the fourth through-flow hole can be plugged by sliding the steel ball left and right.
Preferably, the plug is provided with a seventh through flow hole communicated with the first oil inlet, and the plug is further provided with an eighth through flow hole communicated with the first through flow cavity and the seventh through flow hole.
Compared with the prior art, the invention has the advantages that:
(1) the invention is designed in a plug-in mode, has compact and reasonable structure, few parts and low cost and is convenient for integrated design.
(2) The invention can realize the pressure compensation function through the integration of the valve core and the shuttle valve assembly, solves the problem of the matching of the pressure compensation valve of the cartridge type proportional reversing valve and conveniently realizes the proportional flow control loop with the pressure compensation function consisting of the cartridge valve.
Drawings
FIG. 1 is a cross-sectional view of an embodiment of the present invention;
FIG. 2 is a block diagram of a shuttle valve assembly in an embodiment of the present invention;
FIG. 3 is a hydraulic schematic of an embodiment of the present invention;
fig. 4 is a schematic diagram of an embodiment of the present invention using hydraulic pressure.
Detailed Description
The invention is described in further detail below with reference to the accompanying examples.
As shown in fig. 1 to 3, a preferred embodiment of the present invention is shown.
A plug-in type pressure compensation valve comprises a valve body 1, a shuttle valve component 11, a valve sleeve 7, a valve core 6, a spring seat 5, a spring 4 and a plug 8.
The valve body 1 is internally provided with a first mounting cavity 101 and a second mounting cavity 102 along the axial direction, the side wall of the valve body is provided with a first pressure oil port C and a second pressure oil port D which are communicated with the first mounting cavity 101, and the valve body 1 is internally provided with a first through flow hole 103 which is communicated with the first mounting cavity 101 and the second mounting cavity 102.
The shuttle valve assembly 11 is arranged in the first mounting cavity 101 and divides the first mounting cavity 101 into a first through flow cavity 1a communicated with the first pressure port C, a second through flow cavity 1b communicated with the second pressure port D and a third through flow cavity 1C communicated with the first through flow hole 103, and a first oil inlet 21 communicated with the first through flow cavity 1a, a second oil inlet 31 communicated with the second through flow cavity 1b and an oil outlet 32 communicated with the third through flow cavity 1C are arranged on the shuttle valve assembly 11. The shuttle valve assembly 11 comprises a first valve seat 2, a second valve seat 3 and a steel ball 9, wherein an axial third mounting cavity 24, a radial second oil inlet 31, a fourth through hole 33 for communicating the third mounting cavity 24 with the second oil inlet 31 and an oil outlet 32 communicated with the third mounting cavity 24 are arranged in the second valve seat 3; the first valve seat 2 is fixedly arranged in a third mounting cavity 24, and a first oil inlet 21, a fifth through flow hole 23 communicated with the third mounting cavity 24 and a sixth through flow hole 22 communicated with the first oil inlet 21 and the fifth through flow hole 23 are arranged in the first valve seat 2; the steel ball 9 is slidably arranged in the sixth through flow hole 22, and can slide left and right to block the first oil inlet 21 and the fourth through flow hole 33.
One end of the valve sleeve 7 extends into the second mounting cavity 102 and is fixedly connected with the valve body 1 through the retaining ring 10, a third pressure port B is arranged on the side wall of the middle portion of the valve sleeve, and a fourth pressure port a is further arranged at the other end of the valve sleeve along the axial direction.
The valve core 6 is slidably arranged in an inner hole of the valve sleeve 7, a second through flow hole 61 communicated with the fourth pressure port A is axially arranged in the valve core, an annular first through flow groove 62 communicated with the third pressure port B is arranged on the side wall of the valve core 6, a third through flow hole 63 communicated with the first through flow groove 62 and the second through flow hole 61 is further radially arranged in the valve core, and the communication area of the first through flow groove 62 and the third pressure port B can be controlled by the left-right sliding of the valve core 6.
And a spring seat 5 provided in the second mounting cavity 102, one end of which abuts against one end of the valve element 6.
And the spring 4 is arranged in the second mounting cavity 102, one end of the spring 4 abuts against the other end of the spring seat 5, and the other end of the spring abuts against the bottom surface of the second mounting cavity 102.
And the plug 8 is in threaded connection with the valve body 1 to plug the opening of the first mounting cavity 101, a seventh through flow hole 82 communicated with the first oil inlet 21 is formed in the plug 8, and an eighth through flow hole 81 communicated with the first through flow cavity 1a and the seventh through flow hole 82 is further formed in the plug 8.
The working principle and the process of the invention are as follows:
as shown in fig. 4, in practical use, the third pressure port B of the cartridge type pressure compensating valve 13 of the present invention is connected to the outlet of the hydraulic pump 12, the fourth pressure port a is connected to the port P of the proportional directional valve 14, the first pressure port C is connected to the port a1 of the proportional directional valve 14, and the second pressure port D is connected to the port B1 of the proportional directional valve 14.
If the proportional reversing valve 14 works in the left position, the oil port P is communicated with the oil port B1, the oil port a1 is communicated with the oil port T, oil at the outlet of the hydraulic pump 12 sequentially passes through the third pressure oil port B, the first through-flow groove 62, the third through-flow hole 63, the second through-flow hole 61, the fourth pressure oil port a and the oil port P and then enters the oil port B1, and at the moment, the pressure of the oil port B1 is greater than the pressure of the oil port a 1; the oil of the oil port B1 passes through the first through-flow cavity 1a, the eighth through-flow hole 81, the seventh through-flow hole 82, the first oil inlet 21 and the sixth through-flow hole 22 in sequence by the first pressure oil port C and then acts on the steel ball 9, the steel ball 9 is pushed rightwards to block the fourth through-flow hole 33, the oil of the oil port B1 passes through the fifth through-flow hole 23, the third mounting cavity 24, the oil outlet 32, the third through-flow cavity 1C and the first through-flow hole 103 in sequence by the sixth through-flow hole 22 and then enters the second mounting cavity 102 to act on the valve core 6; if the load of the oil port B1 changes to increase the pressure difference between the fourth pressure oil port a and the oil port B1, the valve core 6 moves leftward under the action of the pressure difference, the communication area between the first through flow groove 62 and the third pressure oil port B is reduced, the pressure difference between the fourth pressure oil port a and the oil port B1 is maintained to be basically constant, the function of pressure compensation is realized, and the output flow of the oil port B1 can be maintained to be constant on the premise that the opening of the proportional directional valve 14 is not changed; if the load of the oil port B1 changes to reduce the pressure difference between the fourth pressure oil port a and the oil port B1, the valve element 6 moves rightward under the action of the pressure difference, the communication area between the first through-flow groove 62 and the third pressure oil port B is increased, the pressure difference between the fourth pressure oil port a and the oil port B1 is maintained to be basically constant, the function of pressure compensation is realized, and the output flow of the oil port B1 can be maintained to be constant on the premise that the opening of the proportional directional valve 14 is not changed.
If the proportional reversing valve 14 works at the right position, the oil port P is communicated with the oil port a1, the oil port B1 is communicated with the oil port T, oil at the outlet of the hydraulic pump 12 sequentially passes through the third pressure oil port B, the first through-flow groove 62, the third through-flow hole 63, the second through-flow hole 61, the fourth pressure oil port a and the oil port P and then enters the oil port B1, and at the moment, the pressure of the oil port a1 is greater than the pressure of the oil port B1; the pressure of the oil port A1 enters the second mounting cavity 102 and acts on the valve core 6 after being selected by the shuttle valve assembly 11; if the load of the oil port a1 changes to increase the pressure difference between the fourth pressure oil port a and the oil port a1, the valve core 6 moves leftwards under the action of the pressure difference, the communication area between the first through-flow groove 62 and the third pressure oil port B is reduced, the pressure difference between the fourth pressure oil port a and the oil port a1 is maintained to be basically constant, the pressure compensation function is realized, and the output flow of the oil port a1 can be maintained to be constant on the premise that the opening of the proportional directional valve 14 is not changed; if the pressure difference between the fourth pressure port a and the port a1 is reduced due to the load change of the port a1, the valve element 6 moves rightward under the action of the pressure difference, the communication area between the first through flow groove 62 and the third pressure port B is increased, the pressure difference between the fourth pressure port a and the port B1 is maintained to be basically constant, the pressure compensation function is realized, and the output flow of the port a1 can be maintained to be constant on the premise that the opening of the proportional directional valve 14 is not changed.
Claims (1)
1. The working method of the cartridge type pressure compensation valve is characterized in that: the plug-in pressure compensation valve comprises
The valve comprises a valve body (1), wherein a first mounting cavity (101) and a second mounting cavity (102) are axially arranged in the valve body (1), a first pressure oil port (C) and a second pressure oil port (D) which are communicated with the first mounting cavity (101) are formed in the side wall of the valve body (1), and a first through flow hole (103) which is communicated with the first mounting cavity (101) and the second mounting cavity (102) is further formed in the valve body (1);
the shuttle valve assembly (11) is arranged in the first mounting cavity (101) and divides the first mounting cavity (101) into a first through flow cavity (1a) communicated with the first pressure oil port (C), a second through flow cavity (1 b) communicated with the second pressure oil port (D) and a third through flow cavity (1C) communicated with the first through flow hole (103), and a first oil inlet (21) communicated with the first through flow cavity (1a), a second oil inlet (31) communicated with the second through flow cavity (1 b) and an oil outlet (32) communicated with the third through flow cavity (1C) are formed in the shuttle valve assembly (11);
one end of the valve sleeve (7) extends into the second mounting cavity (102) and is fixedly connected with the valve body (1) through the retaining ring (10), a third pressure oil port (B) is formed in the side wall of the middle of the valve sleeve, and a fourth pressure oil port (A) is further formed in the other end of the valve sleeve along the axial direction;
the valve core (6) is arranged in an inner hole of the valve sleeve (7) in a sliding mode, a second through flow hole (61) communicated with the fourth pressure oil port (A) is formed in the valve core along the axial direction, an annular first through flow groove (62) communicated with the third pressure oil port (B) is formed in the side wall of the valve core, a third through flow hole (63) communicated with the first through flow groove (62) and the second through flow hole (61) is further formed in the valve core along the radial direction, and the communicating area of the first through flow groove (62) and the third pressure oil port (B) can be controlled by the left-right sliding of the valve core (6);
the spring seat (5) is arranged in the second mounting cavity (102), and one end of the spring seat is abutted against one end of the valve core (6);
the spring (4) is arranged in the second mounting cavity (102), one end of the spring abuts against the other end of the spring seat (5), and the other end of the spring abuts against the bottom surface of the second mounting cavity (102);
the plug (8) is connected to the valve body (1) in a threaded manner so as to plug the opening of the first mounting cavity (101); a seventh through flow hole (82) communicated with the first oil inlet (21) is formed in the plug (8), and an eighth through flow hole (81) communicated with the first through flow cavity (1a) and the seventh through flow hole (82) is further formed in the plug (8);
the shuttle valve assembly (11) comprises a first valve seat (2), a second valve seat (3) and a steel ball (9), wherein an axial third mounting cavity (24), a radial second oil inlet (31), a fourth through-flow hole (33) for communicating the third mounting cavity (24) with the second oil inlet (31) and an oil outlet (32) communicated with the third mounting cavity (24) are formed in the second valve seat (3); the first valve seat (2) is fixedly arranged in the third mounting cavity (24) and is internally provided with a first oil inlet (21), a fifth through flow hole (23) communicated with the third mounting cavity (24) and a sixth through flow hole (22) communicated with the first oil inlet (21) and the fifth through flow hole (23); the steel ball (9) is arranged in the sixth through flow hole (22) in a sliding manner, and can block the first oil inlet (21) and the fourth through flow hole (33) in a left-right sliding manner;
the third pressure oil port (B) is connected with an outlet of the hydraulic pump (12), the fourth pressure oil port (A) is connected with an oil port P of the proportional reversing valve (14), the first pressure oil port (C) is connected with an oil port A1 of the proportional reversing valve (14), and the second pressure oil port (D) is connected with an oil port B1 of the proportional reversing valve (14);
if the proportional reversing valve (14) works at the left position, the oil port P is communicated with the oil port B1, the oil port A1 is communicated with the oil port T, oil at the outlet of the hydraulic pump (12) sequentially passes through the third pressure oil port (B), the first through flow groove (62), the third through flow hole (63), the second through flow hole (61), the fourth pressure oil port (A) and the oil port P and then enters the oil port B1, and at the moment, the pressure of the oil port B1 is greater than the pressure of the oil port A1; oil of the oil port B1 sequentially passes through a first flow cavity (1a), an eighth flow hole (81), a seventh flow hole (82), a first oil inlet (21) and a sixth flow hole (22) by a first pressure oil port (C) and then acts on the steel ball (9), the steel ball (9) is pushed rightwards to block the fourth flow hole (33), and oil of the oil port B1 sequentially passes through a fifth flow hole (23), a third mounting cavity (24), an oil outlet (32), a third flow cavity (1C) and the first flow hole (103) by the sixth flow hole (22) and then enters a second mounting cavity (102) to act on the valve core (6); if the load of the oil port B1 changes to cause the pressure difference between the fourth pressure oil port (A) and the oil port B1 to be increased, the valve core (6) moves leftwards under the action of the pressure difference, the communication area between the first through flow groove (62) and the third pressure oil port (B) is reduced, the pressure difference between the fourth pressure oil port (A) and the oil port B1 is maintained to be basically constant, the pressure compensation function is realized, and the output flow of the oil port B1 can be maintained to be constant on the premise that the opening of the proportional directional valve (14) is not changed; if the pressure difference between the fourth pressure oil port (a) and the oil port B1 is reduced due to the load change of the oil port B1, the valve core (6) moves rightwards under the action of the pressure difference, the communication area between the first through flow groove (62) and the third pressure oil port (B) is increased, the pressure difference between the fourth pressure oil port (a) and the oil port B1 is maintained to be basically constant, the function of pressure compensation is realized, and the output flow of the oil port B1 can be maintained to be constant on the premise that the opening of the proportional directional valve (14) is not changed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911288679.8A CN111022403B (en) | 2018-06-08 | 2018-06-08 | Pressure compensation valve capable of being integrated in cartridge valve hydraulic system and working method |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810588233.6A CN108661966B (en) | 2018-06-08 | 2018-06-08 | Plug-in type pressure compensation valve |
| CN201911288679.8A CN111022403B (en) | 2018-06-08 | 2018-06-08 | Pressure compensation valve capable of being integrated in cartridge valve hydraulic system and working method |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810588233.6A Division CN108661966B (en) | 2018-06-08 | 2018-06-08 | Plug-in type pressure compensation valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111022403A CN111022403A (en) | 2020-04-17 |
| CN111022403B true CN111022403B (en) | 2021-10-26 |
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Family Applications (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911275400.2A Active CN110905880B8 (en) | 2018-06-08 | 2018-06-08 | Pressure compensation valve and valve core of cartridge valve hydraulic system |
| CN201810588233.6A Active CN108661966B (en) | 2018-06-08 | 2018-06-08 | Plug-in type pressure compensation valve |
| CN201911288679.8A Active CN111022403B (en) | 2018-06-08 | 2018-06-08 | Pressure compensation valve capable of being integrated in cartridge valve hydraulic system and working method |
Family Applications Before (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911275400.2A Active CN110905880B8 (en) | 2018-06-08 | 2018-06-08 | Pressure compensation valve and valve core of cartridge valve hydraulic system |
| CN201810588233.6A Active CN108661966B (en) | 2018-06-08 | 2018-06-08 | Plug-in type pressure compensation valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (3) | CN110905880B8 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116771950A (en) * | 2021-03-30 | 2023-09-19 | 陕西华诚领航电磁科技有限责任公司 | Proportional solenoid valve and pressure regulating device therein |
| CN114754167A (en) * | 2022-05-17 | 2022-07-15 | 潍柴动力股份有限公司 | Shuttle valve |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2270467B1 (en) * | 1974-03-29 | 1977-09-30 | Mercier Bernard | |
| ZA771041B (en) * | 1976-05-06 | 1977-12-28 | Commercial Shearing | Control valves |
| JP2557000B2 (en) * | 1990-05-15 | 1996-11-27 | 株式会社小松製作所 | Control valve device |
| DE29509213U1 (en) * | 1995-03-24 | 1996-07-25 | O & K Orenstein & Koppel Ag, 13581 Berlin | Device for flow pressure-independent flow distribution in a spool for mobile construction and work machines |
| CN101922477B (en) * | 2009-06-09 | 2013-02-06 | 上海立新液压有限公司 | Pressure-compensated valve |
| CN102094863B (en) * | 2010-12-30 | 2013-09-04 | 江苏国瑞液压机械有限公司 | Electrohydraulic ratio multi-channel control valve with convertible pressure compensation mode |
| CN102434519B (en) * | 2011-11-29 | 2014-10-15 | 三一汽车起重机械有限公司 | Engineering machine and flow distributing and converging hydraulic control system thereof |
| CN202579417U (en) * | 2012-06-06 | 2012-12-05 | 常德中联重科液压有限公司 | Hydraulic circuit |
| CN203081879U (en) * | 2013-02-21 | 2013-07-24 | 中联重科股份有限公司 | hydraulic control circuit |
| CN103216477B (en) * | 2013-04-28 | 2016-03-16 | 贵州大学 | A kind of metering pump pressure compensating method of single-power hydraulic power and device |
| CN105443480B (en) * | 2014-08-12 | 2017-09-08 | 徐工集团工程机械股份有限公司 | Work connection valve body structure and proportional multi-way valve |
| CN104265715B (en) * | 2014-10-16 | 2017-02-15 | 江苏恒立液压科技有限公司 | pressure compensating valve |
| CN205533507U (en) * | 2016-04-22 | 2016-08-31 | 青神格林维尔流体动力控制技术有限公司 | Take pressure compensation's hydraulic pressure proportional valve piece |
-
2018
- 2018-06-08 CN CN201911275400.2A patent/CN110905880B8/en active Active
- 2018-06-08 CN CN201810588233.6A patent/CN108661966B/en active Active
- 2018-06-08 CN CN201911288679.8A patent/CN111022403B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN110905880B8 (en) | 2021-12-31 |
| CN110905880A (en) | 2020-03-24 |
| CN108661966B (en) | 2019-12-20 |
| CN108661966A (en) | 2018-10-16 |
| CN110905880B (en) | 2021-12-03 |
| CN111022403A (en) | 2020-04-17 |
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Effective date of registration: 20211213 Address after: 256600 No. 1, Gaosi Road, high tech Industrial Development Zone, Binzhou City, Shandong Province Patentee after: Binzhou Kechuang Incubator Co.,Ltd. Address before: 213000 No.199, Keji Avenue, Longhutang Industrial Park, Xinbei District, Changzhou City, Jiangsu Province Patentee before: Zhang Linghua |