CN104564873B - Single load hydraulic system and machine - Google Patents
Single load hydraulic system and machine Download PDFInfo
- Publication number
- CN104564873B CN104564873B CN201310506844.9A CN201310506844A CN104564873B CN 104564873 B CN104564873 B CN 104564873B CN 201310506844 A CN201310506844 A CN 201310506844A CN 104564873 B CN104564873 B CN 104564873B
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- Prior art keywords
- hydraulic system
- pressure
- variable pump
- valve
- control valve
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- 239000012530 fluid Substances 0.000 claims abstract description 57
- 238000006073 displacement reaction Methods 0.000 claims abstract description 17
- 238000004891 communication Methods 0.000 abstract description 7
- 238000005086 pumping Methods 0.000 abstract description 3
- 239000002828 fuel tank Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000284 extract Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000012224 working solution Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
-
- 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
-
- 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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Power Steering Mechanism (AREA)
Abstract
The hydraulic system (10) that the present invention relates to a kind of for machine, including steering hydraulic system (11), hydraulic system of working (12), for the variable pump (14) to steering hydraulic system supply hydraulic fluid, with the constant displacement pump (16) for supplying hydraulic fluid to hydraulic system of working, wherein, the variable pump is selectively in fluid communication with steering hydraulic system and hydraulic system of working by pressure-gradient control valve (13), it is characterized in that, the pressure-gradient control valve has a LS mouthfuls (133), the LS mouthfuls for receiving the load feedback pressure signal (LS) from steering hydraulic system in steering hydraulic system work, and the pressure-gradient control valve is configured to preferentially be supplied to steering hydraulic system by the hydraulic fluid of variable pump pumping when steering hydraulic system works.
Description
Technical field
Present invention relates in general to a kind of hydraulic system, relate more specifically to a kind of single load-sensitive hydraulic system and packet
Machine containing the hydraulic system.
Background technique
The machine of such as wheel loader, excavator, bull-dozer, land leveller or other type heavy equipments etc usually makes
It is completed various tasks with multiple actuators of the hydraulic fluid for the one or more pumps being supplied on machine.Existing liquid
Pressure system mainly includes double constant displacement pump autonomous systems, double constant displacement pump converging systems, bivariate pump autonomous system etc..These hydraulic pressure systems
System has the disadvantage that, double constant displacement pump autonomous systems and converging system all have the defects that it is not energy-efficient, especially machine not
When work, there is the energy loss of system under back pressure when the engine speed of machine centainly either changes,
And bivariate pumping system then higher cost and control is more complicated, and the cleannes of oil product are required very under severe operating condition
Height, this makes the cleannes for how guaranteeing oil product become a problem.
In addition, being it is known that in the prior art using the single load-sensitive hydraulic system for opening core valve, use in such systems
One is used for the constant displacement pump of hydraulic system of working for the variable pump of steering hydraulic system and one.The hydraulic system is using steering
Preferential hydraulic control method, when machine turns to, variable pump is worked as machine and is not turned to preferentially to steering hydraulic system fuel feeding
When, collaborated by the hydraulic fluid that at least part of the hydraulic fluid of variable pump output can be exported with constant displacement pump and is supplied to work
Make hydraulic system, power tool is made more effectively to work.But one of this hydraulic system the disadvantage is that, in the standby shape of machine
The smallest flow in hydraulic system is not able to maintain under state.
The present invention is directed to overcome the problems, such as the above-mentioned one or more and/or prior art other problems.
Summary of the invention
In an aspect, the present invention relates to a kind of hydraulic system for machine, which includes steering hydraulic
System, hydraulic system of working, for the variable pump to steering hydraulic system supply hydraulic fluid and for hydraulic system of working
Supply hydraulic fluid constant displacement pump, wherein the variable pump by pressure-gradient control valve selectively with steering hydraulic system and working solution
Press system fluid connection, which is characterized in that the pressure-gradient control valve has a LS mouthfuls, and the LS mouthfuls in steering hydraulic system work
The load feedback pressure signal from steering hydraulic system is received, and the pressure-gradient control valve is configured to work when steering hydraulic system
When by variable pump pumping hydraulic fluid be preferentially supplied to steering hydraulic system.
Advantageously, the pressure-gradient control valve is fluidly connected to sequence valve by check valve, and the sequence valve is fluidly connected to work
Hydraulic system, and the hydraulic system includes the control valve for controlling the output flow of the variable pump, when machine is in
When standby mode, the sequence valve is closed, so that flowing to the control valve by the hydraulic fluid that variable pump pumps with by variable pump
Output flow adjust to smaller value, to reach energy-efficient purpose.
In another aspect, the present invention relates to a kind of machines including the hydraulic system.
Detailed description of the invention
Below with reference to schematical attached drawing, the present invention will be described in more detail.Attached drawing and corresponding embodiment are merely to say
Bright purpose, and is not intended to limit the present invention.In the accompanying drawings:
Fig. 1 schematically shows hydraulic system according to the present invention,
Pressure-gradient control valve used in hydraulic system Fig. 2 shows Fig. 1, and
Fig. 3 is the partial schematic diagram of hydraulic system according to the present invention.
Specific embodiment
Fig. 1 schematically shows the hydraulic system 10 according to the present invention for being used for a machine, such as wheel loader, simultaneously
Referring to Fig. 3, hydraulic system 10 includes steering hydraulic system 11 and hydraulic system of working 12.Steering hydraulic system 11 includes variable pump
14, which is used to extract hydraulic fluid from fuel tank 21 and hydraulic fluid is delivered to transfer (such as the vehicle of machine
Wheel) 22 so that machine turn to.Hydraulic system of working 12 includes constant displacement pump 16, which is used to extract flow of pressurized from fuel tank 21
Hydraulic fluid is simultaneously delivered to the power tool 26 of machine to realize different tasks by body.Power tool can be embodied as shoveling
Bucket, fork arrangement, propulsion device, cutter device, scoop, snow breaker or any other task execution dress known in the art
It sets.Power tool can complete various movements under the driving of hydraulic fluid, such as lift, tilt, pivot, rotation, swing or
Person's other movements known in the art.
As shown in Figure 1, constant displacement pump 16 is fluidly connected with power tool 26 via opening core valve 24, so that by constant displacement pump 16 from oil
The hydraulic fluid that case 21 extracts can drive power tool to realize desired movement.In addition, hydraulic fluid can be from power tool
26 return to fuel tank 21 by opening core valve 24.
The output end of variable pump 14 is fluidly connected with a pressure-gradient control valve 13.The schematic diagram of pressure-gradient control valve 13 is shown in detail in Fig. 2.It is excellent
First valve 13 has input port 130 and two output ports 131,132, wherein the output end of variable pump 14 and pressure-gradient control valve 13
Input port 130 fluidly connects, and output port 131 is fluidly connected via the input port of a check valve 17 and sequence valve 18, suitable
Sequence valve 18 is fluidly connected with power tool 26 via opening core valve 24.The steering of another output port 132 and machine of pressure-gradient control valve 13
Device 22 fluidly connects.When the input port 130 of pressure-gradient control valve 13 and output port 132 are in fluid communication, by variable pump 14 from oil
The hydraulic fluid that case 21 extracts can flow to the transfer 22 of machine through pressure-gradient control valve 13, to realize desired steering operation.
In addition, hydraulic fluid can return to fuel tank 21 from transfer 22.
Other than input port 130 and two output ports 131,132, pressure-gradient control valve 13 further includes and transfer 22
The LS mouth 133 that control port fluidly connects, the load feedback pressure LS from transfer 22 can be arrived via control channel 28
Up to LS mouth 133.Pressure-gradient control valve 13 also comprises the spring 5 of spool and the right side bias spool into Fig. 2.When from variable pump
When 14 hydraulic fluid reaches input port 130, hydraulic fluid is preferentially supplied to output port 132 through spool.Work as transfer
22 when not working, and output port 132 is in closed state, at this point, LS mouthfuls of pressure is zero, hydraulic fluid acts on the right side of spool
End, overcomes spring 5 to act on the biasing force on spool, keeps spool mobile towards the left side in Fig. 2, the input port of pressure-gradient control valve 13
130 are in fluid communication with output port 131.In this way, the hydraulic fluid from variable pump 14 flows to check valve 17 through pressure-gradient control valve 13, and
Connect sequence valve 18, so that the hydraulic fluid from variable pump 14 is defeated together with the hydraulic fluid from constant displacement pump 16
It is sent to hydraulic system of working 12, two pumps 14 and 16 operate under the state of interflow, so that the efficiency of hydraulic system 10 increases.
As shown in figs. 1 and 3, hydraulic system 10 according to the present invention further includes shuttle valve 15.As known in the art, shuttle valve 15
Including two input ports and an output port.The first input port 151 and 11 fluid of steering hydraulic system of shuttle valve 15 connect
Connect to receive the load feedback pressure signal LS of the transfer 22 from steering hydraulic system, the second input port 152 with
Hydraulic system of working 12 fluidly connects to receive the pressure signal from hydraulic system of working.The output port 153 of shuttle valve 15
It is fluidly connected with the control valve 19 for variable pump 14, to send the pressure signal received to variable pump 14, pushes and become
The swash plate of amount pump 14, to control the work of variable pump 14.If only steering hydraulic system 11 works, shuttle valve 15 can rotation in future
Variable pump 14 is sent to the load feedback pressure signal LS of device 22.If only hydraulic system of working 12 works, shuttle valve 15
Pressure signal from hydraulic system of working can be sent to variable pump 14.If steering hydraulic system 11 and hydraulic system of working
12 are all working, then effect has from steering hydraulic system 11 and working hydraulic pressure system the two of shuttle valve 15 input port respectively simultaneously
The pressure signal of system 12, wherein will send variable pump 14 to by biggish pressure signal at this time.Especially as seen from Figure 3, variable pump 14
Output end be also fluidly coupled to control valve 19, when variable pump 14 export the sufficiently large balance to break control valve 19 of pressure
Formula, the pressure difference value Δ p(margine pressure for overcoming control valve 19) when, control valve 19, which can be connected, leads to variable pump 14
Control oil cylinder 20 flow path, thus push the swash plate oil cylinder of variable pump 14, change swash plate pivot angle, thus regulated variable pump 14
Output flow.
When machine carries out steering operation, output port 132 and transfer 22 are in fluid communication, the liquid from variable pump 14
It presses fluid to reach transfer 22, turns to machine.Load feedback pressure LS from transfer 22 is passed through after passing through throttle valve
The left end of spool is acted on by the LS mouth 133 of pressure-gradient control valve 13.When the revolving speed of transfer is very big, thus load feedback pressure LS foot
When enough big, enable to the spool of pressure-gradient control valve 13 mobile towards the right side in Fig. 2.At this point, the input port 130 of pressure-gradient control valve 13 with
Output port 132 is in fluid communication.Hydraulic fluid from variable pump 14 flows to steering hydraulic system 11, to realize desired turn
To movement.
It should be appreciated that pressure-gradient control valve 13 can be ratio valve-type, spool can be according to acting between spool both ends
Pressure difference and proportionally move.Therefore, with the variation of the load feedback pressure LS from transfer 22, by variable pump 14
The hydraulic fluid of extraction can distribute between the output port 131 and 132 of pressure-gradient control valve 13.In this way, as required, carrying out independent variable
The a part of of the hydraulic fluid of pump 14 can be supplied to steering hydraulic system 11, another part then can with come from constant displacement pump 16
Hydraulic fluid be supplied to hydraulic system of working 12 together.
Advantageously, pressure-gradient control valve 13, check valve 17, sequence valve 18 and shuttle valve 15 can be designed to Cartridge inserted valve integrated block, therefore save on
The arrangement space of hydraulic system 10.
The various working conditions of hydraulic system 10 are described in detail below.
Industrial feasibility
When the steering hydraulic system 11 of machine does not work, and when hydraulic system of working 12 works, the of shuttle valve 15 is acted on
The load feedback pressure signal of one input port 151 is zero, and shuttle valve 15 will be transmitted from the pressure signal of hydraulic system of working 12
To variable pump 14, starts variable pump 14 and work.At this point, the load feedback pressure LS at the LS mouth 133 of pressure-gradient control valve 13 is also zero, make
Overcome spring 5 to act on the spring force on spool with the pressure of the hydraulic fluid of the spool right end in pressure-gradient control valve 13, makes the spool
Left side into Fig. 2 is mobile, and input port 130 and output port 131 are in fluid communication.Hydraulic fluid from variable pump 14 via
Check valve 17 and sequence valve 18 collaborate with the hydraulic fluid from constant displacement pump 16, are then transported to work via opening core valve 24 together
Industry tool 26, thus constant displacement pump 16 and variable pump 14 provide hydraulic fluid to hydraulic system of working jointly.
When the steering hydraulic system 11 of machine works, and when hydraulic system of working 12 does not work, the of shuttle valve 15 is acted on
The pressure signal of two input ports 152 is zero, and the load feedback pressure signal LS of shuttle valve low damage hydraulic system in 15 future 11 is passed
It send to variable pump 14, starts variable pump 14 and work.Meanwhile load feedback pressure LS from transfer 22 and pressure-gradient control valve 13
Spring 5 makes right side of the spool of pressure-gradient control valve 13 into Fig. 2 mobile jointly, thus the input port 130 and output end of pressure-gradient control valve 13
Mouth 132 is in fluid communication, and the hydraulic fluid from variable pump 14 flows to steering hydraulic system 11, to realize that desired turn to is moved
Make.
It is negative from steering hydraulic system 11 when the steering hydraulic system 11 of machine and hydraulic system of working 12 all work
The first input port 151 that feedback pressure signal LS acts on shuttle valve 15 is carried, the pressure signal from hydraulic system of working 12 is made
Used in the second input port 152 of shuttle valve 15.At this point, shuttle valve 15 is sent to variable for one of larger in the two pressure signals
Pump 14, starting variable pump 14 work.Meanwhile the spool of pressure-gradient control valve 13 is in the load feedback pressure letter from steering hydraulic system 11
It is moved under the collective effect of number LS and the hydraulic fluid from variable pump 14, so that one of the hydraulic fluid from variable pump 14
Divide by priority of supply to steering hydraulic system 11, realizes desired go to action, and rest part is then and from constant displacement pump 16
Hydraulic fluid is supplied to hydraulic system of working 12 behind interflow.
When machine is in standby, steering hydraulic system 11 and hydraulic system of working 12 do not work.At this point, turning to
Device does not generate any load feedback pressure signal LS, and the input port 130 and 131 fluid of output port of pressure-gradient control valve 13 connect
It is logical.Hydraulic fluid from variable pump 14 is by 17 order of arrival valve 18 of pressure-gradient control valve 13 and check valve.Hydraulic system of working 12
In hydraulic fluid directly return to fuel tank 21, cause the circuit pressure of hydraulic system of working 12 lower, sequence valve 18 close, at this time
The control valve 19 of variable pump 14 is flowed to by the hydraulic fluid that variable pump 14 pumps.It is gradually increasing by the pressure that variable pump 14 exports,
Until breaking the balanced type of control valve 19, the pressure difference value Δ p(margine pressure of control valve 19 is overcome), make control valve
19 lead to the flow path (referring to attached drawing 3) of the control oil cylinder 20 of variable pump 14, push the swash plate oil cylinder of variable pump 14, control oil
Cylinder 20 controls the swash plate pivot angle of variable pump 14 to the output flow very little of variable pump 14, to realize energy-efficient purpose.
Hydraulic system of the invention is described by specific embodiment above.It shows to those skilled in the art
And be clear to, a variety of changes can be made to hydraulic system of the invention without departing from the present invention in the case of the inventive idea
And deformation.The practice of the considerations of in conjunction with to specification and disclosed hydraulic system, other embodiments are for those skilled in the art
It will be apparent for member.Specification and example are considered only as illustratively, real range by following the claims and
Their equivalent program indicates.
Claims (5)
1. a kind of hydraulic system (10) for machine, including steering hydraulic system (11), hydraulic system of working (12), for
Steering hydraulic system supplies the variable pump (14) of hydraulic fluid and for the constant displacement pump to hydraulic system of working supply hydraulic fluid
(16), wherein the variable pump is selectively connected with steering hydraulic system and hydraulic system of working fluid by pressure-gradient control valve (13)
It is logical, which is characterized in that the pressure-gradient control valve has a LS mouthfuls (133), and the LS mouthfuls in steering hydraulic system work for receiving
The load feedback pressure signal (LS) of low damage hydraulic system, and the pressure-gradient control valve is configured to when steering hydraulic system works
Steering hydraulic system is preferentially supplied to by the hydraulic fluid that variable pump pumps,
Wherein, the pressure-gradient control valve is fluidly connected to sequence valve (18) by check valve (17), and the sequence valve is fluidly connected to work
Make hydraulic system, and the hydraulic system includes the control valve (19) for controlling the output flow of the variable pump, works as machine
When device is in standby, the sequence valve is closed, so that flowing to the control valve (19) by the hydraulic fluid that variable pump pumps
Adjusting the output flow of variable pump to smaller value.
2. hydraulic system according to claim 1, wherein the hydraulic system includes shuttle valve (15), and the shuttle valve is used for
Future low damage hydraulic system the load feedback pressure signal and pressure signal from hydraulic system of working in it is higher
One is transmitted to variable pump, to control variable pump work.
3. hydraulic system according to any one of the preceding claims, wherein the pressure-gradient control valve is configured in the work
Hydraulic system closes at least part of the hydraulic fluid pumped by variable pump with the hydraulic fluid pumped by constant displacement pump
It flows and is supplied to hydraulic system of working.
4. hydraulic system according to claim 2, wherein the pressure-gradient control valve, check valve, sequence valve and shuttle valve are configured to one
Cartridge inserted valve integrated block.
5. a kind of machine, including hydraulic system according to any one of the preceding claims.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310506844.9A CN104564873B (en) | 2013-10-24 | 2013-10-24 | Single load hydraulic system and machine |
| RU2014142887A RU2678475C2 (en) | 2013-10-24 | 2014-10-23 | Single-load hydraulic system and machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310506844.9A CN104564873B (en) | 2013-10-24 | 2013-10-24 | Single load hydraulic system and machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104564873A CN104564873A (en) | 2015-04-29 |
| CN104564873B true CN104564873B (en) | 2018-12-21 |
Family
ID=53081714
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310506844.9A Active CN104564873B (en) | 2013-10-24 | 2013-10-24 | Single load hydraulic system and machine |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104564873B (en) |
| RU (1) | RU2678475C2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA3039305A1 (en) * | 2018-04-06 | 2019-10-06 | The Raymond Corporation | Auxiliary hydraulic circuit filtering systems and methods |
| RU191188U1 (en) * | 2019-05-07 | 2019-07-29 | Маргарита Викторовна Минеева | TRACTOR HYDRAULIC SYSTEM |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5579642A (en) * | 1995-05-26 | 1996-12-03 | Husco International, Inc. | Pressure compensating hydraulic control system |
| GB2324575A (en) * | 1997-04-24 | 1998-10-28 | Caterpillar Inc | Load sense hydraulic system |
| CN2610133Y (en) * | 2003-03-14 | 2004-04-07 | 柯坚 | Quantitative variable confluent system of loader |
| CN201169289Y (en) * | 2008-01-29 | 2008-12-24 | 广西柳工机械股份有限公司 | Forklift load sensing priority steering hydraulic system |
| CN101954927A (en) * | 2010-10-19 | 2011-01-26 | 中国人民解放军总装备部军械技术研究所 | Multi-load hydraulic sensing system for single-power source and multi-system working |
| CN203113417U (en) * | 2012-12-28 | 2013-08-07 | 龙工(上海)机械制造有限公司 | Univariate hydraulic system of loading machine |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2160696C2 (en) * | 1997-10-31 | 2000-12-20 | Стесин Александр Борисович | Fork-lift truck hydraulic system |
| RU13205U1 (en) * | 1999-12-06 | 2000-03-27 | Открытое акционерное общество Тверской экскаваторный завод | FORKLIFT HYDRAULIC SYSTEM |
| RU84878U1 (en) * | 2009-04-22 | 2009-07-20 | Общество с ограниченной ответственностью "Инженерный центр" | HYDRAULIC DRIVER OF A SINGLE LOAD LOADER |
-
2013
- 2013-10-24 CN CN201310506844.9A patent/CN104564873B/en active Active
-
2014
- 2014-10-23 RU RU2014142887A patent/RU2678475C2/en active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5579642A (en) * | 1995-05-26 | 1996-12-03 | Husco International, Inc. | Pressure compensating hydraulic control system |
| GB2324575A (en) * | 1997-04-24 | 1998-10-28 | Caterpillar Inc | Load sense hydraulic system |
| CN2610133Y (en) * | 2003-03-14 | 2004-04-07 | 柯坚 | Quantitative variable confluent system of loader |
| CN201169289Y (en) * | 2008-01-29 | 2008-12-24 | 广西柳工机械股份有限公司 | Forklift load sensing priority steering hydraulic system |
| CN101954927A (en) * | 2010-10-19 | 2011-01-26 | 中国人民解放军总装备部军械技术研究所 | Multi-load hydraulic sensing system for single-power source and multi-system working |
| CN203113417U (en) * | 2012-12-28 | 2013-08-07 | 龙工(上海)机械制造有限公司 | Univariate hydraulic system of loading machine |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2014142887A3 (en) | 2018-07-30 |
| CN104564873A (en) | 2015-04-29 |
| RU2678475C2 (en) | 2019-01-29 |
| RU2014142887A (en) | 2016-05-20 |
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