CN105626615A - Steering feedback type flow amplification valve - Google Patents
Steering feedback type flow amplification valve Download PDFInfo
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- CN105626615A CN105626615A CN201610108016.3A CN201610108016A CN105626615A CN 105626615 A CN105626615 A CN 105626615A CN 201610108016 A CN201610108016 A CN 201610108016A CN 105626615 A CN105626615 A CN 105626615A
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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
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Servomotors (AREA)
Abstract
The invention relates to the hydraulic technology, in particular to a steering feedback type flow amplification valve. The valve comprises a valve body, a reversing valve and a three-way flow compensation valve are arranged in the valve body, and the valve body is provided with an oil inlet P, an oil returning opening T, a working opening A, a working opening B, a guidance level control opening a, a guidance level control opening b, and an oil opening PF; an LS channel for collecting oil pressure of a working cavity A and oil pressure of a working cavity B is arranged in a reversing valve element; and a load feedback cavity is formed in the valve body and is communicated with a spring cavity of the three-way flow compensation valve through a load feedback hole. Through the LS channel arranged inside the reversing valve element, the relation between the spring cavity of the three-way flow compensation valve and the working cavity A/B is built; and according to the opening degree of a throttle groove of the reversing valve element, the flow corresponding to the steering degree is output, and precise steering is achieved. The LS channel is arranged inside the reversing valve element, the valve body structure is greatly simplified, and the structure is compact and reliable.
Description
Technical field
The present invention relates to technical field of hydraulic pressure, particularly relate to a kind of be applied to engineering machinery hydraulic steering turn to feedback-type flux amplification valve.
Background technology
Steering hydraulic system is one of of paramount importance system in wheel loader, and it directly affects the safety of complete machine, working performance, energy resource consumption and operation comfort. Flux amplification valve is widely used in big-and-middle-sized engineering machinery especially loading machine steering hydraulic system, its effect is that the pilot control flow that steering gear is exported carries out flow according to certain amplification and hydraulic power amplifies, control the motion of steering hydraulic executive component, the advantage with energy Appropriate application system power, and handle steadily light, compact conformation, application on loader is more and more extensive, it has also become the main flow direction of current steering development. But loading machine steering system also exists following drawback at present: 1, under non-steering situation, as long as steering cylinder there being oil pressure exist, loader hydraulic system will at corresponding high pressure kicks, the shortcoming such as cause that system energy consumption is big, temperature rise, steering pump life-span are low, thus reducing system work efficiency, cause that the problem of Hydraulic System Fever and digging force, pull strength instability produces; 2, starting moment vibration, the problem such as vibration, stop timing vibration of creeping, cause that loader operation comfortableness is poor, steering there is also the problem that high and low rotating speed is inconsistent simultaneously; 3, in the steering gear of pilot control part position adopt be O type rotary valve function principle, namely steering gear is in middle position when not working, the guide's oil pocket amplifying spool two ends is to close, it is likely to result in pocketed oil when therefore amplifying spool return to build the pressure phenomenon, affect the accuracy of course changing control, there will be loader time serious and low damage phenomenon occurs, cause potential safety hazard; 4, owing to the pilot control area variable gradient at amplification spool two ends is non-linear so that output is also non-linear to the changes in flow rate of steering cylinder, cause that loader goes out to turn now to potential safety hazards such as " unstable " when walking at a high speed.
Summary of the invention
For the problems referred to above, it is an object of the invention to provide a kind of compact conformation, turn to and reliably turn to feedback-type flux amplification valve smoothly.
For reaching above-mentioned purpose, the scheme that the present invention takes is: one turns to feedback-type flux amplification valve, include valve body, reversal valve it is provided with in valve body, three-way flowrate recuperation valve, valve body arranges oil inlet P, oil return inlet T, working hole A, working hole B, pilot stage controls mouth a, pilot stage controls mouth b, hydraulic fluid port PF, oil inlet P is by the oil suction chamber of three-way flowrate recuperation valve connection reversal valve, the oil back chamber of oil return inlet T connection reversal valve, working hole A and working hole B is respectively communicated with the working chamber A and working chamber B of reversal valve, pilot stage controls mouth a and pilot stage controls mouth b and is respectively communicated with pilot stage left control end and the right control end of pilot stage of reversal valve, the load-sensitive LS passage of collecting work chamber A and working chamber B oil pressure it is provided with in described change-over valve core, valve body is provided with load feedback chamber, and load feedback chamber is connected with three-way flowrate recuperation valve spring cavity by load feedback hole, when not turning to, reversal valve is in middle position, and load-sensitive LS passage, load feedback chamber all connect with oil return inlet T, and oil inlet P turns on hydraulic fluid port PF, when turning to, pilot stage controls mouth a/b and promotes reversal valve to be in left/right position, and working chamber A/B is connected with three-way flowrate recuperation valve spring cavity by load-sensitive LS passage, load feedback chamber, load feedback hole, and oil inlet P turns on B/A working hole.
Described load-sensitive LS passage includes LS axially extending bore, LS radial direction through hole, A chamber oil pressure feedback hole and B chamber oil pressure feedback hole; LS axially extending bore axially penetrates through change-over valve core, LS radial direction through hole connection load feedback chamber and LS axially extending bore, A chamber oil pressure feedback hole extends radially through change-over valve core with B chamber oil pressure feedback hole and connects with LS axially extending bore, when reversal valve is in middle position, working chamber A, working chamber B separate with A chamber oil pressure feedback hole, B chamber oil pressure feedback hole respectively; When reversal valve is in left/right position, working chamber A/B passes sequentially through A/B chamber oil pressure feedback hole, LS axially extending bore, LS radial direction through hole connect with load feedback chamber.
Described change-over valve core is provided with left meter in groove and right meter in groove, and oil inlet P passes sequentially through three-way flowrate compensating spool, the oil suction chamber of reversal valve, left/right meter in groove connect with working chamber A/B.
Described pilot stage is controlled mouth a and is connected by the balance pipe on end cap with pilot stage control mouth b.
Described change-over valve core is provided with off-load annular groove, and load feedback chamber is provided with the first off-load limit, second unloads limit, and when reversal valve is in middle position, there is positive opening amount on reversing valve core off-load annular groove and the first off-load limit, the second off-load limit.
Described change-over valve core is provided with K type pilot control throttling channel, is provided with pilot control oil back chamber in valve body, and spool left/right moves rear pilot control throttling channel and connects with pilot control oil back chamber.
Described working hole A and working hole B respectively and is connected to overload oil compensating valve between oil return inlet T.
It is connected to overflow valve between spring cavity and the oil return inlet T of described three-way flowrate recuperation valve.
Beneficial effects of the present invention:
(1) by being arranged on contacting of load-sensitive LS Path Setup three-way flowrate recuperation valve spring cavity change-over valve core within and working chamber A/B, when steering gear rotates, change-over valve core commutates toward left/right, pilot stage controls the load pressure of mouth and is delivered to three-way flowrate recuperation valve spring cavity by load-sensitive LS passage, recuperation valve makes pressure reduction before and after change-over valve core throttling channel constant, aperture according to change-over valve core throttling channel, the flow exporting with turning to degree corresponding, it is achieved precisely turn to.
(2) load-sensitive LS passage is arranged on inside change-over valve core, without setting up feedback runner at valve inner, and A chamber oil pressure feedback hole and B chamber oil pressure feedback hole are also disposed on change-over valve core so that the chamber number of change valve reduces, enormously simplify valve body structure, compact conformation is reliable.
(3) when steering gear does not turn to, reversal valve is in middle position, load-sensitive LS passage and oil back chamber T UNICOM, channel pressure is close to zero, feeding back to three-way flowrate compensating spool spring cavity, oil inlet P is with relatively low pressure (about 0.3MPa) off-load to hydraulic fluid port PF, bit-loss in nothing.
(4) pilot stage left/right is controlled end and is connected by balance pipe, and rotation problem when solution turns to by no means walking eliminates safe hidden trouble.
(5) controlling throttling channel is K shape groove, area gradient linearly changes, left/right meter in groove is coordinated to carry out Flow amplification according to setting magnification ratio, commutation pressure gradually rises to live load pressure from low pressure, avoid the occurrence of because flow step causes turning to unstable phenomenon, smooth operation relaxes, and Consumer's Experience is high.
Accompanying drawing explanation
Fig. 1 is regular flow amplifying valve structure sectional view;
Fig. 2 is Figure 1B to figure;
Fig. 3 is regular flow amplifying valve hydraulic schematic diagram;
Fig. 4 is embodiment of the present invention structure chart;
Fig. 5 is that the embodiment of the present invention turns to schematic diagram when not working;
Fig. 6 is embodiment of the present invention schematic diagram when turning to work;
Fig. 7 is embodiment of the present invention hydraulic schematic diagram.
Description of symbols in figure:
I reversal valve, II three-way flowrate recuperation valve
1 valve body, 2 LS axially extending bores, 3 drive end bearing brackets, the 4 left control ends of pilot stage, 5 pilot control throttling channels, the 6 left oil back chambers of pilot control, 7 left oil back chambers, 8 meter out grooves, 9 working chamber A, 10 A chamber oil pressure feedback holes, 11 left meter in grooves, 12 oil suction chambers, 13 right meter in grooves, 14 B chamber oil pressure feedback holes, 15 working chamber B, 16 right oil back chambers, 17 first off-load limits, the 18 left shoulders of off-load annular groove, 19 second off-load limits, the 20 right shoulders of off-load annular groove, 21 LS radial direction through hole, 22 rear end caps, the 23 right control ends of pilot stage, the 24 right oil back chambers of pilot control, 25 spring cavitys, 26 load feedback holes, 27 load feedback chambeies, 28 counterbalance springs, 29 three-way flowrate compensating spools, 30 balance pipes, 31 change-over valve cores, 32 shuttle valves.
Detailed description of the invention
For being more fully understood that the present invention, below in conjunction with the drawings and specific embodiments, technical scheme is further described.
As shown in Figures 4 to 7, feedback-type flux amplification valve is turned to by of the invention process, integrated in its valve body it is provided with reversal valve I, three-way flowrate recuperation valve II, is provided with oil inlet P, oil return inlet T, working hole A, working hole B, pilot stage controls mouth a, pilot stage controls mouth b, hydraulic fluid port PF. Oil inlet P connects the oil suction chamber of reversal valve I by oil suction chamber 12. The left oil back chamber 7 of oil return inlet T connection reversal valve I and right oil back chamber 16, working hole A and working hole B are respectively communicated with the working chamber A and working chamber B15 of reversal valve I. Described working hole A and working hole B respectively and is connected to overflow valve and Fill valve that check valve composes in parallel between oil return inlet T, the oil-in of check valve is connected with oil return inlet T. It is connected to overflow valve between control end and the oil return inlet T of described three-way flowrate recuperation valve.
Pilot stage controls mouth a, pilot stage controls mouth b and connects pilot stage left control end 4 and the right control end 23 of pilot stage of reversal valve I respectively, change-over valve core 31 end is provided with pilot control throttling channel 5 near the left control end 4 of pilot stage, the left oil back chamber of pilot control 6 and the left oil back chamber 24 of pilot control it is provided with in valve body 1, after change-over valve core 31 is moved to the left, pilot control throttling channel 5 connects with pilot control oil back chamber 6. Owing to pilot control throttling channel 5 area gradient linearly changes, commutation pressure gradually rises to live load pressure from low pressure, it is to avoid occur causing turning to unstable phenomenon because of flow step. Pilot stage left control end 4 is connected by balance pipe 30 with the right control end 23 of pilot stage, solves parking autobiography problem, eliminates safe hidden trouble.
Being provided with the load-sensitive LS passage of collecting work chamber A and working chamber B oil pressure in described change-over valve core 31, load-sensitive LS passage includes LS axially extending bore 2, LS radial direction through hole 21, A chamber oil pressure feedback hole 10 and B chamber oil pressure feedback hole 14. LS axially extending bore 2 axially penetrates through change-over valve core 31, LS radial direction through hole 21 connects load feedback chamber 27 and LS axially extending bore 2, A chamber oil pressure feedback hole 10 and B chamber oil pressure feedback hole 14 extend radially through change-over valve core 31, connect with LS axially extending bore 2, for the pressure of collecting work chamber A9 and working chamber B15. It is internal that load-sensitive LS passage is arranged on change-over valve core 31, without setting up feedback oil duct at valve inner, and left meter in groove 11 and right meter in groove 13 are also disposed on change-over valve core 31, the inner chamber number making change valve reduces, simplifying valve body structure, whole valve arrangement is compact reliably.
Change valve is provided with load feedback chamber 27, and change-over valve core 31 axially penetrates through load feedback chamber 27, closing, left side opening, opening and the unloading zones slot fit being arranged on spool on the right side of load feedback chamber 27. Off-load annular groove is made up of the right shoulder 20 of the left shoulder of off-load annular groove 18 and off-load annular groove, off-load limit relative aperture off-load big about the 0.01mm of annular groove shoulder. Change-over valve core 31 is in middle position, and off-load annular groove separates with off-load limit, and right oil back chamber 16 connects with load feedback chamber 27, and pressure is close to zero. When change-over valve core 31 is in right/left position, off-load annular groove coordinates with off-load limit, and working chamber A9/ working chamber B passes sequentially through oil pressure feedback hole 10/B chamber, A chamber oil pressure feedback hole 14, LS axially extending bore 2, LS radial direction through hole 21 connect with load feedback chamber 27. Load feedback chamber 27 is connected with spring cavity 25 by load feedback hole 26.
Being additionally provided with left meter in groove 11 and right meter in groove 13 on described change-over valve core 31, oil inlet P passes sequentially through oil suction chamber 12, the right meter in groove 13 of left meter in groove 11/ connects with working chamber A9/ working chamber B15. Change-over valve core 31 is turned left/is moved right, pilot stage controls the load pressure of mouth and is delivered to spring cavity 25 by load-sensitive LS passage, the aperture of the right meter in groove 13 of left meter in groove 11/, the flow exporting with turning to degree corresponding, it is achieved precisely turn to is controlled according to load pressure.
The course of action of the present invention is: when not turning to, and change-over valve core 31 is in middle position, and load-sensitive LS passage is linked up with oil back chamber T, channel pressure is close to zero, feeding back to spring cavity 25, oil inlet P is with very low pressure (about 0.3MPa) off-load to hydraulic fluid port PF, bit-loss in nothing. And position pressure is the high pressure suppressed in steering cylinder at that time in tradition flux amplification valve.
During right turn, guide's fluid flows into the left control end 4 of pilot stage from through drive end bearing bracket 3, promotes change-over valve core 31 toward moving right, so that pilot control throttling channel 5 communicates with the left oil back chamber 6 of pilot control flows back to fuel tank. And change-over valve core 31 is turned right mobile further, the first off-load limit 17 coordinates closing passage with the left shoulder 18 of off-load annular groove. B chamber oil pressure feedback hole 14 communicates with working chamber B15, through LS axially extending bore 2, LS radial direction through hole 21, oil pressure is guided to load feedback chamber 27, guides in spring cavity 25 again through load feedback hole 26. Promote three-way flowrate compensating spool 29 toward moving left, turn down the throttling channel of three-way flowrate compensating spool 29, make P mouth pressure be gradually increased to ratio and turn to the high certain pressure (about 0.3MPa) of working chamber B15. When change-over valve core 31 is further toward moving right, right meter in groove 13 communicates with working chamber B15, and fluid flows into steering cylinder through right meter in groove 13, it is achieved the fluid-link steering action of working host. Change-over valve core 31 is further toward moving right, until when commutation displacement is corresponding with the speed of steering wheel rotation, being maintained at this position, normal operation. When turning to, oil suction chamber P pressure is to be gradually increased to higher about 0.3MPa than steering load pressure from standby low pressure (0.3MPa), thus turn to when beginning to turn on, before and after right meter in groove 13, pressure differential is about about 0.3MPa, do not have pressure reduction bigger when former regular flow amplifying valve initially commutates, the phenomenon that steering flow is unstable suddenly occurs. Turn left identical with the course of action principle that turns right, repeat no more.
Claims (8)
1. one kind turns to feedback-type flux amplification valve, include valve body, reversal valve it is provided with in valve body, three-way flowrate recuperation valve, valve body arranges oil inlet P, oil return inlet T, working hole A, working hole B, pilot stage controls mouth a, pilot stage controls mouth b, hydraulic fluid port PF, oil inlet P is by the oil suction chamber of three-way flowrate recuperation valve connection reversal valve, the oil back chamber of oil return inlet T connection reversal valve, working hole A and working hole B is respectively communicated with the working chamber A and working chamber B of reversal valve, pilot stage controls mouth a and pilot stage controls mouth b and is respectively communicated with pilot stage left control end and the right control end of pilot stage of reversal valve, it is characterized in that: in described change-over valve core, be provided with the load-sensitive LS passage of collecting work chamber A and working chamber B oil pressure, valve body is provided with load feedback chamber, and load feedback chamber is connected with three-way flowrate recuperation valve spring cavity by load feedback hole, when not turning to, reversal valve is in middle position, and load-sensitive LS passage, load feedback chamber all connect with oil return inlet T, and oil inlet P turns on hydraulic fluid port PF, when turning to, pilot stage controls mouth a/b and promotes reversal valve to be in left/right position, and working chamber A/B is connected with three-way flowrate recuperation valve spring cavity by load-sensitive LS passage, load feedback chamber, load feedback hole, and oil inlet P turns on working hole B/A.
2. according to claim 1 turn to feedback-type flux amplification valve, it is characterised in that: described load-sensitive LS passage includes LS axially extending bore, LS radial direction through hole, A chamber oil pressure feedback hole and B chamber oil pressure feedback hole; LS axially extending bore axially penetrates through change-over valve core, LS radial direction through hole connection load feedback chamber and LS axially extending bore, A chamber oil pressure feedback hole extends radially through change-over valve core with B chamber oil pressure feedback hole and connects with LS axially extending bore, when reversal valve is in middle position, working chamber A, working chamber B separate with A chamber oil pressure feedback hole, B chamber oil pressure feedback hole respectively; When reversal valve is in left/right position, working chamber A/B passes sequentially through A/B chamber oil pressure feedback hole, LS axially extending bore, LS radial direction through hole connect with load feedback chamber.
3. according to claim 1 and 2 turn to feedback-type flux amplification valve, it is characterized in that: described change-over valve core is provided with left meter in groove and right meter in groove, oil inlet P passes sequentially through three-way flowrate compensating spool, the oil suction chamber of reversal valve, left/right meter in groove connect with working chamber A/B.
4. according to claim 1 turn to feedback-type flux amplification valve, it is characterised in that: described pilot stage is controlled mouth a and controls mouth b with pilot stage and connected by the balance pipe on end cap.
5. according to claim 1 turn to feedback-type flux amplification valve, it is characterized in that: described change-over valve core is provided with off-load annular groove, load feedback chamber is provided with the first off-load limit, second unloads limit, when reversal valve is in middle position, there is positive opening amount on reversing valve core off-load annular groove and the first off-load limit, the second off-load limit.
6. according to claim 1 turn to feedback-type flux amplification valve, it is characterized in that: described change-over valve core is provided with K type pilot control throttling channel, being provided with pilot control oil back chamber in valve body, spool left/right moves rear pilot control throttling channel and connects with pilot control oil back chamber.
7. according to claim 1 turn to feedback-type flux amplification valve, it is characterised in that: described working hole A and working hole B respectively and is connected to overload oil compensating valve between oil return inlet T.
8. according to claim 1 turn to feedback-type flux amplification valve, it is characterised in that: it is connected to overflow valve between spring cavity and the oil return inlet T of described three-way flowrate recuperation valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610108016.3A CN105626615A (en) | 2016-02-29 | 2016-02-29 | Steering feedback type flow amplification valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610108016.3A CN105626615A (en) | 2016-02-29 | 2016-02-29 | Steering feedback type flow amplification valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105626615A true CN105626615A (en) | 2016-06-01 |
Family
ID=56041852
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610108016.3A Pending CN105626615A (en) | 2016-02-29 | 2016-02-29 | Steering feedback type flow amplification valve |
Country Status (1)
| Country | Link |
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| CN (1) | CN105626615A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107725523A (en) * | 2017-11-14 | 2018-02-23 | 江苏恒立液压科技有限公司 | Load sensing multi-way valve and there is its engineering machinery |
| CN108150676A (en) * | 2018-02-05 | 2018-06-12 | 江苏恒立液压科技有限公司 | Multi-way valve |
| CN112287498A (en) * | 2020-10-27 | 2021-01-29 | 哈尔滨工程大学 | Numerical simulation research method for valve core opening of three-way spring valve |
| CN113931892A (en) * | 2021-09-28 | 2022-01-14 | 中联重科股份有限公司 | Load-sensitive multi-way valve with independently controlled load port and hydraulic system |
| CN114576228A (en) * | 2022-05-06 | 2022-06-03 | 英轩重工有限公司 | Flow amplifying valve and steering hydraulic control system thereof |
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| US4716933A (en) * | 1986-10-16 | 1988-01-05 | J. I. Case Company | Valve unit |
| CN1361362A (en) * | 2000-12-28 | 2002-07-31 | 浙江临海海宏集团有限公司 | Priority-type flow rate enlarging and merging valve |
| CN201818577U (en) * | 2010-10-22 | 2011-05-04 | 浙江海宏液压科技股份有限公司 | Preferential type flow amplifier valve |
| CN202176565U (en) * | 2011-08-05 | 2012-03-28 | 浙江海宏液压科技股份有限公司 | Flow amplifying valve |
| CN104029722A (en) * | 2014-01-23 | 2014-09-10 | 广西柳工机械股份有限公司 | Hydraulic steering system of engineering machine |
| CN204082733U (en) * | 2014-07-16 | 2015-01-07 | 浙江海宏液压科技股份有限公司 | Preference type flux amplification valve |
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- 2016-02-29 CN CN201610108016.3A patent/CN105626615A/en active Pending
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US4716933A (en) * | 1986-10-16 | 1988-01-05 | J. I. Case Company | Valve unit |
| CN1361362A (en) * | 2000-12-28 | 2002-07-31 | 浙江临海海宏集团有限公司 | Priority-type flow rate enlarging and merging valve |
| CN201818577U (en) * | 2010-10-22 | 2011-05-04 | 浙江海宏液压科技股份有限公司 | Preferential type flow amplifier valve |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107725523A (en) * | 2017-11-14 | 2018-02-23 | 江苏恒立液压科技有限公司 | Load sensing multi-way valve and there is its engineering machinery |
| CN107725523B (en) * | 2017-11-14 | 2023-12-15 | 江苏恒立液压科技有限公司 | Load-sensitive multiway valve and engineering machinery with same |
| CN108150676A (en) * | 2018-02-05 | 2018-06-12 | 江苏恒立液压科技有限公司 | Multi-way valve |
| CN112287498A (en) * | 2020-10-27 | 2021-01-29 | 哈尔滨工程大学 | Numerical simulation research method for valve core opening of three-way spring valve |
| CN112287498B (en) * | 2020-10-27 | 2022-05-20 | 哈尔滨工程大学 | Numerical simulation research method for valve core opening degree of three-way spring valve |
| CN113931892A (en) * | 2021-09-28 | 2022-01-14 | 中联重科股份有限公司 | Load-sensitive multi-way valve with independently controlled load port and hydraulic system |
| CN113931892B (en) * | 2021-09-28 | 2022-06-14 | 中联重科股份有限公司 | Load-sensitive multi-way valve with independently controlled load port and hydraulic system |
| CN114576228A (en) * | 2022-05-06 | 2022-06-03 | 英轩重工有限公司 | Flow amplifying valve and steering hydraulic control system thereof |
| CN114576228B (en) * | 2022-05-06 | 2022-07-22 | 英轩重工有限公司 | Flow amplifying valve and steering hydraulic control system thereof |
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| C06 | Publication | ||
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| CB02 | Change of applicant information | ||
| CB02 | Change of applicant information |
Address after: 317000 358, zhe Road, Dayang street, Taizhou, Zhejiang. Applicant after: Zhejiang Gaoyu Hydraulic Mechanical and Electrical Co., Ltd. Address before: 317000 No. 358, extension Road, Dayang street, Taizhou, Zhejiang. Applicant before: Zhejiang Gaoyu Hydraulic Mechanical and Electrical Co., Ltd. |
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| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20160601 |