CN111577691A - Low-pulsation flow control valve based on post-valve energy storage compensation - Google Patents
Low-pulsation flow control valve based on post-valve energy storage compensation Download PDFInfo
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- CN111577691A CN111577691A CN202010313197.XA CN202010313197A CN111577691A CN 111577691 A CN111577691 A CN 111577691A CN 202010313197 A CN202010313197 A CN 202010313197A CN 111577691 A CN111577691 A CN 111577691A
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- flow passage
- balance
- runner
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- piston
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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
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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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
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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
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/20—Excess-flow valves
- F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
- F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
- F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
- F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
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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
- F16K47/00—Means in valves for absorbing fluid energy
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Safety Valves (AREA)
Abstract
The invention relates to a low-pulsation flow control valve based on post-valve energy storage compensation, which comprises a valve body, a valve core, an oil source flow passage, a load flow passage and an oil tank flow passage, wherein the oil source flow passage, the load flow passage and the oil tank flow passage are arranged in the valve body, an oil return flow passage and a balance flow passage are also arranged between the load flow passage and the oil tank flow passage in the valve body, the oil return flow passage is communicated with the oil tank flow passage, the balance flow passage is communicated with the load flow passage, a balance through hole which is communicated with the oil return flow passage is also arranged in the balance through hole, a balance piston capable of moving back and forth along the balance through hole is also arranged in the balance through hole, one end with a larger cross section area of the balance piston is arranged in the balance flow passage, one end with a smaller. Compared with the prior art, the invention can obviously reduce the secondary flow pressure pulsation phenomenon of the hydraulic valve caused by cavitation and surge of the valve port notch.
Description
Technical Field
The invention belongs to the technical field of fluid control, and relates to a low-pulsation flow control valve based on post-valve energy storage compensation.
Background
The hydraulic slide valve structure is a basic structure form of a hydraulic valve, and has a full-circumference opening and a non-full-circumference opening, the valve can be functionally formed into a reversing valve, a direction throttle valve, a flow control valve and the like, and the operation control modes include manual operation, proportion, servo and the like. The slide valve flow channel has a complex structure, small size and high flow speed, so that complex flow field pressure distribution is formed, and finally cavitation is often caused. The existence of cavitation not only causes certain flow field pressure loss, but also is coupled with the system flow to form a cavitation surge phenomenon, so that the system flow after the valve is periodically pulsed. The flow pulsation has the characteristics of high frequency and low amplitude, and is closely related to the pressure distribution and the structure of the notch. The hydraulic radius of the U-shaped throttling notch is large, the anti-blocking performance is good, and the adjustable range is wide. The hydraulic slide valve has the problems that the structure of an internal flow channel of the hydraulic slide valve is complex, when oil flows through a notch, the flow velocity is increased rapidly, the local pressure in the liquid is reduced, cavitation is generated, the two-phase mass is interactively coupled with the pressure flow pulsation of the flow channel in the cavitation process, the cavitation surge phenomenon is formed, the flow pressure pulsation behind the valve is caused, and the stable operation of an actuator is influenced.
Chinese patent CN201920176330.4 discloses a low-noise anti-cavitation structure regulating valve, which prevents the generation of cavitation phenomenon by multi-stage pressure reduction and noise reduction, and reduces the noise generated when the medium flows through; chinese patent CN200920011129.7 discloses an anti-cavitation high pressure difference control valve, which can realize different pressure reduction stages, and solve the working conditions of different pressures and pressure differences; chinese patent ZL201320793666.8 discloses an anti-cavitation high-temperature high-pressure four-stage pressure reducing valve, which can ensure stable operation in high-temperature environment. However, in the above valves, the problem of pressure flow pulsation caused by valve port cavitation surge is not considered, and therefore, it is necessary to design a device capable of solving the problem of pressure flow pulsation caused by valve port cavitation surge.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a low-pulsation flow control valve based on post-valve energy storage compensation.
The purpose of the invention can be realized by the following technical scheme:
the utility model provides a low pulsation flow control valve based on energy storage compensation behind valve, includes valve body, case to and arrange oil source runner, load runner and the oil tank runner in the valve body, oil return runner and balanced runner have still been arranged between inherent load runner of valve body and the oil tank runner, wherein, oil return runner intercommunication the oil tank runner, balanced runner and load runner intercommunication, the balanced through-hole of mutual intercommunication between oil return runner and the balanced runner still is provided with the balanced piston that can follow its round trip movement in the balanced through-hole, and this balanced piston sectional area is great one end is arranged in the balanced runner, and the one end that the sectional area is less then is arranged in the oil return runner, still is equipped with the elastic component on the great one end of the sectional area of balanced piston and balanced runner between the tip that is close to the balanced through-hole.
Furthermore, a lateral flow passage is further arranged on the valve core, wherein one end of the lateral flow passage is communicated with the load flow passage, and the other end of the lateral flow passage is communicated with an area between the end part of the balance piston and the bottom end of the balance flow passage in the balance flow passage. The lateral flow passages are provided to reduce the pressure at the large end of the balance piston, so that the elastic member only needs to provide a small force to enable the balance piston to reach a balanced state.
Further, the resilient member has a pre-compression amount when the load flow path is at a rated pressure.
Further, the elastic member is a spring.
Furthermore, the oil return flow passage and the balance flow passage are separated by a boss, and the boss is provided with the balance through hole.
Furthermore, the balance piston is composed of a piston rod and a piston plate which are connected into a whole, wherein the piston rod penetrates through the balance through hole and is arranged in the oil return flow channel, the piston plate is positioned in the balance flow channel, and the elastic part is arranged between the piston plate and the bottom of the balance flow channel.
Furthermore, the diameter of the piston rod is smaller than the aperture of the balance through hole.
Furthermore, a convex shoulder is arranged on the valve core, and U-shaped throttling notches are arranged at two ends of the convex shoulder.
Furthermore, the middle position of the shoulder is also provided with an annular pressure equalizing groove.
The pressure on one end with larger sectional area of the balance piston depends on the load flow channel, and the pressure on the other end depends on the pressure of the return oil flow channel, the elastic force of the elastic piece and the pressure of the lateral flow channel which can be optimally designed. When the load flow passage pressure is at the rated pressure, the elastic element has a certain pre-compression amount. When the pressure is less than the rated pressure, i.e., the flow rate becomes small, the compression amount of the elastic member also becomes small to compensate for the flow rate. On the contrary, when the pressure is higher than the rated pressure, the compression amount of the elastic part is increased to compensate the flow.
The working principle of the hydraulic proportional valve is that a command signal is subjected to power amplification through a proportional amplifier, current is proportionally output to a proportional electromagnet of the proportional valve, the proportional electromagnet outputs force and proportionally moves the position of a valve core, the flow of liquid flow can be proportionally controlled, the direction of the liquid flow can be changed, and therefore position or speed control over an actuating mechanism is achieved. According to the invention, researches show that cavitation is formed in the throttling opening because the liquid flow at the throttling opening has high flow velocity and forms local low pressure, and when the pressure is lower than the saturated vapor pressure at the corresponding temperature, the cavitation phenomenon can occur. When the pressure is lower than the outlet pressure, the fluid can be caused to flow backwards, namely, the surging phenomenon can occur at the throttling opening, and the problem of pressure flow pulsation of the actuator behind the valve is further caused. When the pressure at the throttling opening is reduced, the balance piston absorbs a certain flow from the oil return flow passage under the action of the pressure to supplement the flow to the throttling opening, so that the cavitation surge phenomenon at the throttling opening is prevented, and the flow pulsation is inhibited. When the pressure at the throttle is increased, the balance piston of the invention can transmit the redundant flow into the oil return flow channel under the pressure action. When the pressure at the throttle returns to normal, the balance piston returns to the original position under the action of the pressures at the two ends.
Compared with the prior art, the invention can effectively inhibit cavitation at the throttling port in the valve and throttling cavitation surge of the notch of the sliding valve caused by the phenomenon of flow backflow, and reduce the problem of flow pulsation by arranging the energy storage compensation device consisting of the balance piston, the elastic piece and the like, and has the advantages of simple structure, safety, reliability and easy maintenance and replacement.
Drawings
FIG. 1 is a schematic structural view of the present invention;
the notation in the figure is:
1-valve core, 2-valve body, 3-oil tank flow channel, 4-driving device, 5-oil source flow channel, 6-load flow channel, 7-throttling notch, 8-shoulder, 9-lateral flow channel, 10-balance piston, 11-elastic part, 12-boss, 13-oil return flow channel, 14-balance through hole, 15-pressure equalizing groove and 16-balance flow channel.
Detailed Description
The invention is described in detail below with reference to the figures and specific embodiments. The present embodiment is implemented on the premise of the technical solution of the present invention, and a detailed implementation manner and a specific operation process are given, but the scope of the present invention is not limited to the following embodiments.
The invention provides a low-pulsation flow control valve based on post-valve energy storage compensation, which has a structure shown in figure 1 and comprises a valve body 2 and a valve core 1, and an oil source flow passage 5, a load flow passage 6 and a tank flow passage 3 arranged in the valve body 2, an oil return flow passage 13 and a balance flow passage 16 are further arranged between the load flow passage 6 and the tank flow passage 3 in the valve body 2, wherein the oil return flow passage 13 is communicated with the oil tank flow passage 3, the balance flow passage 16 is communicated with the load flow passage 6, a balance through hole 14 communicated with the oil return flow passage 13 and the balance flow passage 16, a balance piston 10 capable of moving back and forth along the balance through hole 14, the end with larger sectional area of the balance piston 10 is arranged in the balance flow passage 16, the end with smaller sectional area is arranged in the oil return flow passage 13, an elastic member 11 is further provided between the end of the balance piston 10 having a larger cross-sectional area and the end of the balance flow passage 16 near the balance through-hole 14.
In a specific embodiment of the present invention, the valve core 1 is further provided with a lateral flow passage 9, wherein one end of the lateral flow passage 9 communicates with the load flow passage 6, and the other end communicates with a region between the end of the balance piston 10 and the bottom end of the balance flow passage 16 in the balance flow passage 16. The effect of the lateral flow channels 9 is to reduce the pressure at the large end of the balancing piston 10, so that the resilient element 11 only needs to provide a small force to bring the balancing piston 10 to a balanced state.
In a specific embodiment of the present invention, the elastic member 11 has a pre-compression amount when the load flow passage 6 is at a rated pressure.
In a specific embodiment of the present invention, the elastic member 11 is a spring.
In a specific embodiment of the present invention, the oil return flow passage 13 and the balance flow passage 16 are separated by a boss 12, and the boss 12 is provided with the balance through hole 14.
In a specific embodiment of the present invention, the balance piston 10 is composed of a piston rod and a piston plate connected into a whole, wherein the piston rod passes through the balance through hole 14 and is disposed in the oil return flow channel 13, the piston plate is disposed in the balance flow channel 16, and the elastic member 11 is disposed between the piston plate and the bottom of the balance flow channel 16.
In a more specific embodiment, the diameter of the piston rod is smaller than the diameter of the balance through hole 14.
In a specific embodiment of the present invention, the valve core 1 is further provided with a shoulder 8, and the two ends of the shoulder 8 are further provided with U-shaped throttling notches 7.
In a more specific embodiment, the shoulder 8 is further provided with a pressure equalizing groove 15 in the shape of a ring at a middle position.
The above embodiments may be implemented individually, or in any combination of two or more.
Example 1:
referring to fig. 1, the present embodiment provides a low pulsation flow control valve based on post-valve energy storage compensation, including a valve body 2, a valve core 1, and an oil source flow channel 5, a load flow channel 6, an oil tank flow channel 3, an oil return flow channel 13, and a balance flow channel 16 arranged in the valve body 2, wherein the load flow channel 6, the oil tank flow channel 3, the oil return flow channel 13, and the balance flow channel 16 are symmetrically arranged with the oil source flow channel 5 as a center, the two oil tank flow channels 3 are communicated with each other, wherein the oil return flow channel 13 is communicated with the oil tank flow channel 3, the balance flow channel 16 is communicated with the load flow channel 6, a balance through hole 14 communicated with each other between the oil return flow channel 13 and the balance flow channel 16 is further provided with a balance piston 10 capable of moving back and forth along the balance through hole 14, the end with a larger cross-sectional area of the balance piston 10, an elastic member 11 is further provided between the end of the balance piston 10 having a larger cross-sectional area and the end of the balance flow passage 16 near the balance through-hole 14 (i.e., a side surface of the boss 12).
Referring to fig. 1 again, the valve core 1 is further provided with a lateral flow passage 9, wherein one end of the lateral flow passage 9 is communicated with the load flow passage 6, and the other end is communicated with an area between the end of the balance piston 10 and the bottom end of the balance flow passage 16 in the balance flow passage 16. The effect of the lateral flow channels 9 is to reduce the pressure at the large end of the balancing piston 10, so that the resilient element 11 only needs to provide a small force to bring the balancing piston 10 to a balanced state.
Referring to fig. 1 again, the oil return flow passage 13 and the balance flow passage 16 are separated by a boss 12, and a balance through hole 14 is formed in the boss 12. The balance piston 10 is composed of a piston rod and a piston plate which are connected into a whole, wherein the piston rod passes through the balance through hole 14 and is arranged in the oil return flow passage 13, the piston plate is positioned in the balance flow passage 16, and an elastic part 11 is arranged between the piston plate and the bottom of the balance flow passage 16. The diameter of the piston rod is smaller than the diameter of the balance through hole 14.
Referring to fig. 1 again, the valve core 1 is further provided with a shoulder 8, two ends of the shoulder 8 are further provided with U-shaped throttling notches 7, the shoulder 8 and the throttling notches 7 are arranged to be matched with the movement of the valve core 1 in the valve body 2, so that the valve core 1 can separate and conduct two adjacent channels (such as an oil source channel 5 and a load channel 6, and the load channel 6 and a tank channel 3) in the valve body 2, and the valve core 1 is further connected with an external driving device 4. The middle position of the shoulder 8 is also provided with an annular pressure equalizing groove 15. The elastic member 11 used in this embodiment is a spring.
The device of the embodiment controls the balance piston 10 to move by the pressure at the two ends of the balance piston 10, further controls the flow pulsation, solves the throttling cavitation surge and realizes the low pulsation flow control. One end of the balance piston 10 is connected with the load flow passage 6, and the other end is connected with the oil return flow passage 13. The pressure at one end of the balance piston 10 is given by the load flow passage 6, and the pressure at the other end is the sum of the pressure of the return flow passage 13, the spring force and the compensation pressure of the lateral flow passage 9. When the load flow channel 6 is at the nominal pressure, the spring has a certain pre-compression. When pressure is less than rated pressure, the flow can diminish, and balanced piston 10 left side pressure sum can be greater than right side pressure, and the compressive capacity of spring can diminish, and at this moment, balanced piston 10 can move to being close to load runner 6 direction under the left side pressure effect, and simultaneously, fluid can be followed oil return runner 13 and compensated load runner 6 under the left side pressure effect. When the pressure is higher than the rated pressure, the flow rate will be increased, the sum of the pressures on the left side of the balance piston 10 will be smaller than the pressure on the right side, the compression amount of the spring will be increased, at this time, the balance piston 10 will move towards the direction close to the boss 12 under the action of the pressure on the right side, and the oil will enter the oil return flow passage 13 from the load flow passage 6 under the action of the pressure on the right side to compensate the load flow passage 6.
In the flow control valve of the invention, the maximum moving distance of the balance piston 10 depends on the distance between the boss 12 and the oil return flow passage 13, and the capacity of adjusting the flow depends on the sectional area of the large end of the balance piston 10 and the expansion and contraction frequency of the spring.
The embodiments described above are described to facilitate an understanding and use of the invention by those skilled in the art. It will be readily apparent to those skilled in the art that various modifications to these embodiments may be made, and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present invention is not limited to the above embodiments, and those skilled in the art should make improvements and modifications within the scope of the present invention based on the disclosure of the present invention.
Claims (10)
1. The utility model provides a low pulsation flow control valve based on energy storage compensation behind valve, includes valve body, case to and arrange oil source runner, load runner and the oil tank runner in the valve body, its characterized in that, still arranged oil return runner and balanced runner between inherent load runner of valve body and the oil tank runner, wherein, oil return runner intercommunication the oil tank runner, balanced runner and load runner intercommunication, the balanced through-hole of mutual intercommunication between oil return runner and the balanced runner still is provided with the balanced piston that can follow its round trip movement in the balanced through-hole, and in the balanced runner was arranged in to the great one end of this balanced piston sectional area, the one end that the sectional area is less then arranged in the oil return runner, still was equipped with the elastic component between the tip that is close to balanced through-hole on the great one end of sectional area of balanced piston and the balanced runner.
2. The low-pulsation flow control valve based on post-valve energy storage compensation according to claim 1, wherein a lateral flow passage is further arranged on the valve core, wherein one end of the lateral flow passage is communicated with the load flow passage, and the other end of the lateral flow passage is communicated with an area between the end of the balance piston and the bottom end of the balance flow passage in the balance flow passage.
3. The low pulsation flow control valve based on post valve energy storage compensation according to claim 1, wherein the elastic member has a pre-compression amount when the load flow passage is at a rated pressure.
4. The low pulsation flow control valve based on post valve energy storage compensation according to claim 1, wherein the elastic member is a spring.
5. The low-pulsation flow control valve based on post-valve energy storage compensation according to claim 1, wherein the oil return flow passage and the balance flow passage are separated by a boss, and the balance through hole is formed in the boss.
6. The low-pulsation flow control valve based on post-valve energy storage compensation according to claim 1, wherein the balance piston is composed of a piston rod and a piston plate which are connected into a whole, wherein the piston rod passes through the balance through hole and is arranged in the oil return flow passage, the piston plate is arranged in the balance flow passage, and the elastic element is arranged between the piston plate and the bottom of the balance flow passage.
7. The low-pulsation flow control valve based on post-valve energy storage compensation of claim 6, wherein the diameter of the piston rod is smaller than the diameter of the balance through hole.
8. The low-pulsation flow control valve based on post-valve energy storage compensation according to claim 1, wherein a shoulder is further arranged on the valve core, and a U-shaped throttling notch is further arranged at two ends of the shoulder.
9. The low-pulsation flow control valve based on post-valve energy storage compensation according to claim 8, wherein a pressure equalizing groove is further formed in the middle of the shoulder.
10. The low pulsation flow control valve based on post valve energy storage compensation according to claim 9, wherein the pressure equalizing groove is annular.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010313197.XA CN111577691B (en) | 2020-04-20 | 2020-04-20 | Low-pulsation flow control valve based on post-valve energy storage compensation |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010313197.XA CN111577691B (en) | 2020-04-20 | 2020-04-20 | Low-pulsation flow control valve based on post-valve energy storage compensation |
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| CN111577691A true CN111577691A (en) | 2020-08-25 |
| CN111577691B CN111577691B (en) | 2022-04-05 |
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| CN202010313197.XA Active CN111577691B (en) | 2020-04-20 | 2020-04-20 | Low-pulsation flow control valve based on post-valve energy storage compensation |
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Citations (11)
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|---|---|---|---|---|
| US3623509A (en) * | 1968-12-12 | 1971-11-30 | Bosch Gmbh Robert | Check valve controlling hydraulic apparatus |
| JPS5697682A (en) * | 1979-12-29 | 1981-08-06 | Kayaba Ind Co Ltd | Damping device for spool valve |
| CN1603582A (en) * | 2004-11-12 | 2005-04-06 | 宁波华液机器制造有限公司 | Hydraulic variable valve control system |
| CN201187613Y (en) * | 2008-03-11 | 2009-01-28 | 浙江大学 | Mechanical proportional balance valve for oil tank liquid level automatic control |
| CN101943187A (en) * | 2009-07-10 | 2011-01-12 | 上海立新液压有限公司 | One-way balancing valve with brake unlocking port |
| CN102705289A (en) * | 2012-06-21 | 2012-10-03 | 唐香平 | Energy recovery balance valve |
| CN103089737A (en) * | 2013-01-31 | 2013-05-08 | 杨洁 | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation |
| CN203570734U (en) * | 2013-11-26 | 2014-04-30 | 中联重科股份有限公司渭南分公司 | Balance valve, hydraulic cylinder stretching control loop and hydraulic equipment |
| CN107709749A (en) * | 2015-06-25 | 2018-02-16 | 日立汽车系统株式会社 | Flow control valve and high-pressure fuel feed pump |
| CN108591158A (en) * | 2018-07-11 | 2018-09-28 | 中国船舶重工集团公司第七0四研究所 | A kind of high-pressure high-flow two-position four-way pilot operated directional control valve |
| CN210290320U (en) * | 2019-07-18 | 2020-04-10 | 宁波程锐液压科技有限公司 | Reversing valve body of load sensing valve |
-
2020
- 2020-04-20 CN CN202010313197.XA patent/CN111577691B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3623509A (en) * | 1968-12-12 | 1971-11-30 | Bosch Gmbh Robert | Check valve controlling hydraulic apparatus |
| JPS5697682A (en) * | 1979-12-29 | 1981-08-06 | Kayaba Ind Co Ltd | Damping device for spool valve |
| CN1603582A (en) * | 2004-11-12 | 2005-04-06 | 宁波华液机器制造有限公司 | Hydraulic variable valve control system |
| CN201187613Y (en) * | 2008-03-11 | 2009-01-28 | 浙江大学 | Mechanical proportional balance valve for oil tank liquid level automatic control |
| CN101943187A (en) * | 2009-07-10 | 2011-01-12 | 上海立新液压有限公司 | One-way balancing valve with brake unlocking port |
| CN102705289A (en) * | 2012-06-21 | 2012-10-03 | 唐香平 | Energy recovery balance valve |
| CN103089737A (en) * | 2013-01-31 | 2013-05-08 | 杨洁 | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation |
| CN203570734U (en) * | 2013-11-26 | 2014-04-30 | 中联重科股份有限公司渭南分公司 | Balance valve, hydraulic cylinder stretching control loop and hydraulic equipment |
| CN107709749A (en) * | 2015-06-25 | 2018-02-16 | 日立汽车系统株式会社 | Flow control valve and high-pressure fuel feed pump |
| CN108591158A (en) * | 2018-07-11 | 2018-09-28 | 中国船舶重工集团公司第七0四研究所 | A kind of high-pressure high-flow two-position four-way pilot operated directional control valve |
| CN210290320U (en) * | 2019-07-18 | 2020-04-10 | 宁波程锐液压科技有限公司 | Reversing valve body of load sensing valve |
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| Publication number | Publication date |
|---|---|
| CN111577691B (en) | 2022-04-05 |
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