CN113833708B - Multi-way valve with inlet and outlet pressure difference detection function - Google Patents
Multi-way valve with inlet and outlet pressure difference detection function Download PDFInfo
- Publication number
- CN113833708B CN113833708B CN202111153317.5A CN202111153317A CN113833708B CN 113833708 B CN113833708 B CN 113833708B CN 202111153317 A CN202111153317 A CN 202111153317A CN 113833708 B CN113833708 B CN 113833708B
- Authority
- CN
- China
- Prior art keywords
- valve
- pressure
- oil cavity
- oil
- valve core
- 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.)
- Active
Links
- 238000001514 detection method Methods 0.000 title claims abstract description 45
- 238000006073 displacement reaction Methods 0.000 claims abstract description 45
- 239000010410 layer Substances 0.000 claims abstract description 34
- 239000012792 core layer Substances 0.000 claims abstract description 33
- 238000007789 sealing Methods 0.000 claims abstract description 17
- 239000003921 oil Substances 0.000 claims description 137
- 239000010720 hydraulic oil Substances 0.000 claims description 10
- 230000000052 comparative effect Effects 0.000 claims description 8
- 230000009471 action Effects 0.000 claims description 5
- 230000004044 response Effects 0.000 claims description 5
- 238000001914 filtration Methods 0.000 claims description 4
- 238000005452 bending Methods 0.000 claims description 3
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- 239000007788 liquid Substances 0.000 claims description 3
- 230000008859 change Effects 0.000 claims description 2
- 230000010355 oscillation Effects 0.000 abstract description 4
- 230000005540 biological transmission Effects 0.000 abstract description 2
- 238000000034 method Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 238000013016 damping Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
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)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
A multiway valve with inlet and outlet differential pressure detection belongs to the technical field of hydraulic transmission systems and electronic control, and comprises a main valve core layer and a differential pressure detection layer; the main valve core layer comprises: the valve comprises a valve body, a main valve core displacement sensor and a pressure sensor; electromagnetic drivers are arranged at two ends of the main valve core; an adjusting screw, a spring and a main valve core displacement sensor are arranged in the electromagnetic driver, and the pressure sensor is arranged in a pressure oil port P before throttling and a valve body after throttling; the differential pressure detection layer comprises a valve front oil cavity, a valve rear oil cavity, a pressure spring, a comparison piston, an end cover, a displacement sensor, a proportional electromagnet and a working oil duct; the valve front oil cavity and the valve rear oil cavity are positioned at two sides of the comparison piston, the pressure spring is positioned between the valve rear oil cavity spring seat and the comparison piston, the end cover and the sealing ring are used for sealing and sealing the valve front oil cavity, the annular proportion electromagnet is arranged in the end cover, and the displacement sensor is arranged outside the end cover. The invention avoids the oscillation of the valve core, thereby ensuring the valve core to work stably.
Description
Technical Field
The invention relates to the technical field of hydraulic transmission systems and electronic control, in particular to a multi-way valve with inlet and outlet pressure difference detection.
Background
The multi-way reversing valve is a control element of a hydraulic system of engineering machinery and is an element for realizing system pressure flow control and load pressure control. In order to meet the demands of higher and higher accuracy requirements for flow control and energy efficiency improvement, more accurate control of the main valve core action is required. Most of the existing multi-way valves adopt a load sensitive pressure compensation mode, and a certain pressure loss can be caused either by a pre-valve compensation mode or a post-valve compensation mode. In order to reduce pressure loss and improve energy efficiency, under the condition that the multi-way valve does not use a pressure compensation method, the pressure sensor detects the pressure difference between the front part and the rear part of the main valve to control the electromagnetic driver to realize the position and speed control of the main valve core, thereby realizing the calculation flow compensation. However, due to factors such as severe load pressure variation and interference, the pressure difference between the front valve and the rear valve detected by the pressure sensor also varies severely, which can cause movement oscillation of the main valve core and is unfavorable for stable operation of the system.
Disclosure of Invention
Aiming at the problems of oscillation and unstable operation of a valve core in the control method, the invention provides a multi-way valve with inlet and outlet pressure difference detection
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
a multi-way valve with inlet and outlet pressure difference detection is characterized by comprising a main valve core layer positioned at the upper part and a pressure difference detection layer positioned at the lower part. The main valve core layer and the differential pressure detection layer are of an integrated structure. The hydraulic oil return device is specifically provided with a working oil port A, a working oil port B, a pressure oil port P and an oil return port T. P1 represents the inlet pressure of the multiway valve; p2 represents the outlet pressure of the multiplex valve. The pressure oil port P is communicated with a valve front oil cavity of the pressure difference detection layer, and the throttled oil way is communicated with a valve rear oil cavity of the pressure difference detection layer.
The main valve core layer is provided with a main valve core and a valve core oil duct, and oil inlet and outlet ports of the oil duct are in circular arc transition. The main valve core reciprocates in the main valve core layer, and the working oil port B is communicated with the oil return port T while the pressure oil port P is communicated with the working oil port A, or the working oil port A is communicated with the oil return port T while the pressure oil port P is communicated with the working oil port B, so that the normal work of the actuating mechanism is ensured.
The electromagnetic driver drives the main valve core to move to control the opening of the valve port, and the spring and the adjusting screw are arranged in the electromagnetic driver to keep the main valve core in a neutral position when the main valve core is in a non-working state. A displacement sensor for detecting the displacement of the main valve spool is also included in the electromagnetic driver. A sealing device is arranged between the electromagnetic driver and the valve body.
The main valve core layer is provided with pressure sensors on the front pressure oil port and the rear valve body, differential pressure signals are detected through the pressure sensors, the main valve core is driven to move through an electromagnetic driver after filtering treatment, redundancy of the system is ensured, and the system can work normally under the condition of displacement detection failure.
The differential pressure detection layer comprises a valve front oil cavity, a valve rear oil cavity, a pressure spring, a comparison piston, an end cover, a displacement sensor, an electromagnet and a working oil duct.
The front oil cavity of the valve is communicated with the pressure oil port P of the main valve core layer through a working oil duct, and the rear oil cavity of the valve is communicated with the throttle rear oil passage of the main valve core layer through the working oil duct.
The short rod of the comparative piston is positioned in the oil cavity behind the valve, a certain length is arranged between the short rod and the valve body, and the length is smaller than the maximum compression amount of the pressure spring. When the force comparison piston is at the limit position, the main valve core has a certain valve opening so as to ensure that the multi-way valve keeps stable flow output. The valve body is also provided with a supporting structure of the short rod, so that the short rod part is prevented from bending deformation caused by overlarge pressure. The long rod of the comparative piston is positioned in the front oil cavity of the valve and extends out of the end cover. A displacement sensor for detecting displacement of the comparative piston is arranged outside the end cover. The force comparison pistons are of symmetrical structures, and the effective acting areas of the hydraulic oil force comparison pistons are equal.
The longitudinal section of the end cover is T-shaped, and a sealing ring is arranged between the end cover and the valve body to prevent leakage. The end cap is centrally apertured and is engaged with the longer rod of the relatively piston. The proportional electromagnet is arranged in the end cover, the electric signal is applied to the proportional electromagnet to enable the comparison piston to have flutter action, a certain oil film thickness is maintained on the contact surface of the comparison piston and the valve body, hysteresis caused by friction is reduced, and dynamic response of the system is improved.
The displacement sensor is arranged on the outer side of the end cover, when the pressure of the oil cavity in front of the valve and the pressure of the oil cavity behind the valve have pressure difference, the piston can move relatively, the displacement sensor detects a displacement signal of the piston relatively, the displacement signal is transmitted to the electric control unit and then fed back to the electromagnetic driver of the main valve core layer to control the action of the main valve core so as to achieve the effects of controlling the opening of the valve port and controlling the flow. Force balance equation for the comparison piston and two chambers:
wherein: p1 is the inlet pressure of the multi-way valve, and the unit is MPa; p2 is the outlet pressure of the multi-way valve, and the unit is MPa; a is the pressure area of the comparison piston, and the unit is m 2 The method comprises the steps of carrying out a first treatment on the surface of the M is the mass of the comparison piston, and the unit is K g ；B P Is a viscous damping coefficient; k is the stiffness of the pressure spring, unitIs N.mm -1 The method comprises the steps of carrying out a first treatment on the surface of the X is the displacement of the comparator piston in m.
In order to improve the linearity of the systemThe impact on the system is as small as possible, so that M is as small as possible, i.e. the mass of the force comparison piston is as small as possible while ensuring the necessary strength and rigidity; the effect of (KX) in the formula on the system is as large as possible, so that the value of K is appropriately increased, that is, the stiffness of the pressure spring is increased to improve the linearity of the whole system.
The working oil channels are two oil channels led out of the pressure oil port P of the main valve core layer and the throttled oil channel to two cavities of the differential pressure detection layer respectively, so that phase deviation of pressure of an oil cavity in front of a valve of the differential pressure detection device and pressure of the oil cavity behind the valve can be avoided, the communicating oil channels of the main valve core layer and the displacement detection layer are designed to be of the same structure and the same length to be used as fixed liquid resistance, and the communicating oil channels can reach the differential pressure detection layer as short as possible.
The volume of the oil cavity behind the valve is 10% -30% larger than that of the oil cavity in front of the valve, so that unstable hydraulic oil and possible phase deviation caused by the fact that the volume of the oil cavity behind the valve is reduced when the oil cavity behind the valve is pressurized are prevented.
The invention avoids the oscillation of the valve core, thereby ensuring the valve core to work stably.
Drawings
Fig. 1 is a structural diagram of the present invention.
In the figure: 1. valve body, 2, main valve core, 3, first sealing washer, 4, electromagnetic drive, 5, adjusting screw, 6, the spring, 7, main valve core displacement sensor, 8, displacement sensor, 9, proportion electro-magnet, 10, second sealing washer, 11, end cover, 12, valve oil pocket before the valve, 13, compare the piston, 14, pressure spring, 15, spring holder, 16, bearing structure, 17, valve oil pocket after, 18, working oil duct, 19, pressure sensor, A, first working oil port, B, second working oil port, P, pressure oil port, T, oil return port, P1, multiple-way valve entry pressure, P2, multiple-way valve exit pressure.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
As shown in the figure, the multi-way valve with inlet and outlet pressure difference detection is divided into an upper layer and a lower layer. The upper layer is a main valve core layer, and the lower layer is a differential pressure detection layer.
The main valve core layer comprises: the valve comprises a valve body 1, a main valve core 2, a first sealing ring 3, an electromagnetic driver 5, an adjusting screw 6, a spring 7, a main valve core displacement sensor 7 and a pressure sensor 19;
the differential pressure detection layer includes: the displacement sensor 8, the proportional electromagnet 9, the second sealing ring 10, the end cover 11, the comparative piston 13, the pressure spring 14, the spring seat 15 and the supporting structure 16;
between the main spool layer and the differential pressure detection layer, there are working oil passages 18 connected to the pre-valve oil chamber 12 and the post-valve oil chamber 17 of the differential pressure detection layer, respectively.
The main valve core layer is provided with a main valve core and a valve core oil duct, and oil inlet and outlet ports of the oil duct are in circular arc transition. The main valve core reciprocates in the main valve core layer, and the working oil port B is communicated with the oil return port T while the pressure oil port P is communicated with the working oil port A, or the working oil port A is communicated with the oil return port T while the pressure oil port P is communicated with the working oil port B, so that the normal work of the actuating mechanism is ensured.
The electromagnetic driver drives the main valve core to move to control the opening of the valve port, and the spring and the adjusting screw are arranged in the electromagnetic driver to keep the main valve core in a neutral position when the main valve core is in a non-working state. A displacement sensor for detecting the displacement of the main valve spool is also included in the electromagnetic driver. A sealing device is arranged between the electromagnetic driver and the valve body.
The main valve core layer is provided with pressure sensors on the front pressure oil port and the rear valve body, differential pressure signals are detected through the pressure sensors, the main valve core is driven to move through an electromagnetic driver after filtering treatment, redundancy of the system is ensured, and the system can work normally under the condition of displacement detection failure.
The differential pressure detection layer comprises a valve front oil cavity, a valve rear oil cavity, a pressure spring, a comparison piston, an end cover, a displacement sensor, an electromagnet and a working oil duct.
The front oil cavity of the valve is communicated with the pressure oil port P of the main valve core layer through a working oil duct, and the rear oil cavity of the valve is communicated with the throttle rear oil passage of the main valve core layer through the working oil duct.
The short rod of the comparative piston is positioned in the oil cavity behind the valve, a certain length is arranged between the short rod and the valve body, and the length is smaller than the maximum compression amount of the pressure spring. When the force comparison piston is at the limit position, the main valve core has a certain valve opening so as to ensure that the multi-way valve keeps stable flow output. The valve body is also provided with a supporting structure of the short rod, so that the short rod part is prevented from bending deformation caused by overlarge pressure. The long rod of the comparative piston is positioned in the front oil cavity of the valve and extends out of the end cover. A displacement sensor for detecting displacement of the comparative piston is arranged outside the end cover. The force comparison pistons are of symmetrical structures, and the effective acting areas of the hydraulic oil force comparison pistons are equal.
The longitudinal section of the end cover is T-shaped, and a sealing ring is arranged between the end cover and the valve body to prevent leakage. The end cap is centrally apertured and is engaged with the longer rod of the relatively piston. The proportional electromagnet is arranged in the end cover, the electric signal is applied to the proportional electromagnet to enable the comparison piston to have flutter action, a certain oil film thickness is maintained on the contact surface of the comparison piston and the valve body, hysteresis caused by friction is reduced, and dynamic response of the system is improved.
The working principle of the invention is as follows: when the pressure oil port P starts to feed oil, the valve front oil cavity 12 of the differential pressure detection layer is filled at the same time, the force comparison piston 13 in the differential pressure detection layer moves inwards to compress the pressure spring 14, the displacement sensor 8 detects the movement of the force comparison piston 13, a displacement signal is transmitted to the electronic control unit so as to feed back to the main valve core 2 to reduce the valve opening, the short rod part of the force comparison piston (12) is positioned in the valve rear oil cavity 17, a certain length is reserved between the short rod and the valve body 1, and when the force comparison piston (12) is in a limiting position, the main valve core 2 has a certain valve opening so as to keep the flow stably output. The hydraulic oil is throttled by the main valve core 2 and then fills the valve rear oil cavity 17 of the differential pressure detection layer, at this time, the pressure of the valve rear oil cavity 17 is the multi-way valve outlet pressure P2, the valve front oil cavity 12 is the multi-way valve inlet pressure P1, the hydraulic oil of the valve front oil cavity 12 and the valve rear oil cavity 17 has a pressure difference so as to drive the piston 13 to move, and the displacement sensor 8 transmits a displacement signal to the electric control unit after detecting the displacement of the piston 13 so as to feed back to the electromagnetic driver 4 of the main valve core layer, thereby controlling the movement of the main valve core 2 to change the valve opening degree control flow.
The working oil duct 18 is led to the pre-valve oil cavity 12 and the post-valve oil cavity 17 of the differential pressure detection layer from the main valve core layer pressure oil port P and the throttled oil passage respectively, so that phase deviation exists between the pressures of the pre-valve oil cavity 12 and the post-valve oil cavity 17 of the differential pressure detection device is avoided, the main valve core layer and the working oil duct 18 of the differential pressure detection layer are designed to be of the same structure and the same length as a fixed liquid resistance, the structure and the length of the working oil duct 18 are quantitatively researched and analyzed, the pressure can reach the differential pressure detection layer timely as much as possible, and the response speed and the accuracy of a displacement detection system are improved.
The mass of the force ratio is as small as possible compared to the mass of the piston 13 while ensuring the necessary strength and rigidity; the pressure spring 14 has to select a larger spring stiffness without affecting the response speed, so that the linearity of the system can be improved as much as possible to ensure the accuracy and resolution of displacement detection.
The pressure sensor 19 is arranged on the front pressure oil port P of the main valve core layer and the valve body after throttling, a pressure difference signal can be detected through the pressure sensor 19, the main valve core 2 is driven to move through the electromagnetic driver 4 after filtering treatment, redundancy of the system is ensured, and the system can work normally under the condition of displacement detection failure.
Claims (1)
1. A multi-way valve with inlet and outlet differential pressure detection is characterized by comprising a main valve core layer positioned at the upper part and a differential pressure detection layer positioned at the lower part; the main valve core layer and the differential pressure detection layer are of an integrated structure; the main valve core layer comprises: the valve comprises a valve body, a main valve core, a sealing ring, an electromagnetic driver, an adjusting screw, a spring, a main valve core displacement sensor and a pressure sensor; electromagnetic drivers are arranged at two ends of the main valve core and are sealed through sealing rings; an adjusting screw, a spring and a main valve core displacement sensor are arranged in the electromagnetic driver, and the pressure sensor is arranged in a pressure oil port P before throttling and a valve body after throttling; the differential pressure detection layer comprises a valve front oil cavity, a valve rear oil cavity, a pressure spring, a comparison piston, an end cover, a displacement sensor, a proportional electromagnet and a working oil duct; the valve front oil cavity and the valve rear oil cavity are positioned at two sides of the comparison piston, the pressure spring is positioned between the valve rear oil cavity spring seat and the comparison piston, the end cover and the sealing ring are used for sealing and sealing the valve front oil cavity, the inside of the end cover is provided with a ring-shaped proportion electromagnet, and the outside is provided with a displacement sensor; the valve front oil cavity is communicated with the pressure oil port P of the main valve core layer through a working oil duct, the valve rear oil cavity is communicated with the throttle rear oil path of the main valve core layer through the working oil duct, and the effective acting area of the valve front oil cavity is equal to that of the valve rear oil cavity compared with that of the comparison piston; the short rod part of the force comparison piston is positioned in the oil cavity behind the valve, the length between the short rod and the valve body is smaller than the limit compression amount of the pressure spring, and when the force comparison piston is positioned at the limit position, the main valve core has a certain valve port opening degree so as to ensure that the multi-way valve keeps stable flow output; the valve body is also provided with a supporting structure for preventing the short rod part from bending deformation caused by excessive pressure and the short rod part of the relatively piston; the long rod of the comparative piston is positioned in the front oil cavity of the valve and extends out of the end cover, and a displacement sensor for detecting the displacement of the valve core is arranged outside the end cover; the working oil channels are respectively led to a front oil cavity and a rear oil cavity of the differential pressure detection layer from a main valve core layer pressure oil port P and a throttle rear oil channel, and the main valve core layer and the working oil channels of the differential pressure detection layer are designed to be of the same structure and the same length and serve as fixed liquid resistance; the volume of the oil cavity behind the valve is 10% -30% larger than that of the oil cavity in front of the valve, so that unstable hydraulic oil and possible phase deviation caused by the fact that the volume of the oil cavity behind the valve is reduced when the oil cavity behind the valve is pressurized are prevented; the pressure sensors are arranged on the front pressure oil port and the rear throttle valve body of the main valve core layer, the pressure difference signals can be detected through the pressure sensors, the main valve core is driven to move through the electromagnetic driver after filtering treatment, the redundancy of the system is ensured, and the system can work normally under the condition of displacement detection failure; the longitudinal section of the end cover is T-shaped, a sealing ring is arranged between the end cover and the valve body to prevent leakage, the center of the end cover is provided with a hole and is matched with a long rod of the comparison piston, a proportional electromagnet is arranged in the end cover, an electric signal is applied to the comparison piston through the proportional electromagnet to enable the comparison piston to have flutter action, a certain oil film thickness is maintained at the contact surface of the comparison piston and the valve body, hysteresis caused by friction is reduced, and the dynamic response of a system is improved; when the pressure oil port P starts to enter oil, the valve front oil cavity of the differential pressure detection layer is filled simultaneously, the pressure comparison piston in the differential pressure detection layer moves inwards to compress the pressure spring, the displacement sensor detects the movement of the pressure comparison piston, a displacement signal is transmitted to the electronic control unit and fed back to the main valve core to reduce the opening degree of the valve port, hydraulic oil is filled in the valve rear oil cavity of the differential pressure detection layer after being throttled by the main valve core, at the moment, the pressure of the valve rear oil cavity is the multi-way valve outlet pressure P2, the valve front oil cavity is the multi-way valve inlet pressure P1, the pressure difference exists between the hydraulic oil in the valve front oil cavity and the hydraulic oil in the valve rear oil cavity, so that the pushing force is compared with the movement of the piston, and the electromagnetic driver which transmits the displacement signal to the electronic control unit and feeds back to the main valve core layer after detecting the displacement of the pressure comparison piston controls the movement of the main valve core layer to change the opening degree control flow.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111153317.5A CN113833708B (en) | 2021-09-29 | 2021-09-29 | Multi-way valve with inlet and outlet pressure difference detection function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111153317.5A CN113833708B (en) | 2021-09-29 | 2021-09-29 | Multi-way valve with inlet and outlet pressure difference detection function |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN113833708A CN113833708A (en) | 2021-12-24 |
| CN113833708B true CN113833708B (en) | 2024-01-19 |
Family
ID=78967508
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111153317.5A Active CN113833708B (en) | 2021-09-29 | 2021-09-29 | Multi-way valve with inlet and outlet pressure difference detection function |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113833708B (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105221506A (en) * | 2015-09-18 | 2016-01-06 | 徐州工业职业技术学院 | A kind of load-sensitive valve and load-sensitive hydraulic system |
| CN108150475A (en) * | 2018-02-05 | 2018-06-12 | 江苏恒立液压科技有限公司 | Load sensing multi-way valve group and with its walking machine hydraulic system |
| CN109630491A (en) * | 2018-12-26 | 2019-04-16 | 太原理工大学 | A kind of automatically controlled compensation two-way proportional flow control valve |
| CN111022404A (en) * | 2019-12-16 | 2020-04-17 | 江苏汇智高端工程机械创新中心有限公司 | Reversing valve, hydraulic system and engineering machinery |
| CN111396391A (en) * | 2020-04-23 | 2020-07-10 | 太原理工大学 | High-precision large-flow multi-way valve with disturbance compensation |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109654074B (en) * | 2018-12-26 | 2020-04-07 | 太原理工大学 | Hydraulic system of engineering machinery |
-
2021
- 2021-09-29 CN CN202111153317.5A patent/CN113833708B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105221506A (en) * | 2015-09-18 | 2016-01-06 | 徐州工业职业技术学院 | A kind of load-sensitive valve and load-sensitive hydraulic system |
| CN108150475A (en) * | 2018-02-05 | 2018-06-12 | 江苏恒立液压科技有限公司 | Load sensing multi-way valve group and with its walking machine hydraulic system |
| CN109630491A (en) * | 2018-12-26 | 2019-04-16 | 太原理工大学 | A kind of automatically controlled compensation two-way proportional flow control valve |
| CN111022404A (en) * | 2019-12-16 | 2020-04-17 | 江苏汇智高端工程机械创新中心有限公司 | Reversing valve, hydraulic system and engineering machinery |
| CN111396391A (en) * | 2020-04-23 | 2020-07-10 | 太原理工大学 | High-precision large-flow multi-way valve with disturbance compensation |
Also Published As
| Publication number | Publication date |
|---|---|
| CN113833708A (en) | 2021-12-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5445188A (en) | Pilot operated servo valve | |
| US9234532B2 (en) | Velocity control of unbalanced hydraulic actuator subjected to over-center load conditions | |
| US4753328A (en) | Vehicle suspension systems and damping arrangements therefor | |
| US5937645A (en) | Hydraulic device | |
| US4132506A (en) | Pressure and volume-flow control for variable pump | |
| JP2010528243A (en) | Force feedback poppet valve with integrated pressure compensator | |
| USRE38355E1 (en) | Electrohydraulic control device for double-acting consumer | |
| US3854382A (en) | Hydraulic actuator controls | |
| EP2201254B1 (en) | Load sensing directional control valve with an element having priority under saturation conditions | |
| US6220288B1 (en) | Electrohydraulic control device | |
| CN113833708B (en) | Multi-way valve with inlet and outlet pressure difference detection function | |
| CN111365313B (en) | Valve core friction force compensation hydraulic valve under centrifugal environment | |
| WO2021141874A1 (en) | Flow control valve with load-sense signal generation | |
| JP4960646B2 (en) | Load sensing hydraulic controller | |
| US4542678A (en) | Control arrangement for hydraulic motor | |
| US5386697A (en) | Unit for controlling a plurality of hydraulic actuators | |
| US5799485A (en) | Electrohydraulic control device for double-acting consumer | |
| WO2018043401A1 (en) | Hydraulic drive system for construction machine | |
| JP4658274B2 (en) | Control valve | |
| JPH06159311A (en) | Control unit of plurality of hydraulic actuator | |
| US5735311A (en) | Pressure compensation valve | |
| JP2000266046A (en) | Bearing preload hydraulic circuit, main spindle device and method for preload of roller bearing | |
| US5533551A (en) | Pressure regulating servovalve | |
| JP2000283109A (en) | Actuator controller | |
| JPS63263119A (en) | Vehicle hydraulic supply device |
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 |