CN112524112A - Differential pressure output valve - Google Patents
Differential pressure output valve Download PDFInfo
- Publication number
- CN112524112A CN112524112A CN202011362737.XA CN202011362737A CN112524112A CN 112524112 A CN112524112 A CN 112524112A CN 202011362737 A CN202011362737 A CN 202011362737A CN 112524112 A CN112524112 A CN 112524112A
- Authority
- CN
- China
- Prior art keywords
- valve
- pressure
- oil
- valve body
- hole
- 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.)
- Granted
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
- 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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
Abstract
The invention belongs to the technical field of hydraulic valves, and particularly relates to a differential pressure output valve. The invention mainly solves the technical problems of complex structure, poor shock resistance and unsuitability for the working site with bad working conditions of the existing differential pressure measuring meter of the hydraulic system. The technical scheme adopted by the invention is as follows: a differential pressure output valve comprises a front valve body, a rear valve body, a control piston, a push rod, a supporting seat, a reset spring, a valve core, a constant flow valve, a pressure measuring joint and a safety valve; a piston hole is transversely arranged in the middle of the front valve body, the control piston is arranged in the piston hole, the supporting seat is arranged in a supporting hole arranged at the right end of the piston hole of the front valve body, the push rod is arranged in a push rod hole arranged in the center of the supporting seat, and the left end of the push rod is contacted with the control piston; the right side of the front valve body is connected with the left side of the rear valve body, so that the right end of the push rod is in contact with the left end of the valve core.
Description
Technical Field
The invention belongs to the technical field of hydraulic valves, and particularly relates to a differential pressure output valve.
Background
In the aspect of differential pressure measurement of a hydraulic system, the existing means is to basically adopt a mechanical or electronic differential pressure gauge to carry out differential pressure measurement, however, the mechanical differential pressure gauge core has a complex structure, the electronic differential pressure gauge core has poor shock resistance, and the electronic differential pressure gauge core have high cost and are not suitable for being used in a work site with severe working conditions.
Disclosure of Invention
The invention aims to solve the technical problems of complex structure, poor shock resistance and unsuitability for being used in a working site with severe working conditions of the traditional hydraulic system differential pressure measuring meter, and provides a differential pressure output valve capable of directly outputting differential pressure of a hydraulic system through mechanical force self-balancing.
In order to solve the technical problems, the invention adopts the technical scheme that:
a differential pressure output valve comprises a front valve body, a rear valve body, a control piston, a push rod, a supporting seat, a reset spring, a valve core, a constant flow valve, a pressure measuring joint and a safety valve;
a piston hole is transversely arranged in the middle of the front valve body, the control piston is arranged in the piston hole, the supporting seat is arranged in a supporting hole arranged at the right end of the piston hole of the front valve body, the push rod is arranged in a push rod hole arranged in the center of the supporting seat, and the left end of the push rod is contacted with the control piston;
a stepped main valve hole is transversely formed in the middle of the rear valve body, the reset spring and the large cylindrical end of the valve core are arranged in the large cylindrical hole of the stepped main valve hole, the reset spring is positioned at the left end of the valve core, the small cylindrical end of the valve core is arranged in the small cylindrical hole of the stepped main valve hole, the right side surface of the front valve body is connected with the left side surface of the rear valve body, and the right end of the push rod is in contact with the left end of the valve core;
the constant flow valve is arranged at the lower part of the right end of the rear valve body and is respectively communicated with a high-pressure cavity on the left side of the control piston and a pressure measuring cavity at the right end of the valve core through oil ducts; the pressure measuring oil port is arranged in the middle of the right end face of the rear valve body, the pressure measuring joint is installed on the pressure measuring oil port, the pressure measuring oil port is communicated with the pressure measuring cavity through an oil duct, the safety valve is arranged on the right of the top face of the rear valve body, the lower end of the safety valve is communicated with the pressure measuring cavity through an oil duct, and an oil drainage port arranged on the lower portion of the safety valve is communicated with an oil drainage cavity and an oil drainage port arranged in the main valve hole through oil ducts.
The top surface of the front valve body is provided with a high-pressure oil inlet and a low-pressure oil inlet, the high-pressure oil inlet is communicated with the high-pressure cavity through an oil duct, and the low-pressure oil inlet is communicated with the low-pressure cavity on the right side of the control piston through an oil duct.
The top surface of back valve body is equipped with the draining port, the draining port passes through oil duct and draining chamber intercommunication, form the spring chamber between case and the supporting seat, the spring chamber passes through oil duct and draining port intercommunication, case middle part and the spacing step in main valve hole form the closed chamber, the closed chamber passes through oil duct and low pressure chamber intercommunication.
And a plurality of pressure equalizing grooves are uniformly arranged on the outer circumferential surfaces of the control piston, the push rod and the valve core.
The highest working pressure of the high-pressure oil inlet and the low-pressure oil inlet is 40MPa, and the output pressure difference range of the pressure measuring oil port is 0.5-35 MPa.
Compared with the prior art, the invention has the beneficial effects that:
1. according to the invention, through a mechanical force transmission structure, by utilizing mechanical force self-balance and constant flow principles and matching the area relationship between transmission parts, the oil inlet pressure difference between the high-pressure oil inlet and the low-pressure oil inlet is directly output to the pressure measuring cavity, so that the purpose of directly outputting the pressure difference is achieved, and the stability and reliability of pressure output are ensured.
2. According to the invention, the constant flow valve is added on the oil way for the high-pressure oil to enter the pressure measuring cavity, so that the constant flow of the pressure measuring cavity can be realized when the normal pressure difference is output, and the pressure fluctuation in the pressure measuring cavity and the uncertainty of the output pressure difference caused by the pressure change of the system are prevented.
3. According to the invention, the safety valve is arranged on the upper part of the pressure measuring cavity, and when the pressure of the pressure measuring cavity exceeds the set pressure of the safety valve, the safety valve is opened to play a role in protecting an external instrument.
4. The control piston, the push rod, the valve core and other movable parts of the hydraulic clamping device adopt clearance sealing, and the matching auxiliary excircle is provided with a pressure equalizing groove, so that the hydraulic clamping force is reduced.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic cross-sectional view taken along line A-A of FIG. 1;
FIG. 3 is a left side view of FIG. 1;
FIG. 4 is a schematic structural view of the valve cartridge of the present invention;
FIG. 5 is a schematic diagram of the principles of the present invention;
in the figure: 1-front valve body, 2-rear valve body, 3-control piston, 4-push rod, 5-support seat, 6-reset spring, 7-valve core, 8-constant flow valve, 9-pressure measuring joint, 10-safety valve and 11-plug;
the device comprises an a-high pressure cavity, a b-low pressure cavity, a c-spring cavity, a d-closed cavity, an e-oil release cavity, an f-pressure measuring cavity, a PH-high pressure oil inlet, a PL-low pressure oil inlet, an L-oil release port and an M-pressure measuring oil port;
wherein: 7.1-equalizing groove.
Detailed Description
The invention is further illustrated by the following figures and examples.
As shown in fig. 1 to 4, the differential pressure output valve in the present embodiment includes a front valve body 1, a rear valve body 2, a control piston 3, a push rod 4, a support seat 5, a return spring 6, a valve core 7, a constant flow valve 8, a pressure measuring joint 9, and a safety valve 10;
a piston hole is transversely formed in the middle of the front valve body 1, the control piston 3 is arranged in the piston hole, the supporting seat 5 is arranged in a supporting hole formed in the right end of the piston hole of the front valve body 1, the push rod 4 is arranged in a push rod hole formed in the center of the supporting seat 5, and the left end of the push rod is in contact with the control piston 3;
a step main valve hole is transversely arranged in the middle of the rear valve body 2, the large cylindrical ends of the reset spring 6 and the valve core 7 are arranged in the large cylindrical hole of the step main valve hole, the reset spring 6 is positioned at the left end of the valve core 7, the right side surface of the front valve body 1 is connected with the left side surface of the rear valve body 2, the right end of the push rod 4 is contacted with the left end of the valve core 7, and a plurality of pressure equalizing grooves 7.1 are uniformly arranged on the outer circumferential surfaces of the control piston 3, the push rod 4 and the valve core 7;
the constant flow valve 8 is arranged on the lower portion of the right end of the rear valve body 2, the constant flow valve 8 is respectively communicated with a high-pressure cavity a on the left side of the control piston 3 and a pressure measuring cavity f on the right end of the valve core 7 through oil ducts, a pressure measuring oil port M is arranged in the middle of the right end face of the rear valve body 2, the pressure measuring joint 9 is arranged on the pressure measuring oil port M, the pressure measuring oil port M is communicated with the pressure measuring cavity f through the oil ducts, the safety valve 10 is arranged on the right of the top face of the rear valve body 2, the lower end of the safety valve 10 is communicated with the pressure measuring cavity f through the oil ducts, and an oil drainage port arranged on the lower portion of the safety valve. The output pressure difference of the pressure measuring oil port M is 10MPa, and the pressure difference between the high-pressure cavity a and the low-pressure cavity b is 10 MPa.
The top surface of the front valve body 1 is provided with a high-pressure oil inlet PH and a low-pressure oil inlet PL, the high-pressure oil inlet PH is communicated with the high-pressure cavity a through an oil duct, and the low-pressure oil inlet PL is communicated with the low-pressure cavity b on the right side of the control piston 3 through an oil duct.
The top surface of the rear valve body 2 is provided with an oil drainage port L, the oil drainage port L is communicated with an oil drainage cavity e through an oil duct, a spring cavity c is formed between the valve core 7 and the supporting seat 5, the spring cavity c is communicated with the oil drainage port L through the oil duct, the middle part of the valve core 7 and a main valve hole limiting step form a closed cavity d, and the closed cavity d is communicated with the low-pressure cavity b through the oil duct.
The highest working pressure of the high-pressure oil inlet PH and the low-pressure oil port PL is 40MPa, and the output pressure difference range of the pressure measuring oil port M is 0.5-35 MPa.
The working principle of the invention is as follows:
when the high-pressure oil inlet PH inserts the high-pressure end of system's oil circuit, fluid gets into high-pressure chamber a and acts on the left end of control piston 3, promotes push rod 4 and acts on the left end face of case 7, and fluid passes through oil duct and constant flow valve 8 simultaneously and gets into pressure measurement chamber f, acts on the right-hand member face of case 7. When the low-pressure oil inlet PL is connected to the low-pressure end of the oil circuit of the system, oil enters the low-pressure cavity b and acts on the right end of the control piston 3 and the left end of the push rod 4, and simultaneously the oil enters the closed cavity d through the oil duct and acts on the right annular surface of the large cylindrical end of the valve core 7. At the moment, because the left end acting force of the push rod 4 is equal to the large cylindrical end annular surface acting force of the valve element 7, the valve element 7 moves leftwards to push the push rod 4 to enable the control piston 3 to move leftwards, the valve element 7 is opened from closing to opening, the pressure measuring cavity f is communicated with the oil drainage cavity e, liquid oil in the oil drainage cavity e leaks from the oil drainage port L due to the pressure action, the pressure in the pressure measuring cavity f is reduced, when the pressure in the pressure measuring cavity f is reduced to enable the valve element 7 to reach a self-balancing state under the action of various acting forces, the oil drainage port L does not leak oil, the pressure of an oil port of the pressure measuring cavity M is the pressure difference between the high pressure end and the low pressure end of an oil path of the hydraulic system at the moment, the purpose of outputting the.
When the valve core 7 is in a self-balancing state, after the pressure difference output from the pressure measuring oil port M is measured by using the pressure measuring joint 9, the system oil paths of the high-pressure oil inlet PH and the low-pressure oil inlet PL are disconnected, at the moment, the oil pressure in the pressure difference output valve is zero, and because the return spring 6 is in a compression state, the valve core 7 moves rightwards under the restoring force of the return spring 6 and is restored to an initial state.
When the pressure of the pressure measuring cavity f exceeds the set pressure of the safety valve 10, the safety valve 10 is opened to release the pressure, and the external instrument is protected.
Under the condition that the high-pressure end and the low-pressure end of the system oil way are connected with the high-pressure oil inlet PH and the low-pressure oil inlet PL in a wrong mode respectively, the pressure output measurement result of the pressure measuring oil port M is zero, and accordingly the flow direction of the oil liquid in the system oil way can be judged.
Claims (5)
1. A differential pressure output valve, characterized by: the automatic control valve comprises a front valve body (1), a rear valve body (2), a control piston (3), a push rod (4), a support seat (5), a return spring (6), a valve core (7), a constant flow valve (8), a pressure measuring joint (9) and a safety valve (10);
a piston hole is transversely formed in the middle of the front valve body (1), the control piston (3) is arranged in the piston hole, the supporting seat (5) is arranged in a supporting hole formed in the right end of the piston hole of the front valve body (1), the push rod (4) is arranged in a push rod hole formed in the center of the supporting seat (5), and the left end of the push rod is contacted with the control piston (3);
a stepped main valve hole is transversely formed in the middle of the rear valve body (2), the large cylindrical end of the reset spring (6) and the valve core (7) are arranged in the large cylindrical hole of the stepped main valve hole, the reset spring (6) is positioned at the left end of the valve core (7), the small cylindrical end of the valve core (7) is arranged in the small cylindrical hole of the stepped main valve hole, the right side surface of the front valve body (1) is connected with the left side surface of the rear valve body (2), and the right end of the push rod (4) is contacted with the left end of the valve core (7);
the constant flow valve (8) is arranged at the lower part of the right end of the rear valve body (2), and the constant flow valve (8) is respectively communicated with a high-pressure cavity (a) on the left side of the control piston (3) and a pressure measuring cavity (f) at the right end of the valve core (7) through oil ducts; the hydraulic pressure measuring valve is characterized in that a pressure measuring oil port (M) is arranged in the middle of the right end face of the rear valve body (2), a pressure measuring joint (9) is arranged on the pressure measuring oil port (M), the pressure measuring oil port (M) is communicated with a pressure measuring cavity (f) through an oil duct, the safety valve (10) is arranged on the right of the top face of the rear valve body (2), the lower end of the safety valve (10) is communicated with the pressure measuring cavity (f) through the oil duct, and an oil drainage port arranged on the lower portion of the safety valve (10) is communicated with an oil drainage cavity (e) and an oil drainage port (L) arranged in a.
2. A differential pressure output valve as claimed in claim 1, wherein: the top surface of the front valve body (1) is provided with a high-pressure oil inlet (PH) and a low-pressure oil inlet (PL), the high-pressure oil inlet (PH) is communicated with the high-pressure cavity (a) through an oil duct, and the low-pressure oil inlet (PL) is communicated with the low-pressure cavity (b) on the right side of the control piston (3) through an oil duct.
3. A differential pressure output valve as claimed in claim 1, wherein: the top surface of back valve body (2) is equipped with draining port (L), draining port (L) passes through the oil duct and lets out oil pocket (e) intercommunication, form spring chamber (c) between case (7) and supporting seat (5), spring chamber (c) pass through the oil duct and let out oil pocket (L) intercommunication, case (7) middle part and the spacing step in main valve hole form closed chamber (d), closed chamber (d) pass through the oil duct and communicate with low pressure chamber (b).
4. A differential pressure output valve as claimed in claim 1, wherein: a plurality of pressure equalizing grooves (7.1) are uniformly arranged on the outer circumferential surfaces of the control piston (3), the push rod (4) and the valve core (7).
5. A differential pressure output valve according to any of claims 1-3, wherein: the working pressure of the high-pressure cavity (a) and the pressure measuring cavity (f) is less than 40MPa, and the output pressure difference of the pressure measuring oil port (M) is 0.5-35 MPa.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011362737.XA CN112524112B (en) | 2020-11-27 | 2020-11-27 | Differential pressure output valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011362737.XA CN112524112B (en) | 2020-11-27 | 2020-11-27 | Differential pressure output valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112524112A true CN112524112A (en) | 2021-03-19 |
| CN112524112B CN112524112B (en) | 2023-02-03 |
Family
ID=74994621
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011362737.XA Active CN112524112B (en) | 2020-11-27 | 2020-11-27 | Differential pressure output valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112524112B (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1205768A (en) * | 1995-12-20 | 1999-01-20 | 陶氏化学公司 | System for measuring differential pressure, flow, and level |
| US20020069916A1 (en) * | 2000-12-08 | 2002-06-13 | Ferguson Alan L. | Method and apparatus for determining a valve status |
| CN101598229A (en) * | 2009-07-17 | 2009-12-09 | 陈银宝 | A kind of pressure difference-powered liquid level automatic control valve |
| US20130086899A1 (en) * | 2011-10-05 | 2013-04-11 | Caterpillar Inc. | Hydraulic system with bi-directional regeneration |
| CN103234691A (en) * | 2013-04-24 | 2013-08-07 | 北京农业智能装备技术研究中心 | Greenhouse plant leaf air saturation vapor pressure deficit measuring device and measuring method |
| CN103674410A (en) * | 2012-09-26 | 2014-03-26 | 中国科学院光电研究院 | Differential pressure measuring device and method |
| CN107035738A (en) * | 2017-05-27 | 2017-08-11 | 太重集团榆次液压工业有限公司 | A kind of rotating multi-channel valve with pressurize protecting against shock |
| CN109237056A (en) * | 2018-10-25 | 2019-01-18 | 太重集团榆次液压工业有限公司 | A kind of plug-in precompression valve |
| CN209115429U (en) * | 2018-11-02 | 2019-07-16 | 太重榆次液压工业（上海）有限公司 | A kind of novel hydraulic valve stand |
-
2020
- 2020-11-27 CN CN202011362737.XA patent/CN112524112B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1205768A (en) * | 1995-12-20 | 1999-01-20 | 陶氏化学公司 | System for measuring differential pressure, flow, and level |
| US20020069916A1 (en) * | 2000-12-08 | 2002-06-13 | Ferguson Alan L. | Method and apparatus for determining a valve status |
| CN101598229A (en) * | 2009-07-17 | 2009-12-09 | 陈银宝 | A kind of pressure difference-powered liquid level automatic control valve |
| US20130086899A1 (en) * | 2011-10-05 | 2013-04-11 | Caterpillar Inc. | Hydraulic system with bi-directional regeneration |
| CN103674410A (en) * | 2012-09-26 | 2014-03-26 | 中国科学院光电研究院 | Differential pressure measuring device and method |
| CN103234691A (en) * | 2013-04-24 | 2013-08-07 | 北京农业智能装备技术研究中心 | Greenhouse plant leaf air saturation vapor pressure deficit measuring device and measuring method |
| CN107035738A (en) * | 2017-05-27 | 2017-08-11 | 太重集团榆次液压工业有限公司 | A kind of rotating multi-channel valve with pressurize protecting against shock |
| CN109237056A (en) * | 2018-10-25 | 2019-01-18 | 太重集团榆次液压工业有限公司 | A kind of plug-in precompression valve |
| CN209115429U (en) * | 2018-11-02 | 2019-07-16 | 太重榆次液压工业（上海）有限公司 | A kind of novel hydraulic valve stand |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112524112B (en) | 2023-02-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US3626474A (en) | Pressure indicator and bypass pressure relief valve | |
| CN101520102A (en) | Relive valve | |
| US4353392A (en) | Safety valve assembly | |
| CN112524112B (en) | Differential pressure output valve | |
| US4471797A (en) | Hydraulic circuit breaker reset device | |
| US20240068895A1 (en) | Differential pressure sensor for determining the differential pressure between two pressures | |
| CN111894924A (en) | Manual-automatic integrated control high-water-base high-pressure large-flow digital proportional direction valve | |
| CN204878106U (en) | Large -traffic efflux tubular electricity feedback servovalve | |
| US4453411A (en) | Pressure memory device | |
| CN112360842B (en) | Underwater constant-pressure hydraulic lock, oil cylinder applying same and locking method | |
| EP0310036B1 (en) | Proportioning control valve for use with antilock device | |
| CN213206147U (en) | Accumulator charging valve | |
| CN112160951B (en) | Test system of hydraulic valve | |
| CN113898619A (en) | Accumulator charging valve and hydraulic braking system | |
| US4673220A (en) | Brake pressure control valve assembly having a bypass function | |
| CN215172714U (en) | Automatic pressure supplementing structure of low-pressure cavity | |
| CN212225648U (en) | Valve group with pressure measuring connector | |
| CN117366054A (en) | Hydraulic load sensitive multi-way valve test system | |
| CN218407982U (en) | Externally-mounted speed limiting valve | |
| CN216200813U (en) | Modal conversion valve used in airplane front wheel control and shimmy damping system | |
| CN108916147A (en) | A kind of check valve of carry potential overflow function | |
| CN114013417B (en) | Constant-proportion pressure distribution valve with variable width of pressure equalizing groove | |
| CN218377164U (en) | Shock-resistant pilot operated safety valve | |
| CN212536289U (en) | Hydraulic valve with good sealing performance | |
| CN217652989U (en) | Differential hydraulic cylinder with bidirectional balance valve |
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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |