CN111664136B - Load compensation balance valve - Google Patents
Load compensation balance valve Download PDFInfo
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- CN111664136B CN111664136B CN202010447759.XA CN202010447759A CN111664136B CN 111664136 B CN111664136 B CN 111664136B CN 202010447759 A CN202010447759 A CN 202010447759A CN 111664136 B CN111664136 B CN 111664136B
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- 238000013016 damping Methods 0.000 claims description 24
- 230000005484 gravity Effects 0.000 abstract description 10
- 230000009471 action Effects 0.000 abstract description 5
- 238000000034 method Methods 0.000 abstract description 5
- 230000008569 process Effects 0.000 abstract description 5
- 239000012530 fluid Substances 0.000 description 9
- 230000006872 improvement Effects 0.000 description 9
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000006378 damage Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 208000027418 Wounds and injury Diseases 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 208000014674 injury Diseases 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/026—Pressure compensating valves
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
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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
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
Abstract
A load compensating balance valve. The balance valve solves the problem that the balance valve of the existing gravity system has poor speed-regulating capacity in the actual use process. The valve comprises a valve body and a valve core, wherein a first oil port and a second oil port are formed in the valve body, a control cavity and a spring cavity are formed in two ends of the valve core, a first channel is formed in the valve core, the first channel is communicated with the first oil port, the valve core is in a first state of enabling the first oil port to be isolated from the second oil port and a second state of enabling the first oil port to be communicated with the second oil port, when the valve core is in the second state, pressure oil of the first oil port is communicated with the spring cavity through the first channel and a first throttling port, and spring force of the spring cavity and pressure of the spring cavity for picking up the pressure oil of the first oil port are matched with each other to control opening of the control cavity in a mutual balance mode. The invention also has the advantages of simple structure, convenient assembly, reliable action, long service life and the like.
Description
Technical Field
The invention relates to a hydraulic control system of engineering machinery, in particular to a load compensation balance valve.
Background
With the requirements of the construction industry on efficiency improvement, the demand of aerial work platform equipment is wider and wider. It is commonly used for performing high-altitude operations such as exterior wall maintenance, high-altitude construction, street lamp installation, etc. The existing high-altitude operation platform product amplitude-change lowering system has two amplitude-change lowering modes of gravity falling and power falling, and the two amplitude-change lowering modes have own advantages and disadvantages.
In many boom engineering machinery, the load of an oil cylinder supporting a boom is changed along with the change of the angle of the boom, and in general, the lower the angle of the boom is, the larger the load is; the higher the boom angle, the smaller the load. The balance valve is generally arranged on the oil cylinder of the hydraulic system, and plays a role in maintaining load when the balance valve is static, so that oil leakage of the oil cylinder is prevented, and the overturning of the arm support structure is further prevented, so that danger is avoided; when the arm support falls, the falling speed of the arm support is controlled through the throttling function of the balance valve, so that the falling speed of the arm support can be controlled according to the requirement of an operator.
The control of the falling speed of the arm support is to control the oil quantity of a load cavity of the oil cylinder, and two general modes exist, namely, the control is performed through an external control pilot low-pressure oil source, namely, only a balance valve is opened, and the flow is generated on the balance valve by means of the gravity of the arm support; one is a high-pressure oil source, the oil source acts on the other cavity of the oil cylinder, and simultaneously controls the control port of the balance valve to open the balance valve so as to form a closed loop, namely a power falling mode; these two modes of luffing down each have their own advantages and disadvantages.
The power dropping mode has the characteristic of high efficiency, and the power dropping system has the defect that certain pressure oil is needed to open the balance valve on the corresponding oil return path through the control port in the extending and retracting processes of the oil cylinder, so that the energy consumption is increased; meanwhile, in the amplitude-variable descending process, the load acting force changes greatly, so that the balance valve is easy to shake, and the amplitude-variable oil cylinder is unstable to fall. The gravity falling mode has the characteristics of stability and low energy consumption, and the gravity falling system has the defects that the gravity falling of the amplitude-variable oil cylinder is influenced by load, when the load is large, the acting force applied to the amplitude-variable oil cylinder by the gravity is large along with the reduction of the angle of the arm support, the falling speed is relatively high, the corresponding flow passing through the balance valve can be increased at the moment, and once the speed is too high, the risk of out of control and the like can be caused, so that certain economic loss and personal injury are caused. When the load is small, the acting force applied by gravity to the amplitude-variable oil cylinder is small, the falling speed is slow, and the working efficiency is reduced.
Disclosure of Invention
The invention provides a load compensation balance valve, which aims to solve the problem that the balance valve of the existing gravity system is poor in speed leveling capability in the actual use process in the background technology.
The technical scheme of the invention is as follows: the utility model provides a load compensation balance valve, includes valve body and case, the valve body on be equipped with first hydraulic fluid port and second hydraulic fluid port, the both ends of case are equipped with control chamber and spring chamber, the case on be equipped with first passageway, first passageway and first hydraulic fluid port be linked together, the case have the first state that makes first hydraulic fluid port and second hydraulic fluid port separate and the second state that makes first hydraulic fluid port and second hydraulic fluid port be linked together, the case be in the second state, the pressure oil of first hydraulic fluid port be linked together through first passageway, first orifice and spring chamber, spring force in spring chamber, spring chamber pick up the pressure of first hydraulic fluid port pressure mutually support with the opening of control chamber's control force mutual balance control case.
As an improvement of the invention, a first valve sleeve is arranged in the valve body, a load pick-up port is arranged on the first valve sleeve, and the load pick-up port enables pressure oil of the first throttling port to be communicated with the spring cavity when the valve core is in a second state.
As a further improvement of the invention, the valve body is provided with an oil return port, and an oil outlet of the load pick-up port is communicated with the oil return port.
As a further improvement of the invention, the valve body is provided with a reversing valve and a first damping hole, the reversing valve is arranged at the oil outlet of the load pick-up port, and the reversing valve is provided with a first position for communicating pressure oil at the load pick-up port with the oil return port and a second position for communicating the pressure oil at the load pick-up port with the oil return port through the first damping hole.
As a further development of the invention, the first orifice is a fixed orifice groove.
As a further improvement of the invention, the first throttling opening is a variable throttling groove, and the opening size of the variable throttling groove changes along with the position change of the valve core when the valve core is in the second state.
As a further improvement of the invention, the first throttling orifice is arranged on the outer surface of the valve core, and the first throttling orifice is in a bevel groove or triangular groove structure.
As a further improvement of the invention, the valve body is provided with a second valve sleeve, the second valve sleeve is arranged at one end of the valve core and is matched with the valve body to form the spring cavity, and the valve core is axially and slidingly matched with the second valve sleeve in a circumferential rotation manner.
As a further improvement of the invention, the valve further comprises a positioning piece, and a positioning notch which is matched with the end part of the valve core and the end part of the second valve sleeve and used for accommodating the positioning piece is arranged between the end part of the valve core and the end part of the second valve sleeve.
As a further improvement of the invention, a control piston is arranged in the control cavity, the control piston comprises a pushing end propped against the valve core and a control end for receiving control oil pressure, the diameter of the control end of the control piston is larger than that of the valve core, and a second damping hole for communicating the control cavity with the oil return port is arranged on the control piston.
The invention has the beneficial effects that the compensation function is arranged, the speed can be regulated in a compensation mode, namely, the higher the load pressure is realized under the condition of not changing the external control oil source pressure, the slower the speed is, the dynamic balance is realized, and the product action is stable and reliable. The invention also has the advantages of simple structure, convenient assembly, reliable action, long service life and the like.
Drawings
Fig. 1 is a schematic structural diagram of an embodiment of the present invention.
Fig. 2 is a schematic view of the semi-sectional structure of fig. 1.
Fig. 3 is a partially enlarged view of the first restriction 22 of fig. 2.
Fig. 4 is a schematic structural view of the valve core 2 in fig. 2.
Fig. 5 is a hydraulic schematic of a first embodiment of the present invention.
Fig. 6 is a hydraulic schematic diagram of a second embodiment of the present invention.
In the figure, 1, a valve body; 11. a reversing valve; 2. a valve core; 21. a first channel; 22. a first orifice; 3. a control chamber; 4. a spring cavity; 5. a first valve sleeve; 51. a load pickup port; 6. a first damping hole; 7. a second valve sleeve; 8. a positioning piece; 9. a control piston; 91. a pushing end; 92. a control end; 93. a second damping hole; A. a first oil port; B. a second oil port; l, an oil return port.
Detailed Description
Embodiments of the invention are further described below with reference to the accompanying drawings:
the load compensation balance valve comprises a valve body 1 and a valve core 2, wherein a first oil port A and a second oil port B are arranged on the valve body 1, a control cavity 3 and a spring cavity 4 are arranged at two ends of the valve core 2, a first channel 21 is arranged on the valve core 2, the first channel 21 is communicated with the first oil port A, the valve core 2 is in a first state of enabling the first oil port A to be isolated from the second oil port B and a second state of enabling the first oil port A to be communicated with the second oil port B, when the valve core 2 is in the second state, pressure oil of the first oil port A is communicated with the spring cavity 4 through the first channel 21 and a first throttling port 22, and spring force of the spring cavity 4 and pressure of the spring cavity 4 picking up the pressure oil of the first oil port A are matched with control force of the control cavity 3 to balance opening of the valve core 2. The invention has the beneficial effects that the compensation function is arranged, the speed can be regulated in a compensation mode, namely, the higher the load pressure is realized under the condition of not changing the external control oil source pressure, the slower the speed is, the dynamic balance is realized, and the product action is stable and reliable. The invention also has the advantages of simple structure, convenient assembly, reliable action, long service life and the like. According to the invention, the load pressure oil is introduced into the spring cavity of the balance valve, so that in a system under the gravity, when the swing arm is reduced along with the angle, the speed can be regulated when the load oil pressure is increased, and the damage to personnel and products caused by the too high speed of the swing arm is avoided.
The valve body 1 is internally provided with a first valve sleeve 5, the first valve sleeve 5 is provided with a load pickup opening 51, and the load pickup opening 51 enables pressure oil of the first throttling port 22 to be communicated with the spring cavity 4 when the valve core 2 is in the second state. The valve body 1 is provided with an oil return port L, and an oil outlet of the load pick-up port 51 is communicated with the oil return port L. Specifically, a first damping hole is provided on the valve body, and the oil outlet of the load pickup port 51 is communicated with the oil return port L through the first damping hole. The difference between fig. 5 and 6 is that whether a reversing valve control is provided is that the valve body 1 is provided with a reversing valve 11 and a first damping hole 6, the reversing valve 11 is arranged at the oil outlet of the load pick-up port 51, and the reversing valve 11 has a first position for communicating pressure oil at the load pick-up port 51 with the oil return port L and a second position for communicating pressure oil at the load pick-up port 51 with the oil return port L through the first damping hole 6. Specifically, the reversing valve is a two-position three-way electromagnetic valve, so that the compensation electric selection can be realized through the on-off of the electromagnetic valve. When compensation is not needed, the electromagnetic valve is powered off, and the falling speed of the oil cylinder is high (at this time, the first damping hole is understood to be large enough, so that the pressure oil of the oil outlet of the load pick-up port 51 is directly communicated with the oil return port, namely, no pressure oil enters the spring cavity); when compensation is needed, the electromagnetic valve is powered up, and the speed is correspondingly compensated (the structure can be simply understood as fig. 2). A bridge is formed between the first throttling orifice and the first damping, and the pressure (called compensation pressure) between the first throttling orifice and the first damping acts on a spring cavity of the balance valve, so that a valve core of the balance valve is acted by the spring force and the compensation pressure, and the pressure of the spring cavity is related to the displacement and the load of the valve core, so that the compensation effect is realized. Specifically, the first damping hole is arranged, the compensation amount can be adjusted through the first damping hole, and the smaller the first damping hole is, the earlier the compensation is; the larger the first damping hole, the later the compensation, i.e. the first damping hole can be set as a variable damping hole, and the pressure oil quantity entering the spring cavity can be adjusted by adjusting the first damping hole.
The balance valve has four oil ports A, B, K, L, and of course, the balance valve can be adjusted according to the requirement, such as pressure measuring port, heat sensitive overflow valve can be added at port A according to the requirement. Specifically, an oil return port L is arranged behind the first damping hole, and the oil return port L is directly communicated with the oil tank without any back pressure. Of course, if it is actually needed, for example, in order to fill the spring cavity, the back pressure can be properly increased to keep the spring cavity full, so that the response of compensation can be improved, and the K port is the control pressure oil port of the control cavity. Typically, port a is connected to a load cylinder and port B is typically connected to a tank.
The first throttling orifice 22 is a fixed throttling groove. Specifically, the first orifice 22 is a variable orifice, and the opening size of the variable orifice changes with the position change of the valve element 2 when the valve element 2 is in the second state. Specifically, the first throttling hole can be a fixed throttling groove or a variable throttling groove, the size of the fixed throttling groove is not changed along with displacement, the compensation characteristic of the variable throttling groove along with the displacement is different from that of the fixed throttling groove, the compensation characteristic of the variable throttling groove is influenced by pressure and displacement, and the fixed throttling groove is influenced by pressure only.
The first throttling orifice 22 is arranged on the outer surface of the valve core 2, and the first throttling orifice 22 is of an inclined plane groove or triangular groove structure. Of course, the first orifice may have other structures during actual production.
The valve body 1 is provided with a second valve sleeve 7, the second valve sleeve 7 is arranged at one end of the valve core 2 and is matched with the valve body 1 to form the spring cavity 4, and the valve core 2 and the second valve sleeve 7 axially slide and circumferentially rotate to be matched. Specifically, the invention also comprises a positioning piece 8, and a positioning notch which is matched with each other and used for accommodating the positioning piece 8 is arranged between the end part of the valve core 2 and the end part of the second valve sleeve 7. The invention discloses a variable throttling groove, which is characterized in that a chute is arranged on a valve core, a load pick-up port is a round hole, and a main valve core can rotate at 360 degrees in the assembly process. The positioning structure design realizes the positioning function, has the function of an oil duct, and can be used for compensating pressure to enter the spring cavity by the aid of the oil duct.
The control cavity 3 is internally provided with a control piston 9, the control piston 9 comprises a pushing end 91 propped against the valve core 2 and a control end 92 for receiving control oil pressure, the diameter of the control end 92 of the control piston 9 is larger than that of the valve core 2, and the control piston 9 is provided with a second damping hole 93 for communicating the control cavity 3 with an oil return port L. The diameter of the control end 92 of the control piston 9 is larger than that of the valve core 2, so that the conditioning pressure of the spring cavity spring can be increased, and the pressure regulating interval is larger. The invention controls the valve core to move by controlling the piston, is convenient to control, and can also control the valve core to move in other modes in the actual production process.
In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art. Furthermore, in the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
The skilled person will know: while the invention has been described in terms of the foregoing embodiments, the inventive concepts are not limited to the invention, and any modifications that use the inventive concepts are intended to be within the scope of the appended claims.
Claims (3)
1. A load compensation balance valve comprises a valve body (1) and a valve core (2), and is characterized in that a first oil port (A) and a second oil port (B) are arranged on the valve body (1), a control cavity (3) and a spring cavity (4) are arranged at two ends of the valve core (2), a first channel (21) is arranged on the valve core (2), the first channel (21) is communicated with the first oil port (A), the valve core (2) is provided with a first state enabling the first oil port (A) to be isolated from the second oil port (B) and a second state enabling the first oil port (A) to be communicated with the second oil port (B), when the valve core (2) is in the second state, pressure oil of the first oil port (A) is communicated with the spring cavity (4) through the first channel (21) and the first throttling port (22), the spring force of the spring cavity (4) is matched with the pressure oil of the first oil port (A) to pick up pressure oil, the first oil port (A) is matched with the pressure oil of the control cavity (3) to be in a mutual mode, a valve sleeve (5) is arranged in the first valve core (5) is arranged on the valve body (1), the valve body (1) is provided with an oil return port (L), an oil outlet of the load pick-up port (51) is communicated with the oil return port (L), the valve body (1) is provided with a reversing valve (11) and a first damping hole (6), the reversing valve (11) is arranged at the oil outlet of the load pick-up port (51), the reversing valve (11) is provided with a first position for enabling the pressure oil at the load pick-up port (51) to be communicated with the oil return port (L) and a second position for enabling the pressure oil at the load pick-up port (51) to be communicated with the oil return port (L) through the first damping hole (6), the first throttle port (22) is arranged on the outer surface of the valve body (2), the first throttle port (22) is of a bevel groove or triangular groove structure, the valve body (1) is provided with a second valve sleeve (7), the second valve sleeve (7) is axially matched with the valve body (8) and is axially matched with the valve body (2) to form a sliding piece (8), the valve core is characterized in that a positioning notch matched with the end part of the valve core (2) and the end part of the second valve sleeve (7) and used for accommodating the positioning piece (8) is formed, a control piston (9) is arranged in the control cavity (3), the control piston (9) comprises a pushing end (91) propped against the valve core (2) and a control end (92) used for receiving control oil pressure, the diameter of the control end (92) of the control piston (9) is larger than that of the valve core (2), and a second damping hole (93) used for communicating the control cavity (3) with the oil return port (L) is formed in the control piston (9).
2. A load compensating balance valve according to claim 1, characterized in that said first restriction (22) is a fixed restriction.
3. A load compensating balance valve according to claim 1, characterized in that the first restriction (22) is a variable restriction, the opening size of which varies with the position of the valve element (2) when the valve element (2) is in the second state.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010447759.XA CN111664136B (en) | 2020-05-25 | 2020-05-25 | Load compensation balance valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010447759.XA CN111664136B (en) | 2020-05-25 | 2020-05-25 | Load compensation balance valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111664136A CN111664136A (en) | 2020-09-15 |
| CN111664136B true CN111664136B (en) | 2024-04-19 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010447759.XA Active CN111664136B (en) | 2020-05-25 | 2020-05-25 | Load compensation balance valve |
Country Status (1)
| Country | Link |
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| CN (1) | CN111664136B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113833709B (en) * | 2021-11-25 | 2022-02-25 | 江苏汇智高端工程机械创新中心有限公司 | Adjustable load pressure compensation balance system, end cover and balance valve |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH048902A (en) * | 1990-04-27 | 1992-01-13 | Hitachi Constr Mach Co Ltd | Pressure compensating valve |
| JP2002357276A (en) * | 2001-06-01 | 2002-12-13 | Yuken Kogyo Co Ltd | Counter balance valve |
| CN105035979A (en) * | 2015-08-05 | 2015-11-11 | 常德中联重科液压有限公司 | Balance valve group and hydraulic system |
| CN105952705A (en) * | 2016-06-29 | 2016-09-21 | 宁波文泽机电技术开发有限公司 | Balance valve |
| CN106195370A (en) * | 2016-08-13 | 2016-12-07 | 李军 | Cartridge balanced valve |
| CN206988212U (en) * | 2017-07-27 | 2018-02-09 | 圣邦集团有限公司 | A kind of balanced valve suitable for crane amplitude variation oil cylinder |
| CN108223864A (en) * | 2018-01-22 | 2018-06-29 | 邵立坤 | A kind of No leakage proportional velocity regulating valve |
| CN108843645A (en) * | 2018-07-20 | 2018-11-20 | 佛山信卓派思机械科技有限公司 | A kind of balanced valve |
| CN108916149A (en) * | 2018-08-31 | 2018-11-30 | 圣邦集团有限公司 | A kind of hydraulic multitandem valve and the hydraulic control system equipped with the multi-way valve |
| CN109488653A (en) * | 2018-12-24 | 2019-03-19 | 圣邦集团有限公司 | Double compensation spool valve post-compensation multi-way valve |
| CN110410531A (en) * | 2019-07-18 | 2019-11-05 | 圣邦集团有限公司 | A kind of hydraulic multitandem valve |
| CN212272686U (en) * | 2020-05-25 | 2021-01-01 | 圣邦集团有限公司 | Load compensation balance valve |
-
2020
- 2020-05-25 CN CN202010447759.XA patent/CN111664136B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH048902A (en) * | 1990-04-27 | 1992-01-13 | Hitachi Constr Mach Co Ltd | Pressure compensating valve |
| JP2002357276A (en) * | 2001-06-01 | 2002-12-13 | Yuken Kogyo Co Ltd | Counter balance valve |
| CN105035979A (en) * | 2015-08-05 | 2015-11-11 | 常德中联重科液压有限公司 | Balance valve group and hydraulic system |
| CN105952705A (en) * | 2016-06-29 | 2016-09-21 | 宁波文泽机电技术开发有限公司 | Balance valve |
| CN106195370A (en) * | 2016-08-13 | 2016-12-07 | 李军 | Cartridge balanced valve |
| CN206988212U (en) * | 2017-07-27 | 2018-02-09 | 圣邦集团有限公司 | A kind of balanced valve suitable for crane amplitude variation oil cylinder |
| CN108223864A (en) * | 2018-01-22 | 2018-06-29 | 邵立坤 | A kind of No leakage proportional velocity regulating valve |
| CN108843645A (en) * | 2018-07-20 | 2018-11-20 | 佛山信卓派思机械科技有限公司 | A kind of balanced valve |
| CN108916149A (en) * | 2018-08-31 | 2018-11-30 | 圣邦集团有限公司 | A kind of hydraulic multitandem valve and the hydraulic control system equipped with the multi-way valve |
| CN109488653A (en) * | 2018-12-24 | 2019-03-19 | 圣邦集团有限公司 | Double compensation spool valve post-compensation multi-way valve |
| CN110410531A (en) * | 2019-07-18 | 2019-11-05 | 圣邦集团有限公司 | A kind of hydraulic multitandem valve |
| CN212272686U (en) * | 2020-05-25 | 2021-01-01 | 圣邦集团有限公司 | Load compensation balance valve |
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| CN111664136A (en) | 2020-09-15 |
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