CN108980126A - A kind of synchronization hydraulic system of meter out - Google Patents
A kind of synchronization hydraulic system of meter out Download PDFInfo
- Publication number
- CN108980126A CN108980126A CN201810991811.0A CN201810991811A CN108980126A CN 108980126 A CN108980126 A CN 108980126A CN 201810991811 A CN201810991811 A CN 201810991811A CN 108980126 A CN108980126 A CN 108980126A
- Authority
- CN
- China
- Prior art keywords
- valve
- fluid port
- hydraulic fluid
- proportional reversing
- way proportional
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/22—Synchronisation of the movement of two or more servomotors
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a kind of synchronization hydraulic systems of meter out, belong to hydraulic system field.Hydraulic system include main pump mould group, two control valve groups and with two one-to-one actuators of control valve group；Main pump mould group includes load sensitive pump and motor；Control valve group includes 3-position 4-way proportional reversing valve, shuttle valve, first check valve and valve for pressure difference, the T hydraulic fluid port of 3-position 4-way proportional reversing valve is connected to the oil inlet of valve for pressure difference, first oil inlet of shuttle valve is connected to the A hydraulic fluid port of 3-position 4-way proportional reversing valve, second oil inlet of shuttle valve is connected to the B hydraulic fluid port of 3-position 4-way proportional reversing valve, the oil outlet of shuttle valve is connected to the oil inlet of the spring cavity of valve for pressure difference and the first check valve respectively, the oil outlet of first check valve respectively with the control port of valve for pressure difference, the oil outlet of first check valve of guide's hydraulic fluid port and another control valve group of load sensitive pump is connected to.Present invention can ensure that the proportional control of the speed of service between each actuator.
Description
Technical field
The invention belongs to hydraulic system field, in particular to a kind of synchronization hydraulic system of meter out.
Background technique
In maritime platform and engineering machinery field, can typically now there be the case where multiple actuators work at the same time.In order to
Save installation space and operating cost, it will usually using the hydraulic system for driving multiple actuators by a main pump module.
However, the operating pressure and flow due to each actuator are all different, so during the work time, each actuator it
Between can generate and influence each other, it is difficult to guarantee the proportional control of the speed of service between each actuator, lead to the stabilization of hydraulic system
Property and synchronism are unable to get maintenance.
Summary of the invention
The embodiment of the invention provides a kind of synchronization hydraulic systems of meter out, it is ensured that the fortune between each actuator
The proportional control of scanning frequency degree.The technical solution is as follows:
The embodiment of the invention provides a kind of synchronization hydraulic system of meter out, the hydraulic system includes main pump mould
Group, two control valve groups and with the one-to-one actuator of described two control valve groups；
The main pump mould group includes load sensitive pump and the motor for driving the load sensitive pump；
The control valve group includes 3-position 4-way proportional reversing valve, shuttle valve, the first check valve and valve for pressure difference, for any one
The 3-position 4-way proportional reversing valve, the P hydraulic fluid port of the 3-position 4-way proportional reversing valve and the oil outlet of the load sensitive pump
Connection, the A hydraulic fluid port of the 3-position 4-way proportional reversing valve are connected to the A1 hydraulic fluid port of the corresponding actuator, the 3-position 4-way
The B hydraulic fluid port of proportional reversing valve is connected to the B1 hydraulic fluid port of the corresponding actuator, the T hydraulic fluid port of the 3-position 4-way proportional reversing valve
It is connected to the oil inlet of the valve for pressure difference, the A hydraulic fluid port of the first oil inlet of the shuttle valve and the 3-position 4-way proportional reversing valve
Connection, the second oil inlet of the shuttle valve are connected to the B hydraulic fluid port of the 3-position 4-way proportional reversing valve, the oil outlet of the shuttle valve
It is connected to respectively with the oil inlet of the spring cavity of the valve for pressure difference and first check valve, the oil outlet point of first check valve
Not with the first of the control port of the valve for pressure difference, guide's hydraulic fluid port of the load sensitive pump and another control valve group
The oil outlet of check valve is connected to, and the oil outlet of the valve for pressure difference is connected to the fuel tank of the hydraulic system.
In a kind of implementation of the invention, the control valve group further includes throttle valve, the oil inlet of the throttle valve
It is connected to the T hydraulic fluid port of the 3-position 4-way proportional reversing valve, the oil outlet of the throttle valve is connected to the fuel tank.
In another implementation of the invention, the control valve group further includes overflow valve, and the first of the overflow valve
Hydraulic fluid port is connected to the A hydraulic fluid port of the 3-position 4-way proportional reversing valve, the second hydraulic fluid port of the overflow valve and the 3-position 4-way ratio
The B hydraulic fluid port circulation of example reversal valve, the control port of the overflow valve are connected to the first hydraulic fluid port of the overflow valve, the overflow valve
Spring cavity be connected to the second hydraulic fluid port of the overflow valve.
In another implementation of the invention, the 3-position 4-way proportional reversing valve of a control valve group
Median Function is O-shaped.
In another implementation of the invention, the 3-position 4-way proportional reversing valve of a control valve group is
Solenoid valve.
In another implementation of the invention, the 3-position 4-way proportional reversing valve of another control valve group
Median Function be Y type.
In another implementation of the invention, the 3-position 4-way proportional reversing valve of another control valve group
For battery valve.
In another implementation of the invention, first actuator is hydraulic motor.
In another implementation of the invention, second actuator is hydraulic motor.
In another implementation of the invention, the main pump mould group further includes second one-way valve, and described second is unidirectional
The oil inlet of valve is connected to the oil outlet of the load sensitive pump, the oil outlet of the second one-way valve respectively with two described three
The P hydraulic fluid port connection of position four-way proportional reversing valve.
Technical solution provided in an embodiment of the present invention has the benefit that
In hydraulic system work, it is assumed that the inlet pressure of an actuator is PA2, the inlet pressure of another actuator
For PA3, and PA2> PA3, then passing through the selection of two shuttle valves, the pressure P of guide's oil port of load sensitive pumpLSWith PA2Phase
Deng.Further, the pressure of the oil outlet of load sensitive pump is PP, PP-PA2=PP-PLS.Due to the spring of load sensitive pump
The pressure of chamber is Δ P, PP=PLS+ Δ P, so, P available in conjunction with above-mentioned formulaP-PA2=Δ P a, that is to say, that control
The P mouth pressure P of the 3-position 4-way proportional reversing valve of valve group processedPWith the inlet pressure P of corresponding actuatorA2Difference be definite value.It is right
For the 3-position 4-way proportional reversing valve of another control valve group, PP-PA3=(PP+PLS)+(PLS-PA3)=Δ P+ Δ PD,
Wherein Δ PDFor PA2And PA3Difference.That is, the P mouth pressure P of the 3-position 4-way proportional reversing valve of another control valve groupPWith
The inlet pressure P of corresponding actuatorA3Difference be similarly definite value.It can be seen that the P mouth of two 3-position 4-way proportional reversing valves is pressed
Power and the inlet pressure difference of corresponding actuator are constant, and because the flow of proportional reversing valve is only logical with discharge coefficient, valve port
Pressure difference and fluid density are related before and after flow area, valve port, and in embodiments of the present invention, since pressure difference is constant before and after valve port,
So the flow of two 3-position 4-way proportional reversing valves can linear ratio control.Also, work as the discharge capacity of load sensitive pump
After reaching maximum, if continuing out big 3-position 4-way proportional reversing valve, the outlet pressure that will lead to load sensitive pump is unable to maintain that
And decline.But since the valve port of two 3-position 4-way proportional reversing valves front and back pressure difference simultaneously declines, so 3-position 4-way ratio
The flow of reversal valve also according to opening area pro rate, therefore actuator linear scale control not by load sensitive pump
The influence of flow saturation.
Detailed description of the invention
To describe the technical solutions in the embodiments of the present invention more clearly, make required in being described below to embodiment
Attached drawing is briefly described, it should be apparent that, drawings in the following description are only some embodiments of the invention, for
For those of ordinary skill in the art, without creative efforts, it can also be obtained according to these attached drawings other
Attached drawing.
Fig. 1 is the flow chart of hydraulic system provided in an embodiment of the present invention；
Each symbol indicates that meaning is as follows in figure:
1- main pump mould group, 11- load sensitive pump, 12- motor, 13- second one-way valve, 2- 3-position 4-way proportional reversing valve,
3- shuttle valve, the first check valve of 4-, 5- valve for pressure difference, 6- throttle valve, 7- overflow valve.
Specific embodiment
To make the object, technical solutions and advantages of the present invention clearer, below in conjunction with attached drawing to embodiment party of the present invention
Formula is described in further detail.
The embodiment of the invention provides a kind of synchronization hydraulic systems of meter out, as shown in Figure 1, hydraulic system includes master
Pump 1, two control valve group of mould group and with the one-to-one actuator 100 of two control valve groups；
Main pump mould group 1 includes load sensitive pump 11 and the motor 12 for driving load sensitive pump 11；
Control valve group includes 3-position 4-way proportional reversing valve 2, shuttle valve 3, the first check valve 4 and valve for pressure difference 5, for any one
The P hydraulic fluid port of 3-position 4-way proportional reversing valve 2,3-position 4-way proportional reversing valve 2 is connected to the oil outlet of load sensitive pump 11, and three
The A hydraulic fluid port of four-way proportional reversing valve 2 is connected to the A1 hydraulic fluid port of corresponding actuator 100, the B oil of 3-position 4-way proportional reversing valve 2
Mouth is connected to the B1 hydraulic fluid port of corresponding actuator 100, and the T hydraulic fluid port of 3-position 4-way proportional reversing valve 2 and the oil inlet of valve for pressure difference 5 connect
Logical, the first oil inlet of shuttle valve 3 is connected to the A hydraulic fluid port of 3-position 4-way proportional reversing valve 2, the second oil inlet of shuttle valve 3 and three
The B hydraulic fluid port of four-way proportional reversing valve 2 is connected to, the oil outlet of shuttle valve 3 respectively with the spring cavity of valve for pressure difference 5 and the first check valve 4
Oil inlet connection, the oil outlet of the first check valve 4 guide's hydraulic fluid port with the control port of valve for pressure difference 5, load sensitive pump 11 respectively
And the oil outlet connection of the first check valve 4 of another control valve group, the oil outlet of valve for pressure difference 5 and the fuel tank of hydraulic system connect
It is logical.
In hydraulic system work, it is assumed that the inlet pressure of an actuator 100 is PA2, another actuator 100 into
Mouth pressure is PA3, and PA2> PA3, then passing through the selection of two shuttle valves 3, the pressure P of guide's oil port of load sensitive pump 11LS
With PA2It is equal.Further, the pressure of the oil outlet of load sensitive pump 11 is PP, PP-PA2=PP-PLS.Due to load-sensitive
The pressure of the spring cavity of pump 11 is Δ P, PP=PLS+ Δ P, so, P available in conjunction with above-mentioned formulaP-PA2=Δ P, that is,
It says, the P mouth pressure P of the 3-position 4-way proportional reversing valve 2 of a control valve groupPWith the inlet pressure P of corresponding actuator 100A2
Difference be definite value.For the 3-position 4-way proportional reversing valve 2 of another control valve group, PP-PA3=(PP+PLS)+(PLS-
PA3)=Δ P+ Δ PD, wherein Δ PDFor PA2And PA3Difference.That is, the 3-position 4-way ratio of another control valve group commutates
The P mouth pressure P of valve 2PWith the inlet pressure P of corresponding actuator 100A3Difference be similarly definite value.It can be seen that two three four
The P mouth pressure and the inlet pressure difference of corresponding actuator 100 of logical proportional reversing valve 2 are constant, and because proportional reversing valve
Flow is only related to pressure difference before and after discharge coefficient, valve port flow area, valve port and fluid density, and in the embodiment of the present invention
In, since pressure difference is constant before and after valve port, so the flow of two 3-position 4-way proportional reversing valves 2 can linear ratio control
System.
Also, after the discharge capacity of load sensitive pump 11 reaches maximum, if continuing out big 3-position 4-way proportional reversing valve 2,
The outlet pressure that will lead to load sensitive pump 11 is unable to maintain that and declines.But due to two 3-position 4-way proportional reversing valves 2
Pressure difference simultaneously declines before and after valve port, so pro rate of the flow of 3-position 4-way proportional reversing valve 2 also according to opening area,
Therefore the linear scale control of actuator 100 is not influenced by 11 flow of load sensitive pump saturation.
In the present embodiment, two actuators 100 all can be hydraulic motor.
In the present embodiment, control valve group further includes throttle valve 6, oil inlet and 3-position 4-way the ratio commutation of throttle valve 6
The T hydraulic fluid port of valve 2 is connected to, and the oil outlet of throttle valve 6 is connected to fuel tank.
In above-mentioned implementation, the T hydraulic fluid port flow velocity of 3-position 4-way proportional reversing valve 2 can control when passing through throttle valve 6,
To realize the oil return flow control to control valve group.
Optionally, control valve group further includes overflow valve 7, the first hydraulic fluid port and the 3-position 4-way proportional reversing valve 2 of overflow valve 7
The connection of A hydraulic fluid port, the second hydraulic fluid port of overflow valve 7 and the B hydraulic fluid port of 3-position 4-way proportional reversing valve 2 circulate, the control port of overflow valve 7
It is connected to the first hydraulic fluid port of overflow valve 7, the spring cavity of overflow valve 7 is connected to the second hydraulic fluid port of overflow valve 7.
In above-mentioned implementation, it can effectively avoid what overloading occurred in corresponding actuator 100 from asking by overflow valve 7
Topic.
In embodiments of the present invention, the Median Function of the 3-position 4-way proportional reversing valve 2 of a control valve group is O-shaped, when
When the 3-position 4-way proportional reversing valve 2 is in middle position, actuator 100 stops working, i.e., hydraulic motor stops operating.
Specifically, the 3-position 4-way proportional reversing valve 2 of a control valve group is solenoid valve, so as to realize 3-position 4-way
The electrical control of proportional reversing valve 2.
In embodiments of the present invention, the Median Function of the 3-position 4-way proportional reversing valve 2 of another control valve group is Y type,
When the 3-position 4-way proportional reversing valve 2 is in middle position, although hydraulic motor no longer receives hydraulic energy, still may be implemented
Rotation improves the applicability of hydraulic system.
Specifically, the 3-position 4-way proportional reversing valve 2 of another control valve group is battery valve, so as to realize three four
The electrical control of logical proportional reversing valve 2.
In the present embodiment, main pump mould group 1 further includes second one-way valve 13, and the oil inlet of second one-way valve 13 and load are quick
The oil outlet connection of sense pump 11, the oil outlet of second one-way valve 13 connect with the P hydraulic fluid port of two 3-position 4-way proportional reversing valves 2 respectively
It is logical.
In above-mentioned implementation, it can effectively avoid hydraulic oil from load sensitive pump 11 by second one-way valve 13
Oil outlet reflux.
The foregoing is merely presently preferred embodiments of the present invention, is not intended to limit the invention, it is all in spirit of the invention and
Within principle, any modification, equivalent replacement, improvement and so on be should all be included in the protection scope of the present invention.
Claims (10)
1. a kind of synchronization hydraulic system of meter out, which is characterized in that the hydraulic system includes main pump mould group, two controls
Valve group and with the one-to-one actuator of described two control valve groups；
The main pump mould group includes load sensitive pump and the motor for driving the load sensitive pump；
The control valve group includes 3-position 4-way proportional reversing valve, shuttle valve, the first check valve and valve for pressure difference, for described in any one
The P hydraulic fluid port of 3-position 4-way proportional reversing valve, the 3-position 4-way proportional reversing valve is connected to the oil outlet of the load sensitive pump,
The A hydraulic fluid port of the 3-position 4-way proportional reversing valve is connected to the A1 hydraulic fluid port of the corresponding actuator, the 3-position 4-way ratio
The B hydraulic fluid port of reversal valve is connected to the B1 hydraulic fluid port of the corresponding actuator, the T hydraulic fluid port of the 3-position 4-way proportional reversing valve and institute
The oil inlet connection of valve for pressure difference is stated, the first oil inlet of the shuttle valve is connected to the A hydraulic fluid port of the 3-position 4-way proportional reversing valve,
Second oil inlet of the shuttle valve is connected to the B hydraulic fluid port of the 3-position 4-way proportional reversing valve, the oil outlet difference of the shuttle valve
Be connected to the oil inlet of the spring cavity of the valve for pressure difference and first check valve, the oil outlet of first check valve respectively with
The control port of the valve for pressure difference, guide's hydraulic fluid port of the load sensitive pump and another control valve group it is first unidirectional
The oil outlet of valve is connected to, and the oil outlet of the valve for pressure difference is connected to the fuel tank of the hydraulic system.
2. hydraulic system according to claim 1, which is characterized in that the control valve group further includes throttle valve, the section
The oil inlet of stream valve is connected to the T hydraulic fluid port of the 3-position 4-way proportional reversing valve, the oil outlet of the throttle valve and the fuel tank
Connection.
3. hydraulic system according to claim 1, which is characterized in that the control valve group further includes overflow valve, described to overflow
Stream valve the first hydraulic fluid port be connected to the A hydraulic fluid port of the 3-position 4-way proportional reversing valve, the second hydraulic fluid port of the overflow valve with it is described
The B hydraulic fluid port of 3-position 4-way proportional reversing valve circulates, and the control port of the overflow valve is connected to the first hydraulic fluid port of the overflow valve,
The spring cavity of the overflow valve is connected to the second hydraulic fluid port of the overflow valve.
4. hydraulic system according to claim 1-3, which is characterized in that described the three of a control valve group
The Median Function of position four-way proportional reversing valve is O-shaped.
5. hydraulic system according to claim 4, which is characterized in that the 3-position 4-way ratio of a control valve group
Example reversal valve is solenoid valve.
6. hydraulic system according to claim 1-3, which is characterized in that another control valve group it is described
The Median Function of 3-position 4-way proportional reversing valve is Y type.
7. hydraulic system according to claim 1-3, which is characterized in that another control valve group it is described
3-position 4-way proportional reversing valve is battery valve.
8. hydraulic system according to claim 1-3, which is characterized in that first actuator is hydraulic horse
It reaches.
9. hydraulic system according to claim 1-3, which is characterized in that second actuator is hydraulic horse
It reaches.
10. hydraulic system according to claim 1-3, which is characterized in that the main pump mould group further includes second
Check valve, the oil inlet of the second one-way valve are connected to the oil outlet of the load sensitive pump, and the second one-way valve goes out
Hydraulic fluid port is connected to the P hydraulic fluid port of two 3-position 4-way proportional reversing valves respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810991811.0A CN108980126B (en) | 2018-08-29 | 2018-08-29 | Return-oil throttling synchronous hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810991811.0A CN108980126B (en) | 2018-08-29 | 2018-08-29 | Return-oil throttling synchronous hydraulic system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108980126A true CN108980126A (en) | 2018-12-11 |
| CN108980126B CN108980126B (en) | 2020-06-26 |
Family
ID=64547451
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810991811.0A Active CN108980126B (en) | 2018-08-29 | 2018-08-29 | Return-oil throttling synchronous hydraulic system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108980126B (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110185670A (en) * | 2019-05-24 | 2019-08-30 | 山东临工工程机械有限公司 | Construction machinery hydraulic system flow allocation method |
| CN110925253A (en) * | 2019-12-19 | 2020-03-27 | 三一重机有限公司 | Engineering machinery composite action control method and device |
| CN111140560A (en) * | 2020-01-15 | 2020-05-12 | 天津市中重科技工程有限公司 | Hydraulic control system of horizontal sucker transverse moving hydraulic motor device for stacking |
| CN111577687A (en) * | 2020-05-06 | 2020-08-25 | 太原理工大学 | Load-sensitive double-hydraulic-cylinder synchronization system and control method thereof |
| CN112833058A (en) * | 2021-01-21 | 2021-05-25 | 长沙中联重科环境产业有限公司 | Load-sensitive hydraulic system and hedge trimming equipment |
| WO2023103208A1 (en) * | 2021-12-09 | 2023-06-15 | 湖南三一华源机械有限公司 | Synchronous control valve, hydraulic control system and work machine |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3422165A1 (en) * | 1983-06-14 | 1984-12-20 | Linde Ag, 6200 Wiesbaden | Hydraulic arrangement with a pump and at least two consumers of hydraulic energy acted upon by this pump |
| EP0438606A1 (en) * | 1989-08-16 | 1991-07-31 | Hitachi Construction Machinery Co., Ltd. | Valve device and hydraulic circuit device |
| JP2000035006A (en) * | 1998-07-16 | 2000-02-02 | Kayaba Ind Co Ltd | Hydraulic control circuit |
| US20080152513A1 (en) * | 2006-12-20 | 2008-06-26 | Hans Esders | Hydraulic circuit arrangement with recovery of energy |
| CN101709623A (en) * | 2009-12-02 | 2010-05-19 | 煤炭科学研究总院西安研究院 | Integral coal mine drilling machine hydraulic system capable of satisfying multiple drilling modes |
| CN203051268U (en) * | 2013-01-06 | 2013-07-10 | 浙江大学 | Multi-degree-freedom parallel pipe piece assembly positioning electrohydraulic control system |
| CN203175567U (en) * | 2013-01-06 | 2013-09-04 | 浙江大学 | Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology |
| CN103882906A (en) * | 2013-12-30 | 2014-06-25 | 华侨大学 | Excavator negative flow system sensitive to load |
| CN107324215A (en) * | 2017-06-28 | 2017-11-07 | 中联重科股份有限公司 | Crane and its hydraulic control system |
| CN108443273A (en) * | 2018-03-14 | 2018-08-24 | 燕山大学 | A kind of emergency management and rescue vehicle equipment oil return line pressure compensation throttle control system |
-
2018
- 2018-08-29 CN CN201810991811.0A patent/CN108980126B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3422165A1 (en) * | 1983-06-14 | 1984-12-20 | Linde Ag, 6200 Wiesbaden | Hydraulic arrangement with a pump and at least two consumers of hydraulic energy acted upon by this pump |
| EP0438606A1 (en) * | 1989-08-16 | 1991-07-31 | Hitachi Construction Machinery Co., Ltd. | Valve device and hydraulic circuit device |
| JP2000035006A (en) * | 1998-07-16 | 2000-02-02 | Kayaba Ind Co Ltd | Hydraulic control circuit |
| US20080152513A1 (en) * | 2006-12-20 | 2008-06-26 | Hans Esders | Hydraulic circuit arrangement with recovery of energy |
| CN101709623A (en) * | 2009-12-02 | 2010-05-19 | 煤炭科学研究总院西安研究院 | Integral coal mine drilling machine hydraulic system capable of satisfying multiple drilling modes |
| CN203051268U (en) * | 2013-01-06 | 2013-07-10 | 浙江大学 | Multi-degree-freedom parallel pipe piece assembly positioning electrohydraulic control system |
| CN203175567U (en) * | 2013-01-06 | 2013-09-04 | 浙江大学 | Energy-saving type shield segment assembling positioning electrohydraulic control system adopting load-sensitive technology |
| CN103882906A (en) * | 2013-12-30 | 2014-06-25 | 华侨大学 | Excavator negative flow system sensitive to load |
| CN107324215A (en) * | 2017-06-28 | 2017-11-07 | 中联重科股份有限公司 | Crane and its hydraulic control system |
| CN108443273A (en) * | 2018-03-14 | 2018-08-24 | 燕山大学 | A kind of emergency management and rescue vehicle equipment oil return line pressure compensation throttle control system |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110185670A (en) * | 2019-05-24 | 2019-08-30 | 山东临工工程机械有限公司 | Construction machinery hydraulic system flow allocation method |
| CN110925253A (en) * | 2019-12-19 | 2020-03-27 | 三一重机有限公司 | Engineering machinery composite action control method and device |
| CN111140560A (en) * | 2020-01-15 | 2020-05-12 | 天津市中重科技工程有限公司 | Hydraulic control system of horizontal sucker transverse moving hydraulic motor device for stacking |
| CN111577687A (en) * | 2020-05-06 | 2020-08-25 | 太原理工大学 | Load-sensitive double-hydraulic-cylinder synchronization system and control method thereof |
| CN112833058A (en) * | 2021-01-21 | 2021-05-25 | 长沙中联重科环境产业有限公司 | Load-sensitive hydraulic system and hedge trimming equipment |
| WO2023103208A1 (en) * | 2021-12-09 | 2023-06-15 | 湖南三一华源机械有限公司 | Synchronous control valve, hydraulic control system and work machine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108980126B (en) | 2020-06-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108980126A (en) | A kind of synchronization hydraulic system of meter out | |
| CN104163385A (en) | Hydraulic control system for winch | |
| CN102865387B (en) | Electric proportional multi-way valve | |
| CN102587443A (en) | Multiway valve hydraulic control system of crawler excavator | |
| CN110219842A (en) | The hydraulic system of hoistable platform | |
| CN104132016A (en) | Three-way flow valve, load-sensitive multi-way valve, hydraulic system and engineering machine | |
| CN106762916A (en) | Work connection, load sensing multi-way valve and engineering machinery | |
| CN106837906B (en) | A kind of anchor capstan hydraulic control system | |
| CN102734241B (en) | Opened and closed hydraulic system and engineering machinery | |
| CN103850286B (en) | A kind of electric drive hydraulic crawler excavator minus flow system based on constant displacement pump | |
| CN110953197B (en) | Power control hydraulic system and crane | |
| CN112746996B (en) | Load sensitive system and engineering hoisting machinery | |
| CN107664130B (en) | Hydraulic control valve group and hydraulic control valve system | |
| CN104033438A (en) | Multi-functional hydraulic-jamming preventing pilot valve for electro-hydraulic directional valve | |
| CN104179743A (en) | Modularized load-sensitive electric-hydraulic proportional multiway valve | |
| CN206655852U (en) | Work connection, load sensing multi-way valve and engineering machinery | |
| CN109519428A (en) | A kind of more hydraulic pump multiplex control systems, work connection and engineering machinery | |
| CN109114053A (en) | A kind of more winch hydraulic systems | |
| CN208719046U (en) | A kind of intelligence confluence Multi-way valve device and engineering machinery | |
| CN104030199A (en) | Forklift hydraulic system with bypass oil way throttling speed regulation loop | |
| CN108975188B (en) | Hydraulic system | |
| CN105862962B (en) | Reduce the hydraulic circuit of return oil pressure | |
| CN208702969U (en) | A kind of hydraulic control system and automobile | |
| CN105889160A (en) | Rapid hydraulic system of scrap steel shear | |
| CN109723694A (en) | Electric control multi-way valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |