CN104481953A - Integrated valve with flow distribution being irrelevant to load pressure and throttling edge being controlled independently - Google Patents
Integrated valve with flow distribution being irrelevant to load pressure and throttling edge being controlled independently Download PDFInfo
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- CN104481953A CN104481953A CN201410765008.7A CN201410765008A CN104481953A CN 104481953 A CN104481953 A CN 104481953A CN 201410765008 A CN201410765008 A CN 201410765008A CN 104481953 A CN104481953 A CN 104481953A
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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
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
- F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds
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- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
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- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a high-response integrated valve with flow distribution being irrelevant to load pressure and a throttling edge being controlled independently. The integrated valve comprises a multi-connected valve bank, a supply oil path P, an oil return path T and a load sensitive oil path LS, wherein the multi-connected valve bank shares a unique supply oil path P, oil return path T and load sensitive oil path LS; the multi-connected valve bank comprises N valve banks, namely, a first-connected valve bank, a second-connected valve bank, ..., a (N-1)th-connected valve bank and a Nth-connected valve bank respectively; N is a natural number being greater than or equal to 2; the first-connected valve bank, the second-connected valve bank, ..., the (N-1)th-connected valve bank and the Nth-connected valve bank have the same composition structures, and are provided with two output oil ports connected with a hydraulic actuator; the first-connected valve bank comprises five two-position and two-way electrohydraulic proportional valves, two shuttle valves, two one-way valves and two pressure compensating valves. The integrated valve is simple in structural composition, is convenient to design and machine, and has high interchangeability.
Description
Technical field
The present invention relates to the height response integrated valve that a kind of hydraulic system throttling limit independently controls, particularly relate to the integrated valve that throttling limit that a kind of assignment of traffic and induced pressure have nothing to do independently controls.
Background technique
The hydraulic system that assignment of traffic and induced pressure have nothing to do, refers to final controlling element highest load pressure control pump and pressure compensated distribution of load independent flow system.Principle be pressure-compensated valve is placed in main valve after, valve post-compensation is carried out to system pressure, when multiple actuator works simultaneously, carry out the pressure of the less actuator of compensatory pressure with the pressure of maximum pressure actuator, to make to keep the pressure reduction of each actuator constant at any time.Therefore can realize the pro rate to multiple actuators flow, when flow needed for final controlling element is greater than the flow of pump, assignment of traffic can be given each final controlling element by system in proportion, instead of flows to underloaded final controlling element.
The hydraulic system realizing assignment of traffic irrelevant to induced pressure forms primarily of load-reacting pump, assignment of traffic control valve, pressure compensator, shuttle valve and corresponding induction oil circuit.Assignment of traffic control valve by controlling the flow reaching hydraulic control final controlling element while bidirectional throttle limit, and then controls the object of its motion.Assignment of traffic control valve only has one to control spool usually, this single spool to the double-direction control on throttling limit, will inevitably cause both one of restriction loss and energy ezpenditure, and then the efficiency causing hydraulic system lower and response performance.Meanwhile, often need for dissimilar hydraulic actuator, design and process different types of control spool, thus the interchangeability causing assignment of traffic control valve is poor, spool design processing difficulties etc.
Summary of the invention
In order to overcome prior art above shortcomings, the invention provides the height that throttling limit that a kind of assignment of traffic and induced pressure have nothing to do independently controls and respond integrated valve, the present invention not only has the irrelevant characteristic of assignment of traffic and induced pressure, and structure simple, design easy to process, interchangeability good, and makes hydraulic system have higher efficiency and response performance.
The technical solution adopted for the present invention to solve the technical problems is:
The integrated valve that the throttling limit that a kind of assignment of traffic and induced pressure have nothing to do independently controls, it comprises Multigang valve group, supply oil circuit P, oil circuit T, load-sensitive oil circuit LS, described Multigang valve group shares unified supply oil circuit P, oil circuit T and load-sensitive oil circuit LS, described Multigang valve group comprises N number of valve group, be respectively the first valve group, second valve group, N – 1 valve group, N joins valve group, here N be more than or equal to 2 natural number, the first described valve group, second valve group, N – 1 valve group, N joins valve group and has identical composition structure, and have two output oil ports be connected with hydraulic actuator, the first described valve group comprises five bi-bit bi-pass electro-hydraulic proportional valves, two shuttle valves, two one-way valves and two pressure-compensated valves, first connecting passage, first connecting passage of one the 4th bi-bit bi-pass electro-hydraulic proportional valve of one first bi-bit bi-pass electro-hydraulic proportional valve are connected with the first connecting passage of one second pressure-compensated valve with the first connecting passage of one first one-way valve, first connecting passage, first connecting passage of one the 5th bi-bit bi-pass electro-hydraulic proportional valve of one second bi-bit bi-pass electro-hydraulic proportional valve are connected with the first connecting passage of one first pressure-compensated valve with the first connecting passage of one second one-way valve, first connecting passage of one the 3rd bi-bit bi-pass electro-hydraulic proportional valve, the second connecting passage of one the 4th bi-bit bi-pass electro-hydraulic proportional valve are connected with supply oil circuit P with the second connecting passage of one the 5th bi-bit bi-pass electro-hydraulic proportional valve, second connecting passage of the second connecting passage of one first bi-bit bi-pass electro-hydraulic proportional valve, the second connecting passage of one second bi-bit bi-pass electro-hydraulic proportional valve and one the 3rd bi-bit bi-pass electro-hydraulic proportional valve and oil circuit T-phase connect, first of one second shuttle valve compares end and is connected with the second connecting passage of one first one-way valve with the second connecting passage of one second pressure-compensated valve, second of one second shuttle valve compares end and is connected with the second connecting passage of one second one-way valve with the second connecting passage of one first pressure-compensated valve, the output oil port of one second shuttle valve compares to hold with first of one first shuttle valve and is connected, second of one first shuttle valve compares end and is connected with the output oil port of bigeminy first shuttle valve, and the output oil port of one first shuttle valve, the control port of one first pressure-compensated valve are connected with load-sensitive oil circuit LS with the control port of one second pressure-compensated valve,
Second of bigeminy first shuttle valve of the second valve group compares end and is connected with the output oil port of 3 first shuttle valves of the 3rd valve group; By that analogy, the N-1 that N-1 joins valve group joins second of the first shuttle valve and compares the output oil port that N that end and N join valve group joins the first shuttle valve and be connected, and the N that N joins valve group joins second of the first shuttle valve and compares to hold and be connected with load-sensitive oil circuit LS; The control port that output oil port and the N of one first shuttle valve join valve first pressure-compensated valve is connected with the control port that N joins the second pressure-compensated valve.
The master input device of each connection is to controller input signal, after controller receives signal, carry out processing and judging, different control logics is selected according to duty requirements, then send control signal to correspondence connection valve group, thus change the on off operating mode of Proportional valve in each valve group, thus realize the action of hydraulic control final controlling element, in the process of non-athletic state, the O corresponding with conventional valve, H, Y, K, M, P, J, C, N-type Median Function can be realized by changing different control signal.
The invention has the beneficial effects as follows: the present invention only need by existing height response electro-hydraulic proportional valve, pressure-compensated valve, shuttle valve and one-way valve carry out organic assembling, do not need according to hydraulic actuator valve body, spool carries out particular design, processing, therefore its structure composition is simple, easy to process, small lot customized production is changed into production in enormous quantities, while guaranteed performance, achieve comparatively considerable economic benefit, in addition, interchangeability of the present invention is strong, in the valve control hydraulic system needing assignment of traffic and induced pressure to have nothing to do, can effectively replace, hydraulic system after replacement not only has the irrelevant function of assignment of traffic and induced pressure, and have import and export oil circuit independently control, Median Function arbitrarily regulates and high responsiveness energy,
Accompanying drawing explanation
Fig. 1 is the integrated valve schematic diagram that throttling limit that assignment of traffic and induced pressure have nothing to do independently controls;
Fig. 2 is the integrated valve hydraulic system applications schematic diagram that throttling limit that assignment of traffic and induced pressure have nothing to do independently controls;
Fig. 3 is the integrated valve hydraulic system applications theory diagram that throttling limit that assignment of traffic and induced pressure have nothing to do independently controls.
In above-mentioned accompanying drawing, 1. an oil hydraulic cylinder, 2. the height that the throttling limit that assignment of traffic and induced pressure have nothing to do independently controls responds integrated valve group, 3. one first shuttle valve, 4. one first pressure-compensated valve, 5. one second shuttle valve, 6. one second pressure-compensated valve, 7. one first one-way valve, 8. one second one-way valve, 9. one first bi-bit bi-pass electro-hydraulic proportional valve, 10. one second bi-bit bi-pass electro-hydraulic proportional valve, 11. 1 3rd bi-bit bi-pass electro-hydraulic proportional valves, 12. 1 4th bi-bit bi-pass electro-hydraulic proportional valves, 13. 1 5th bi-bit bi-pass electro-hydraulic proportional valves, 14. variable displacement pumps, 15. bigeminy the 3rd bi-bit bi-pass electro-hydraulic proportional valve, 16. bigeminy the 4th bi-bit bi-pass electro-hydraulic proportional valve, 17. bigeminy the 5th bi-bit bi-pass electro-hydraulic proportional valve, 18. bigeminy first bi-bit bi-pass electro-hydraulic proportional valves, 19. bigeminy second bi-bit bi-pass electro-hydraulic proportional valves, 20. bigeminy second one-way valves, 21. bigeminy first one-way valves, 22. two the second pressure-compensated valves, 23. bigeminy second shuttle valves, 24. two the first pressure-compensated valves, 25. bigeminy first shuttle valves, 26. bigeminy oil hydraulic cylinders.
Embodiment
Below in conjunction with accompanying drawing and concrete embodiment, the present invention will be described in more detail.
Embodiment
Fig. 1,2 is embodiments disclosed by the invention, the height that the throttling limit that this assignment of traffic and induced pressure have nothing to do independently controls responds integrated valve, comprise Multigang valve group, supply oil circuit P, oil circuit T, load-sensitive oil circuit LS, Multigang valve group shares unified supply oil circuit P, oil circuit T and load-sensitive oil circuit LS, and each connection valve group has two output oil ports be connected with hydraulic actuator; Described Multigang valve group comprises two valve groups, is respectively the first valve group and the second valve group, and the structure composition often joining valve group is identical;
The first described valve group comprises five bi-bit bi-pass electro-hydraulic proportional valves, two shuttle valves, two one-way valves and two each and every one pressure-compensated valves; first connecting passage of one first bi-bit bi-pass electro-hydraulic proportional valve 9, first connecting passage of one the 4th bi-bit bi-pass electro-hydraulic proportional valve 12 is connected with the first connecting passage of one second pressure-compensated valve 6 with the first connecting passage of one first one-way valve 7, first connecting passage of one second bi-bit bi-pass electro-hydraulic proportional valve 10, first connecting passage of one the 5th bi-bit bi-pass electric-hydraulic proportion 13 valve is connected with the first connecting passage of one first pressure-compensated valve 4 with the first connecting passage of one second one-way valve 8, first connecting passage of one the 3rd bi-bit bi-pass electro-hydraulic proportional valve 11, second connecting passage of one the 4th bi-bit bi-pass electro-hydraulic proportional valve 12 is connected with oil feeding line P with the second connecting passage of one the 5th bi-bit bi-pass electro-hydraulic proportional valve 13, second connecting passage of one first bi-bit bi-pass electro-hydraulic proportional valve 9, second connecting passage of one second bi-bit bi-pass electro-hydraulic proportional valve 10 and the second connecting passage of one the 3rd bi-bit bi-pass electro-hydraulic proportional valve 11 and oil circuit T-phase connect, first of one second shuttle valve 5 compares end and is connected with the second connecting passage of one first one-way valve 7 with the second connecting passage of one second pressure-compensated valve 6, second of one second shuttle valve 5 compares end and is connected with the second connecting passage of one second one-way valve 8 with the second connecting passage of one first pressure-compensated valve 4, the output oil port of one second shuttle valve 5 compares to hold with first of one first shuttle valve 3 and is connected,
The second described valve group comprises five bi-bit bi-pass electro-hydraulic proportional valves, two shuttle valves, two one-way valves and two pressure-compensated valves; First connecting passage, first connecting passage of bigeminy the 4th bi-bit bi-pass electro-hydraulic proportional valve 16 of bigeminy first bi-bit bi-pass electro-hydraulic proportional valve 18 are connected with the first connecting passage of bigeminy second pressure-compensated valve 24 with the first connecting passage of bigeminy first one-way valve 21; First connecting passage, first connecting passage of bigeminy the 5th bi-bit bi-pass electro-hydraulic proportional valve 17 of bigeminy second bi-bit bi-pass electro-hydraulic proportional valve 19 are connected with the first connecting passage of bigeminy first pressure-compensated valve 22 with the first connecting passage of bigeminy second one-way valve 20; First connecting passage of bigeminy the 3rd bi-bit bi-pass electro-hydraulic proportional valve 15, the second connecting passage of bigeminy the 4th bi-bit bi-pass electro-hydraulic proportional valve 16 are connected with supply oil circuit P with the second connecting passage of bigeminy the 5th bi-bit bi-pass electro-hydraulic proportional valve 17; Second connecting passage of the second connecting passage of bigeminy first bi-bit bi-pass electro-hydraulic proportional valve 18, the second connecting passage of bigeminy second bi-bit bi-pass electro-hydraulic proportional valve 19 and one the 3rd bi-bit bi-pass electro-hydraulic proportional valve 15 and oil circuit T-phase connect; First of bigeminy second shuttle valve 23 compares end and is connected with the second connecting passage of bigeminy first one-way valve 21 with the second connecting passage of bigeminy second pressure-compensated valve 24; Second of bigeminy second shuttle valve 23 compares end and is connected with the second connecting passage of bigeminy second one-way valve 20 with the second connecting passage of bigeminy first pressure-compensated valve 22; The output oil port of bigeminy second shuttle valve 23 compares to hold with first of bigeminy first shuttle valve 25 and is connected; Second of bigeminy first shuttle valve 25 compares end and is connected with load-sensitive oil circuit LS;
Second of one first shuttle valve 3 compares end and is connected with the output oil port of the first shuttle valve 25 of bigeminy, and the output oil port of one first shuttle valve 3, the control port of one first pressure-compensated valve 4, the control port of one second pressure-compensated valve 6, the control port of bigeminy first pressure-compensated valve 22 are connected with load-sensitive oil circuit LS with the control port of bigeminy second pressure-compensated valve 24.
Composition graphs 2, 3 illustrate that height that the throttling limit that assignment of traffic and induced pressure have nothing to do independently controls responds the workflow of integrated valve: variable displacement pump 14 provides power for whole hydraulic system, the master input device of each connection is to controller input signal, after controller receives signal, carry out processing and judging, different control logics is selected according to duty requirements, then control signal is sent to correspondence connection valve group, thus change the on off operating mode of Proportional valve in each valve group, thus realize the action of hydraulic control final controlling element, in the process of non-athletic state, the O corresponding with conventional valve can be realized by changing different control signal, H, Y, K, M, P, J, C, N-type Median Function.
The hydraulic work system state that height that throttling limit that assignment of traffic and induced pressure have nothing to do independently controls responds integrated valve is entered: for first, second is identical with the first control logic according to table 1 application; When the one second and the 4th bi-bit bi-pass electro-hydraulic proportional valve 10 and 12 is opened simultaneously, when the one first, the 3rd and the 5th bi-bit bi-pass electro-hydraulic proportional valve 9,11 and 13 cuts out simultaneously, the piston rod of oil hydraulic cylinder 1 is protruding; When the one second and the 5th bi-bit bi-pass electro-hydraulic proportional valve 9 and 13 is opened simultaneously, when second, third and a 4th bi-bit bi-pass electro-hydraulic proportional valve 10,11 and 12 cuts out simultaneously, the piston rod of oil hydraulic cylinder 1 is to retraction; When five first, second, third, fourth and fifth bi-bit bi-pass electro-hydraulic proportional valves 9,10,11,12 and 13 Close All, realize O type Median Function; When one first, second, the 4th and the 5th bi-bit bi-pass electro-hydraulic proportional valve 9,10,12 and 13 opens simultaneously, when one the 3rd bi-bit bi-pass electro-hydraulic proportional valve 11 cuts out, realizes H type Median Function; When one first and second bi-bit bi-pass electro-hydraulic proportional valve 9 and 10 is opened simultaneously, when the one the 3rd, the 4th and the 5th bi-bit bi-pass electro-hydraulic proportional valve 11,12 and 13 cuts out simultaneously, realize Y type Median Function; When the one first and the 4th bi-bit bi-pass electro-hydraulic proportional valve 9 and 12 is opened simultaneously, when second, third and a 5th bi-bit bi-pass electro-hydraulic proportional valve 10,11 and 13 cuts out simultaneously, realize K type Median Function; When one the 3rd bi-bit bi-pass electro-hydraulic proportional valve 11 is opened, one first, second, the 4th and the 5th bi-bit bi-pass electro-hydraulic proportional valve 9,10,12 and 13 is when cutting out simultaneously, realizes M type Median Function; When the one the 4th and the 5th bi-bit bi-pass electro-hydraulic proportional valve 12 and 13 is opened simultaneously, when one first, second, and third bi-bit bi-pass electro-hydraulic proportional valve 9,10 and 11 cuts out simultaneously, realize P type Median Function; When one second bi-bit bi-pass electro-hydraulic proportional valve 10 is opened, when the one first, the 3rd, the 4th and the 5th bi-bit bi-pass electro-hydraulic proportional valve 9,11,12 and 13 cuts out simultaneously, realize J type Median Function; When one the 3rd bi-bit bi-pass electro-hydraulic proportional valve 11 is opened, one first, second, the 4th and the 5th bi-bit bi-pass electro-hydraulic proportional valve 9,10,12 and 13 is when cutting out simultaneously, realizes C type Median Function; When one first bi-bit bi-pass electro-hydraulic proportional valve 9 is opened, one second, third, the 4th and the 5th bi-bit bi-pass electro-hydraulic proportional valve 10,11,12 and 13 is when cutting out simultaneously, realizes N-type Median Function.
The height that the throttling limit that table 1 assignment of traffic and induced pressure have nothing to do independently controls responds integrated valve action and the list of meta functional realiey
Claims (1)
1. the integrated valve that the throttling limit that an assignment of traffic and induced pressure have nothing to do independently controls, it is characterized in that: it comprises Multigang valve group, supply oil circuit P, oil circuit T, load-sensitive oil circuit LS, described Multigang valve group shares unified supply oil circuit P, oil circuit T and load-sensitive oil circuit LS, described Multigang valve group comprises N number of valve group, be respectively the first valve group, second valve group, N – 1 valve group, N joins valve group, here N be more than or equal to 2 natural number, the first described valve group, second valve group, N – 1 valve group, N joins valve group and has identical composition structure, and have two output oil ports be connected with hydraulic actuator, the first described valve group comprises five bi-bit bi-pass electro-hydraulic proportional valves, two shuttle valves, two one-way valves and two pressure-compensated valves, first connecting passage, first connecting passage of one the 4th bi-bit bi-pass electro-hydraulic proportional valve of one first bi-bit bi-pass electro-hydraulic proportional valve are connected with the first connecting passage of one second pressure-compensated valve with the first connecting passage of one first one-way valve, first connecting passage, first connecting passage of one the 5th bi-bit bi-pass electro-hydraulic proportional valve of one second bi-bit bi-pass electro-hydraulic proportional valve are connected with the first connecting passage of one first pressure-compensated valve with the first connecting passage of one second one-way valve, first connecting passage of one the 3rd bi-bit bi-pass electro-hydraulic proportional valve, the second connecting passage of one the 4th bi-bit bi-pass electro-hydraulic proportional valve are connected with supply oil circuit P with the second connecting passage of one the 5th bi-bit bi-pass electro-hydraulic proportional valve, second connecting passage of the second connecting passage of one first bi-bit bi-pass electro-hydraulic proportional valve, the second connecting passage of one second bi-bit bi-pass electro-hydraulic proportional valve and one the 3rd bi-bit bi-pass electro-hydraulic proportional valve and oil circuit T-phase connect, first of one second shuttle valve compares end and is connected with the second connecting passage of one first one-way valve with the second connecting passage of one second pressure-compensated valve, second of one second shuttle valve compares end and is connected with the second connecting passage of one second one-way valve with the second connecting passage of one first pressure-compensated valve, the output oil port of one second shuttle valve compares to hold with first of one first shuttle valve and is connected, second of one first shuttle valve compares end and is connected with the output oil port of bigeminy first shuttle valve, and the output oil port of one first shuttle valve, the control port of one first pressure-compensated valve are connected with load-sensitive oil circuit LS with the control port of one second pressure-compensated valve,
Second of bigeminy first shuttle valve of the second valve group compares end and is connected with the output oil port of 3 first shuttle valves of the 3rd valve group; By that analogy, the N-1 that N-1 joins valve group joins second of the first shuttle valve and compares the output oil port that N that end and N join valve group joins the first shuttle valve and be connected, and the N that N joins valve group joins second of the first shuttle valve and compares to hold and be connected with load-sensitive oil circuit LS; The control port that output oil port and the N of one first shuttle valve join valve first pressure-compensated valve is connected with the control port that N joins the second pressure-compensated valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410765008.7A CN104481953B (en) | 2014-12-12 | 2014-12-12 | The pile-up valve that independently controls of throttling limit that assignment of traffic is unrelated with load pressure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410765008.7A CN104481953B (en) | 2014-12-12 | 2014-12-12 | The pile-up valve that independently controls of throttling limit that assignment of traffic is unrelated with load pressure |
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| CN104481953A true CN104481953A (en) | 2015-04-01 |
| CN104481953B CN104481953B (en) | 2016-06-15 |
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| CN201410765008.7A Active CN104481953B (en) | 2014-12-12 | 2014-12-12 | The pile-up valve that independently controls of throttling limit that assignment of traffic is unrelated with load pressure |
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| CN105422533A (en) * | 2015-11-25 | 2016-03-23 | 贵州詹阳动力重工有限公司 | Multi-functional hydraulic output platform of excavator |
| CN106321539A (en) * | 2015-06-24 | 2017-01-11 | 徐工集团工程机械股份有限公司 | Method and system for electric proportional flow quantity distribution |
| CN108317119A (en) * | 2018-04-09 | 2018-07-24 | 徐州燕大传动与控制技术有限公司 | A kind of proportional multi-way valve that hydraulic control inlet and outlet throttling side can be separately adjustable |
| CN108412829A (en) * | 2018-04-09 | 2018-08-17 | 徐州燕大传动与控制技术有限公司 | A kind of separately adjustable load-sensitive formula multi-way valve of inlet and outlet throttling side energy |
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Effective date of registration: 20171122 Address after: 100000, A, building 11, building 30, 302 Xing Xing street, Beijing, Shijingshan District Patentee after: Beijing North Liyuan Hydraulic Transmission Machinery Co., Ltd. Address before: Hebei Street West Harbor area, 066004 Hebei city of Qinhuangdao province No. 438 Patentee before: Yanshan University |
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Address after: 302, 303, building 11, yard 30, Shixing street, Shijingshan District, Beijing Patentee after: Beijing North Liyuan intelligent Polytron Technologies Inc. Address before: Room 302, block a, building 11, yard 30, Shixing street, Shijingshan District, Beijing Patentee before: Beijing North Liyuan Hydraulic Transmission Machinery Co.,Ltd. |
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Denomination of invention: Integrated valve with independent control of throttling edge and flow distribution independent of load pressure Effective date of registration: 20210202 Granted publication date: 20160615 Pledgee: Wuxi rural commercial bank Limited by Share Ltd. Pledgor: Beijing North Liyuan intelligent Polytron Technologies Inc. Registration number: Y2021990000142 |