CN105003475B - The hydraulic system of engineering machinery - Google Patents
The hydraulic system of engineering machinery Download PDFInfo
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- CN105003475B CN105003475B CN201510190974.5A CN201510190974A CN105003475B CN 105003475 B CN105003475 B CN 105003475B CN 201510190974 A CN201510190974 A CN 201510190974A CN 105003475 B CN105003475 B CN 105003475B
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- pressure
- control valve
- working oil
- valve unit
- main pump
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- 241000283074 Equus asinus Species 0.000 claims description 33
- 230000006835 compression Effects 0.000 claims description 22
- 238000007906 compression Methods 0.000 claims description 22
- 239000007788 liquid Substances 0.000 claims description 11
- 210000000635 valve cell Anatomy 0.000 claims description 7
- 238000007599 discharging Methods 0.000 claims description 4
- 239000003921 oil Substances 0.000 description 133
- 238000010586 diagram Methods 0.000 description 10
- 230000000875 corresponding effect Effects 0.000 description 7
- 230000002159 abnormal effect Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 230000002596 correlated effect Effects 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2253—Controlling the travelling speed of vehicles, e.g. adjusting travelling speed according to implement loads, control of hydrostatic transmission
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2285—Pilot-operated systems
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2292—Systems with two or more pumps
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The present invention relates to the hydraulic system of engineering machinery.The hydraulic system of the engineering machinery of the embodiment of the present invention, when for driving mode, makes the working oil spued from the first main pump collaborate the working oil spued from the second main pump, the working oil at interflow is supplied to driving motors, makes driving performance improve.Additionally, even if the situation that the hydraulic system of the engineering machinery of the embodiment of the present invention occurs the first, the 3rd control valve unit (51,53) correctly to control because of unknowable reason, when being driving mode, limit the maximum discharge flow that the first main pump spues, it is thus possible to prevent from travelling hypervelocity, it is thus able to guarantee riding stability, it is possible to prevent driving system durability low.
Description
Technical field
The present invention relates to the hydraulic system of engineering machinery.More specifically, relate to one and possess the first main pump
With the hydraulic system of the second main pump, when for driving mode, the working oil spued from the first main pump collaborates
The working oil spued from the second main pump, the working oil at interflow is supplied to driving motors, thus driving performance can
Mention the hydraulic system of the engineering machinery of raising.
Background technology
It is said that in general, possess power source and hydraulic system in engineering machinery.Power source can be electromotor or
Electro-motor.Hydraulic system can include main pump, main control valve, executor, donkey pump and stick.
Main pump operates by means of power source, spues and defines the working oil of pressure.Main pump can possess multiple.
It addition, main pump can be the variable displacement that discharge flow is variable.The working oil spued from main pump can be supplied
To main control valve.
In main control valve, multiple control valve unit can be configured with.Each control valve unit can be with multiple
Executor connects with each hydraulic line.
Donkey pump operates by means of power source, discharge guide's working oil.Donkey pump can be that discharge flow is solid
Fixed fixed capacity type.The guide's working oil spued from donkey pump can be supplied to stick.
Stick can be operated by operator.If manipulation bar, then produce based on guide's working oil
Control signal.Control signal is the signal corresponding with the operation displacement of stick.Control signal Access Control
The compression zone of the spool of valve cell.If that is, operator's manipulation bar, then, with the operation of stick
The spool of corresponding control valve unit moves, thus, the working oil of the high pressure being fed to main control valve carries
Supply executor.Executor operates by means of the working oil provided, and performs desired operation.
In executor, can there is the lienar for linearly operated, carry out rotating the rotary-type of operating.Line
The executor of property type can be swing arm executor, arm executor, scraper bowl executor etc..It addition, it is rotary-type
Can be the driving motors of engineering machinery, rotary actuator etc..It addition, executor can also include so that engineering
Machinery is able to carry out the apolegamy part executor of additional function, supporting leg (outrigger), dozer (dozer).
On the other hand, in described main control valve, possess the first hydraulic line being connected with the first main pump and
The second hydraulic line being connected with the second main pump.The executor that first main pump and the second main pump are mainly responsible for is
Determine.Such as, in the first hydraulic line, apolegamy part control valve unit, bucket can be configured with
Unit, swing arm 2 speed control valve unit, arm 1 speed control valve unit etc..It addition, at the second hydraulic line
In, travel control valve unit, apolegamy part control valve unit, weave control valve cell, swing arm can be configured with
1 speed control valve unit, arm 2 speed control valve unit etc..
But, there are the following problems for the hydraulic system of common engineering machinery.
Engineering machinery can select a certain kind in work pattern with driving mode.Work pattern is that operation is put
In precedence, swing arm, arm, scraper bowl, portion of upper body rotation etc. is mainly used to operate.Driving mode
Being that traveling is placed in precedence, main use driving motors operates.If electromotor drives, then the
One, the second main pump is driven with donkey pump, in travel control valve unit, inputs and spues from the second main pump
Working oil.In the case of selecting driving mode to perform to travel, the hydraulic system of common engineering machinery
Owing to the second main pump links together with travel control valve unit, thus there is the work spued from the first main pump
Oil cannot be used for travelling, but the problem being expelled directly out.
As other problem, exist under steam, in order to driving motors ample supply working oil to be higher than
Engine rotation number (rpm) during work pattern, such as, with 2,000rpm makes engine-driven situation.
That is, when being work pattern, the rotation number of electromotor being set to 1,500rpm to 1,800rpm, with this
Comparing, the engine rotation number when being driving mode is the highest.Therefore, in the past, in order to meet traveling
Performance, should be selected to the electromotor that the engine shaft power that operates with high rotation number is bigger.Therefore, driving
During dynamic electromotor, loss increases, and there is the problem that fuel economy reduces.
As another problem, in terms of determining the volume specification of main pump, driving performance and operation should be considered
Machine performance, thus have difficulties in terms of determining main pump specification.Such as, if it is considered that driving performance and traction
Power and determine the volume of driving motors, then, travel speed can be according to engine rotation number and the appearance of main pump
Amass and design.But, the volume of main pump determines according to working rig performance, thus needed for meeting travel speed
Engine rotation number independently can only determine with the intention of designer.As a result, not in order to meet engineering machine
The traveling target performance (pull strength and travel speed) of tool and can the performance factor of efficient design running gear,
Thus there is running gear efficiency inevitable very poor problem compared with working rig efficiency.
As another problem, the hydraulic system of conventional engineering machinery proposes a kind of technology, when being capable
When sailing pattern, the working oil spued from the first main pump is made to collaborate the working oil spued from the second main pump, closing
The working oil of stream is supplied to driving motors so that improve driving performance.Travel and realize by means of driving system,
In driving system, in addition to driving motors, including a large amount of elements relevant to traveling.But,
In the hydraulic system of conventional engineering machinery, due to unknowable reason, control by means of current signal
The control portion of system can occur problem.If control portion occurs problem, then the control to the first main pump can be improper.
Particularly when collaborate the working oil spued from the second main pump from the working oil of the first main pump discharge, then supply
The working oil that should give driving motors can excess.That is, compared with the travel speed of the manufacturer of engineering machinery design,
There is the worry driven over the speed limit, there is the problem that riding stability is harmed.If it addition, working oil mistake
Amount is supplied to driving motors, then problem can occur in terms of the durability of driving system.
Prior art literature
Patent documentation
Patent documentation 1: Japanese Laid-Open Patent Publication the 2004-27706th (2004.01.29.)
Summary of the invention
Therefore, the purpose of the technical task that the present invention is to be realized is to provide one to make it possible to make engineering machine
While the driving performance of tool improves, prevent the hydraulic system of the engineering machinery that driving system durability deteriorates.
The present invention want reality technical task be not limited to the above technical task mentioned, do not mention other
Technical task is that those skilled in the art can be expressly understood that from set forth below.
The hydraulic system being intended to reach the engineering machinery of the present invention of described technical task includes: the first main pump
11, the second main pump 12, the working oil of its high pressure that spues respectively；Donkey pump 70, its discharge guide's working oil；
First hydraulic line 21, it is connected with described first main pump 11；Second hydraulic line 22, it is with described the
Two main pumps 12 connect；Travel control valve unit 31, it is configured on described second hydraulic line 22, controls
Make the flow direction of the working oil supplied to driving motors 80；First relief valve 41, it is configured at described
On one hydraulic line 21, the pressure of described first hydraulic line 21 is made to be maintained at below safe pressure；First
Control valve unit 51, when selecting driving mode, this first control valve unit 51 is open and makes described guide
Working oil passes through；Second control valve unit 52, it is by means of the institute via described first control valve unit 51
State guide's working oil and operate, make the working oil spued from described first main pump 11 be connected to described second liquid
Pressure pipeline 22；And shuttle valve 60, at its two ends, the pressure of described guide's working oil is competing with described safe pressure
Strive, make the working oil of relatively large pressure be connected to the first actuator 13 of described first main pump 11.
It addition, for the hydraulic system of the engineering machinery of the embodiment of the present invention, at described first relief valve
The pressure of guide's working oil that the safe pressure arranged in 41 spues with described donkey pump 70 can arrange to obtain phase
With.
It addition, the hydraulic system of the engineering machinery of the embodiment of the present invention can also include the 3rd control valve unit
53, its a certain pump pressure in described first main pump 11 or described second main pump 12 higher than pressure is set time,
The pressure of the working oil provided to described first actuator 13 is provided.
It addition, for the hydraulic system of the engineering machinery of the embodiment of the present invention, described 3rd control valve unit
53 can be proportionally to reduce to described first actuator with described pump pressure and the described difference arranging pressure
The electrical proportional control valve of the pressure of 13 working oils provided.
It addition, for the hydraulic system of the engineering machinery of the embodiment of the present invention, when selecting work pattern,
Described first control valve unit 51 can connect compression zone and the discharging slot of the spool of the second control valve unit 52
Connecting, described second control valve unit 52 disconnects described first hydraulic line 21 and described second hydraulic line
The connection of 22.
It addition, the present invention can provide the hydraulic system of a kind of engineering machinery, including: the first main pump 11,
Second main pump 12, the working oil of its high pressure that spues respectively；Donkey pump 70, its discharge guide's working oil；The
One hydraulic line 21, it is connected with described first main pump 11；Second hydraulic line 22, it is with described second
Main pump 12 connects；Travel control valve unit 31, it is configured on described second hydraulic line 22, controls
Flow direction to the working oil of driving motors 80 supply；First relief valve 41, it is configured at described first
On hydraulic line 21, the pressure of described first hydraulic line 21 is made to be maintained at below safe pressure；First control
Valve cell 51 processed, when selecting driving mode, this first control valve unit 51 opens and makes described guide's work
Pass through as oil；Second control valve unit 52, it is by means of via described in described first control valve unit 51
Guide's working oil and operate, make from described first main pump 11 spue working oil be connected to described second hydraulic pressure
Pipeline 22；3rd control valve unit 53', described guide's working oil is reduced pressure and exports by it；And shuttle valve
60, at its two ends, the pressure of described first hydraulic line 21 and the output of described 3rd control valve unit 53'
Pressure is competed, and makes the working oil of relatively large pressure be connected to the first actuator of described first main pump 11
13。
Now, the elder generation that the safe pressure arranged in described first relief valve 41 spues with described donkey pump 70
The pressure leading working oil can arrange identical.
It addition, a certain pump pressure in described first main pump 11 or described second main pump 12 is higher than arranging pressure
During power, described 3rd control valve unit 53' can reduce the pressure of the working oil of output.
It addition, described 3rd control valve unit 53' can with exceed the pump pressure of the described pump that pressure is set with
The described difference arranging pressure proportionally reduces the pressure of the working oil of output.
It addition, when selecting work pattern, described first control valve unit 51' can connect the second control valve
The compression zone of unit 52' is connected with discharging slot, and described second control valve unit 52' can disconnect described first liquid
Pressure pipeline 21 and the connection of described second hydraulic line 22.
The details of other embodiments are contained in detailed description and accompanying drawing.
The effect of the present invention is as follows.
The hydraulic system of the engineering machinery of the embodiment of the present invention configured as described above, when being driving mode, makes
The working oil spued from the first main pump collaborates the working oil from the second main pump discharge, and the working oil at interflow is carried
Supply driving motors, it is possible to make driving performance improve.
Even if it addition, the hydraulic system of the engineering machinery of the embodiment of the present invention occurs because of unknowable reason
One, the situation that three control valve unit 51,53 cannot correctly control, when being driving mode, it is possible to limits
The maximum discharge flow that first main pump spues.It is thus possible to prevent from travelling hypervelocity, it can be ensured that riding stability,
And then it is low to be prevented from driving system durability.
Accompanying drawing explanation
Fig. 1 is that the hydraulic system of the engineering machinery for first embodiment of the invention is described is transported with work pattern
Hydraulic circuit diagram when turning.
Fig. 2 is that the hydraulic system of the engineering machinery for first embodiment of the invention is described is transported with driving mode
Hydraulic circuit diagram when turning.
Fig. 3 is that the hydraulic system of the engineering machinery for first embodiment of the invention is described is transported with driving mode
The hydraulic circuit diagram of the situation of overload is there is in turning.
Fig. 4 is that the hydraulic system of the engineering machinery for second embodiment of the invention is described is transported with work pattern
Hydraulic circuit diagram when turning.
Fig. 5 is that the hydraulic system of the engineering machinery for second embodiment of the invention is described is transported with driving mode
Hydraulic circuit diagram when turning.
Symbol description
11,12-first, second main pump, 13,14-first, second actuator, 15,16-first,
Two pressure transducers, 17-electromotor, 21,22,23,24,25,26,27,28-first～the 8th liquid
Pressure pipeline, 30-main control valve (MCV), 31-travel control valve unit, 41,42-first and second safety
Valve, 51,52,53-first, second, third control valve unit, 60-shuttle valve, 70-donkey pump, 80-
Driving motors.
Detailed description of the invention
The embodiment described the most in detail referring to the drawings and, advantages of the present invention and feature and realization
Its method will be clear and definite.
With reference to the accompanying drawings, embodiments of the invention are described in detail.Embodiment explained below be for
Helping the understanding of the present invention and exemplarily enumerate, the present invention is interpreted as can be with enforcement described herein
The most various deformation implementation of example.But, during the explanation present invention, when judging to think to relevant public affairs
That knows function or element illustrates when may obscure idea of the invention, and description is omitted and tool
Body illustrates.It addition, accompanying drawing is in order to help the understanding of invention, it not to illustrate by actual ratio chi, a part of structure
The size becoming key element may illustrate turgidly.
On the other hand, the term that aftermentioned term sets as the function considered in the present invention, it can be because of life
Intention or the convention of product person and different, thus its definition should be made based on this specification in the whole text content.
In description in the whole text, identical reference marks censures identical element.
Referring to Fig. 1, the hydraulic system of the engineering machinery of first embodiment of the invention is illustrated.
Fig. 1 is that the hydraulic system of the engineering machinery for first embodiment of the invention is described is transported with work pattern
Hydraulic circuit diagram when turning.
The hydraulic system of first embodiment of the invention can include first, second main pump 11,12, main control
Valve 30, donkey pump 70.
First, second main pump 11,12 operates by means of the power exported from electromotor 17, spues respectively
Working oil.First, second main pump 11,12 can be with volume adjusted by regulation swash plate angle.The first,
The swash plate angle of the second main pump 11,12 can regulate by means respectively of first, second actuator 13,14.
If by first, second actuator 13,14, regulate the swash plate angle of first, second main pump 11,12
Degree, then can regulate the flow of working oil and pressure spued from first, second main pump 11,12.If
The pressure accessing first, second actuator 13,14 reduces, then first, second actuator 13,14 is permissible
The swash plate angle making first, second main pump 11,12 respectively increases, and makes first, second main pump 11,12
Flow increases.On the contrary, if the pressure accessing first, second actuator 13,14 increases, then first,
Second actuator 13,14 can respectively the swash plate angle of first, second main pump 11,12 reduces, make the
One, the flow of the second main pump 11,12 reduces.
Each pump pressure of first, second main pump 11,12 can be measured and be supplied to control portion.Each
Pump pressure can detect by means of first, second pressure transducer 15,16.First, second pressure
Sensor 15,16 can be respectively arranged at the first hydraulic line 21 and the second hydraulic line 22.
Donkey pump 70 can operate by means of electromotor 17 or other electro-motor.Donkey pump 70 is told
Go out guide's working oil.Can be detected from pressure p c of guide's working oil of donkey pump 70 discharge.Guide's work
Make oil and can be supplied to stick.If manipulation bar, then produce corresponding with the operation displacement of stick
Control signal.Control signal can be the pressure signal corresponding with the operation displacement of stick.This control signal
Act on the spool of multiple control valves that main control valve 30 possesses.
On the other hand, on the first main pump 11, connection has the first hydraulic line 21.On the second main pump 12
Connect and have the second hydraulic line 22.First, second hydraulic line 21,22 is connected to main control valve 30.?
The inside of main control valve 30 can possess multiple control valve.On the first hydraulic line 21, can join in succession
It is equipped with multiple control valve, on the second hydraulic line 22, it is also possible to be configured with multiple control valve in succession.Respectively
Individual control valve operates by means of guide's working oil.If guide's working oil acts on the valve of corresponding control valve
Core, then the spool of corresponding control valve moves, and therefore, working oil is supplied to executor, thus respective actuators
Operate.
Travel control valve unit 31 can be on the second hydraulic line 22 in multiple control valves of configuration
Individual.Travel control valve unit 31 controls the flow direction of the working oil to driving motors 80 supply.
On the other hand, the first hydraulic line 21 can be configured with the first relief valve 41, at the second hydraulic pressure
The second relief valve 42 can be configured with on pipeline 22.First hydraulic line 21 can possess multiple control
Valve processed, is configured with the first relief valve 41 in most downstream.Second hydraulic line 22 can possess multiple control
Valve processed, is configured with the second relief valve 42 in most downstream.
In first, second relief valve 41,42, safe pressure can be set.Thus, when at the first hydraulic pressure
When forming abnormal pressure in pipeline 21, the first relief valve 41 is open, thus, the first hydraulic line 21
Pressure can be maintained at below safe pressure.Similarly, abnormal high when being formed in the second hydraulic line 22
During pressure, the second relief valve 42 is open, thus, the pressure of the second hydraulic line 22 can be maintained at safe pressure
Below power.Safe pressure can be such as 40kgf/cm2。
It addition, the first control valve unit can be configured with in guide's working oil discharge pipeline of donkey pump 70
51.First control valve unit 51 can operate according to the first current signal.The elder generation spued from donkey pump 70
Pressure p c leading working oil could be arranged to the value identical with the safe pressure arranged in the first relief valve 41.
Now, if the first actuator 13 accesses the safe pressure of the first relief valve 41 or spues from donkey pump 70
The pressure of guide's working oil, then can regulate the swash plate inclination angle of the first main pump 11 so that the first main pump
The discharge flow of 11 minimizes.
It addition, possess the second control valve unit 52 on the first hydraulic line 21.
It addition, the 3rd hydraulic line 23 makes donkey pump 70 be connected with the compression zone of the second control valve unit 52.
If the first control valve unit 51 does not access the first current signal, then disconnect being subject to of the second control valve unit 52
Splenium and donkey pump 70.On the contrary, if the first control valve unit 51 inputs the first current signal, then make
The compression zone of two control valve unit 52 is connected with donkey pump 70.That is, if the first control valve unit 51 is opened
Putting, then make guide's working oil pass through, this guide's working oil acts on the compression zone of the second control valve unit 52.
First current signal is to determine the signal whether working oil collaborates.
It addition, the 4th hydraulic line 24 makes the second control valve unit 52 be connected with the second hydraulic line 22.
Second control valve unit 52 operates by means of the guide's working oil via the first control valve unit 51.That is,
If the compression zone at the second control valve unit 52 does not accesses guide's working oil, then, the first main pump 11 is told
The working oil gone out, along the first hydraulic line 21, flow to the first relief valve 41 side.On the contrary, if
The compression zone of two control valve unit 52 accesses guide's working oil, then, from the first hydraulic line 21 to master control
The stream of valve 30 side processed is disconnected, and the working oil spued from the first main pump 11 passes through the 4th hydraulic line 24
Interflow is to the second hydraulic line 22.
It is connected to the five, the 6th hydraulic lines 25,26 in the both sides of shuttle valve 60.5th hydraulic line
25 are connected with the 3rd hydraulic line 23.6th hydraulic line 26 is connected to the downstream of the first hydraulic line 21.
That is, the 6th hydraulic line 26 connects at the entrance of the first relief valve 41.It addition, shuttle valve 60 is by means of
Seven hydraulic lines 27 and be connected with the first actuator 13.The pressure of the 5th hydraulic line 25 of input shuttle valve 60
Power and the pressure competition of the 6th hydraulic line 26, select the working oil of bigger pressure in both, from shuttle valve 60
Output.The first actuator 13 is acted on from the working oil of shuttle valve 60 output.
On the other hand, on the 7th hydraulic line 27, connection has the 8th hydraulic line 28.At the 8th hydraulic tube
The 3rd control valve unit 53 is possessed on line 28.3rd control valve unit 53 can be by means of the second electric current letter
Number or the pressure of the 8th hydraulic line 28 and open.If certain in the first main pump 11 or the second main pump 12
One pump pressure is higher than arranging pressure, then the 3rd control valve unit 53 is open.The height of pump pressure is by controlling portion
Judging, according to the result judged, the second current signal accesses the 3rd control valve unit 53.If the
Three control valve unit 53 are open, then the working oil of the 7th hydraulic line 27 is released.If the 3rd control valve
Unit 53 is open, then the pressure of the 7th hydraulic line 27 reduces.
It is big that pump pressure rising is because job load, it is meant that needs the working oil of more various flow.On the other hand,
If the pressure of the 7th hydraulic line 27 reduces, then the pressure acting on the first actuator 13 reduces, therefore,
First actuator 13 makes the inclination angle of the swash plate of the first main pump 11 increase.Therefore, the telling of the first main pump 11
Outflow increases.If it addition, the pressure acting on the second actuator 14 reduces, then the second actuator 13
The inclination angle making the swash plate of the second main pump 12 increases, and therefore, the discharge flow of the second main pump 12 increases.
Another further aspect, the 3rd control valve unit 53 can be electrical proportional control valve.3rd control valve unit
53 and first main pump 11 pump pressure ps1 and the first relief valve 41 difference of pressure is set and proportionally makes the 8th
The pressure of hydraulic line 28 reduces.If the pressure of the 8th hydraulic line 28 reduces, then the 7th hydraulic line
The pressure of 27 reduces, therefore it provides reduce to the pressure of the working oil of the first actuator 13.Thus,
One load more increases, then the most proportional, the discharge flow of the first main pump 11 can more increase.
<work pattern>
Referring to Fig. 1, the situation that hydraulic system is work pattern of first embodiment of the invention is described.
After operator have selected work pattern, the first current signal does not access the first control valve unit 51.Cause
This, the position of the first control valve unit 51 is not changed.Therefore, guide's working oil is by the first control valve unit
51 cut off, and do not access the compression zone of the second control valve unit 52, thus the second control valve unit 52 is not transported
Turn.Thus, the working oil spued from the first main pump 11 flows to the first relief valve via the first hydraulic line 21
41 sides.When the pressure formed in the first hydraulic line 21 is higher than safe pressure, the first relief valve 41 is opened
Put.
On the other hand, in the first hydraulic line 21, the working oil of flowing is supplied to via the 6th hydraulic line 26
Shuttle valve 60.In shuttle valve 60, in the 6th hydraulic line 26 formed pressure with at the 5th hydraulic line
The pressure competition formed in 25.Now, the 5th hydraulic line 25 is owing to being connected with discharging slot, thus essence
Property pressure can be atmospheric pressure.But, in the 6th hydraulic line 26, formed identical with safe pressure or more
Low pressure.Therefore, at the pressure of the 6th hydraulic line 26 and the 5th hydraulic line of input shuttle valve 60
In the pressure of 25, select the pressure of the 6th hydraulic line 26 and export.Thus, at the 6th hydraulic line 26
In the maximum pressure that can be formed be safe pressure, the pressure of the 6th hydraulic line 26 is via the 7th hydraulic tube
Line 27, accesses the first actuator 13 of the first main pump 11.
Now, from the working oil of the second main pump 12 discharge including travel control valve unit 31, it is provided that give
Each control valve unit possessed in second hydraulic line 22.That is, in work pattern, with stick
Operation correspondence, the spool of control valve unit operates, thus the working oil of high pressure is supplied to executor, energy
Enough perform desired operation.
<driving mode>
Referring to Fig. 2, it is described showing of the operating of the driving mode in the hydraulic system of first embodiment of the invention
Example.Fig. 2 is for the driving mode in the hydraulic system of the engineering machinery of first embodiment of the invention is described
The hydraulic circuit diagram of the example of operating.
Operator can select driving mode.If selection driving mode, then at the first control valve unit 51
Input the first current signal.Therefore, the position of the first control valve unit 51 is changed, thus, from auxiliary
The guide's working oil helping pump 70 to spue is supplied to compression zone and the shuttle valve 60 of the second control valve unit 52.
Second control valve unit 52 is changed by means of the guide's working oil accessing compression zone, disconnects from first
Hydraulic line 21 is to the stream of main control valve 30 side, the first hydraulic line 21 and the 4th hydraulic line 24
Connect, thus, the working oil spued from the first main pump 11 collaborates the second liquid by the 4th hydraulic line 24
Pressure pipeline 22.Therefore, the working oil of more various flow can be provided to driving motors 80, so driving performance obtains
To improving.
On the other hand, in shuttle valve 60, the pressure of the 6th hydraulic line 26 and the 5th hydraulic line 25
Pressure is competed.But, the first hydraulic line 21 is disconnected, thus does not supplies work to the 6th hydraulic line 26
Make oil, thus in the 6th hydraulic line 26, be formed without pressure or form extremely low pressure.On the contrary,
Five hydraulic lines 25 are formed the pressure of guide's working oil.Therefore, when for driving mode, the 5th hydraulic pressure
The pressure of pipeline 25 is exported by shuttle valve 60.Thus, guide's working oil via the 5th hydraulic line 25,
Shuttle valve 60 and the 7th hydraulic line 27 and be supplied to the first actuator 13.Therefore, real in the present invention first
Execute the hydraulic system of example when being driving mode, the first actuator 13 do not access the pressure of guide's working oil,
So, the discharge flow of the first main pump 11 minimizes.It is therefore prevented that the travel speed of engineering machinery is non-
Normal hypervelocity, riding stability mentions raising.It addition, by preventing improper hypervelocity, enabling prevent
Driving system be correlated with element durability deteriorate.
It addition, the first control valve unit 51 is controlled according to current signal, even if in the first control valve
Unit 51 occurs certain unknowable mistake, in the first actuator 13, also accesses the pressure of guide's working oil
Power.Therefore, having without exception unrelated with the first control valve unit 51, the discharge flow of the first main pump 11 is permissible
Maintain minimum.
<driving mode-overload>
Referring to Fig. 3, illustrating under driving mode, overload acts on the situation of traveling.Fig. 3 be for
Illustrate that the hydraulic system of engineering machinery of first embodiment of the invention is to occur overload in driving mode operating
The hydraulic circuit diagram of situation.
Such as, when engineering machinery travels at upward trend, with traveling phase ratio, driving motors on level land
80 working oils that may require that more various flow.If load acts on driving motors 80, then the first main pump 11 or
The pump pressure of the second main pump 12 rises.Now, the pump pressure of the first main pump 11 can be by means of the first pressure
Sensor 15 and be detected as ps1 force value, the pump pressure of the second main pump 12 can by means of second pressure pass
Sensor 16 and be detected as ps2 force value.If the pump pressure of the first main pump 11 or the second main pump 12 rises,
Then by means of control portion, the 3rd control valve unit 53 is open.If the 3rd control valve unit 53 is open, then
The working oil of the seven, the 8th hydraulic lines 27,28 is released, thus the seven, the 8th hydraulic lines 27,
The pressure of 28 reduces.Therefore, in the first actuator 13, the pressure lower than the pressure of guide working oil is accessed
Power.The pressure accessing the first actuator 13 reduces, thus the swash plate angle of the first main pump 11 increases.Thus,
The discharge flow of the first main pump 11 increases.The flow increased collaborates the second hydraulic line 22, it is provided that give row
Sail motor 80.Therefore, even if as when upward trend travels, travel load increases, owing to meeting is to row
Sail motor 80 and the working oil of more various flow is provided, thus driving performance can keep good.
On the other hand, the 3rd control valve 53 is controlled according to current signal, due in the 3rd control valve
53 there is certain unknowable mistake, and the guide's working oil from shuttle valve 60 output cannot be by the 3rd control valve 53
Decompression.Even if in this case, owing to the first actuator 13 operates by means of guide's working oil, because of
And the maximum discharge flow of the first main pump 11 is restricted.It is therefore prevented that the travel speed of engineering machinery is non-
Normal hypervelocity, riding stability is improved.It addition, by preventing improper hypervelocity such that it is able to make
Prevent driving system be correlated with element durability deteriorate.
As it has been described above, the hydraulic system of the engineering machinery of first embodiment of the invention is when for driving mode, from
The working oil that first main pump 11 spues collaborates the working oil spued from the second main pump 12, the working oil at interflow
It is supplied to driving motors 80, thus driving performance can be improved.
Even if it addition, the engineering machinery of the present invention hydraulic system occur the first, the 3rd control valve unit 51,
53 situations that cannot normally control because of unknowable reason, when for driving mode, control the first main pump
The maximum discharge flow of 11 such that it is able to prevent hypervelocity.Thereby, it is possible to guarantee riding stability, and then
It is prevented from driving system durability low.
Fig. 4 is that the hydraulic system of the engineering machinery for second embodiment of the invention is described is transported with work pattern
Hydraulic circuit diagram when turning.Fig. 5 is the hydraulic system of the engineering machinery for second embodiment of the invention is described
Hydraulic circuit diagram when operating with driving mode.Referring to Fig. 4 and 5, to second embodiment of the invention
The hydraulic system of engineering machinery illustrates.
The hydraulic system of second embodiment of the invention can include first, second main pump 11,12, main control
Valve 30, donkey pump the 70, first control valve unit 51', the second control valve unit 52', the 3rd control valve list
Unit 53', shuttle valve 60', first, second, third, fourth, the five, the 6th hydraulic line 21,22,23,
24、95、96。
First, second main pump 11,12 operates by means of the power exported from electromotor 17, spues respectively
Working oil.The swash plate angle of first, second main pump 11,12 can be by means respectively of first, second regulation
Device 13,14 and regulate.Main if by regulating first, second in first, second actuator 13,14
The swash plate angle of pump 11,12, then, from the flow of the working oil that first, second main pump 11,12 spues
Can be adjusted with pressure.If the pressure accessing first, second actuator 13,14 reduces, then,
First, second actuator 13,14 can make the swash plate angle of first, second main pump 11,12 increase respectively,
The flow making first, second main pump 11,12 increases.On the contrary, if access first, second actuator 13,
The pressure of 14 increases, then, first, second actuator 13,14 can make respectively first, second main pump 11,
The swash plate angle of 12 reduces, and makes the flow of first, second main pump 11,12 reduce.
The first, second respective pump pressure of main pump 11,12 can measure and be supplied to control portion.The first,
The pump pressure of the second main pump 11,12 can be examined by means respectively of first, second pressure transducer 15,16
Survey.First, second pressure transducer 15,16 can be respectively arranged at the first hydraulic line 21 and the second liquid
Pressure pipeline 22.
Donkey pump 70 can operate by means of electromotor 17 or other electro-motor.Donkey pump 70 is told
Go out guide's working oil.Pressure p c of the guide's working oil spued from donkey pump 70 can be detected.
First main pump 11 connects and has the first hydraulic line 21.Second main pump 12 connects and has second
Hydraulic line 22.First, second hydraulic line 21,22 is connected to main control valve 30.At main control valve
The inside of 30 can possess multiple control valve.On the first hydraulic line 21, multiple control valves can connect
Continuous configuration, the second hydraulic line 22 times, multiple control valves can also configure continuously.Each control valve is borrowed
Help guide's working oil and operate.If guide's working oil acts on the spool of corresponding control valve, control the most accordingly
The spool of valve processed moves, and therefore, working oil is supplied to executor, thus respective actuators operates.
Travel control valve unit 31 can be on the second hydraulic line 22 in multiple control valves of configuration
Individual.Travel control valve unit 31 controls the flow direction of the working oil to driving motors 80 supply.
First hydraulic line 21 can be configured with the first relief valve 41, on the second hydraulic line 22
The second relief valve 42 can be configured with.First hydraulic line 21 can possess multiple control valve,
Downstream is configured with the first relief valve 41.Second hydraulic line 22 can possess multiple control valve,
Downstream is configured with the second relief valve 42.
In first, second relief valve 41,42, safe pressure can be set.When at the first hydraulic line 21
During middle formation abnormal pressure, the first relief valve 41 is open, thus, the pressure of the first hydraulic line 21 is permissible
It is maintained at below safe pressure.Similarly, when forming abnormal pressure in the second hydraulic line 22, the
Two relief valve 42 are open, thus, the pressure of the second hydraulic line 22 can be maintained at below safe pressure.
First control valve unit 51' can be configured on guide's working oil discharge pipeline 90 of donkey pump 70.
First control valve unit 51' can operate according to the first current signal.The guide's work spued from donkey pump 70
Pressure p c making oil could be arranged to the value identical with the safe pressure arranged in the first relief valve 41.This
Time, if the first actuator 13 accesses the safe pressure of the first relief valve 41 or from donkey pump 70 discharge
The pressure of guide's working oil, then can regulate the swash plate inclination angle of the first main pump 11 so that the first main pump 11
Discharge flow minimize.
Second control valve unit 52' can be configured on the first hydraulic line 21.3rd hydraulic line 23 makes
Donkey pump 70 is connected with the compression zone of the second control valve unit 52'.If the first control valve unit 51' is the most defeated
Enter the first current signal, then disconnect the compression zone donkey pump 70 of the second control valve unit 52'.On the contrary, if
First control valve unit 51' inputs the first current signal, then connect the compression zone of the second control valve unit 52' with
Donkey pump 70.That is, if the first control valve unit 51' is open, then guide's working oil is made to pass through, this guide
Working oil acts on the compression zone of the second control valve unit 52'.
4th hydraulic line 24 makes the second control valve unit 52' and the second hydraulic line 22 connect.Second control
Valve cell 52' processed operates by means of the guide's working oil via the first control valve unit 51'.That is, if existed
The compression zone of the second control valve unit 52' does not accesses guide's working oil, then, spue from the first main pump 11
Working oil, along the first hydraulic line 21, flow to the first relief valve 41 side.On the contrary, if in the second control
The compression zone of valve cell 52' processed accesses guide's working oil, then, disconnect from the first hydraulic line 21 to master control
The stream of valve 30 side processed, the working oil spued from the first main pump 11 is collaborated by the 4th hydraulic line 24
Second hydraulic line 22.
Guide's working oil discharge pipeline 90 connects and has the 5th hydraulic line 95.At the 5th hydraulic line 95
Middle connection has the 3rd control valve unit 53', and connecting in the 3rd control valve unit 53' has the 6th hydraulic line
96.3rd control valve unit 53' makes reduced pressure by guide's working oil of the 5th hydraulic line 95 transmission and exported.
3rd control valve unit 53' can operate according to the second current signal.3rd control valve unit 53' is permissible
For electrical proportional air relief valve (Electronic Proportional Pressure Reducing Valve).From the 3rd control
The working oil of valve cell 53' processed output is input to shuttle valve 60' by the 6th hydraulic line 96.If first is main
Some pump pressure in pump 11 or the second main pump 12 is higher than arranging pressure, then, the 3rd control valve unit
53' can make the pressure of the working oil of output reduce.Now, the 3rd control valve unit 53' can with exceed setting
The pump pressure of the pump of pressure proportionally reduces the pressure of the working oil of output with the difference arranging pressure.
First hydraulic line 21 and the 6th hydraulic line 96 input the input port of shuttle valve 60'.Shuttle valve 60'
Output port can be connected with the first actuator 13.First hydraulic line 21 and the of input shuttle valve 60'
The pressure of six hydraulic lines 96 is at war with, and selects the working oil of the biggest pressure, exports from shuttle valve 60'.
The first actuator 13 is acted on from the working oil of shuttle valve 60' output.
<work pattern>
Referring to Fig. 4, illustrate that the hydraulic system of second embodiment of the invention is situation during work pattern.
After operator have selected work pattern, the first current signal does not access the first control valve unit 51'.Cause
This, the position of the first control valve unit 51' is not changed.Therefore, guide's working oil is by the first control valve unit
51' cuts off, and does not access the compression zone of the second control valve unit 52', thus the second control valve unit 52' is inoperative.
Thus, the working oil spued from the first main pump 11 flows to the first relief valve 41 via the first hydraulic line 21
Side.When the pressure formed in the first hydraulic line 21 is higher than safe pressure, the first relief valve 41 is open.
On the other hand, in the first hydraulic line 21, the working oil of flowing is supplied to shuttle valve 60'.At shuttle valve 60'
In, the pressure formed in the first hydraulic line 21 is carried out with the pressure formed in the 6th hydraulic line 96
Competition.Now, the pressure of pressure ratio the 6th hydraulic line 96 of the first hydraulic line 21 is bigger or identical.
Therefore, in the pressure of the first hydraulic line 21 and the pressure of the 6th hydraulic line 96 of input shuttle valve 60',
Select the pressure of the first hydraulic line 21 and export.
<driving mode>
Referring to Fig. 5, it is described showing of driving mode operating in the hydraulic system of second embodiment of the invention
Example.
Operator can select driving mode.If selection driving mode, then at the first control valve unit 51'
Input the first current signal.Therefore, the position of the first control valve unit 51' is changed, thus, from auxiliary
The guide's working oil helping pump 70 to spue is supplied to the compression zone of the second control valve unit 52'.
Second control valve unit 52' changes by means of the guide's working oil accessing compression zone.Thus, from
One hydraulic line 21 is disconnected to the stream of main control valve 30 side, the first hydraulic line 21 and the 4th hydraulic pressure
Pipeline 24 connects, thus, the working oil spued from the first main pump 11 is collaborated by the 4th hydraulic line 24
To the second hydraulic line 22.Therefore, the working oil of more various flow can be provided to driving motors 80, so row
Sail performance to be improved.
On the other hand, in shuttle valve 60', the pressure of the first hydraulic line 21 and the 6th hydraulic line 96
Pressure is competed.But, the first hydraulic line 21 is disconnected by the second control valve unit 52', thus at the first liquid
The downstream of pressure pipeline 21 is formed without pressure or forms minimum pressure.On the contrary, at the 6th hydraulic line 96
The middle pressure forming guide's working oil.Therefore, when for driving mode, the pressure of the 6th hydraulic line 96
Exported by shuttle valve 60'.The first actuator is accessed from the pressure of the 6th hydraulic line 96 of shuttle valve 60' output
13.Therefore, the hydraulic system of second embodiment of the invention is when for driving mode, at the first actuator 13
The pressure that middle access is identical with the pressure of guide's working oil, thus the discharge flow of the first main pump 11 reaches
Little.It is therefore prevented that the improper hypervelocity of the travel speed of engineering machinery, riding stability is improved.
It addition, the first control valve unit 51' is controlled according to current signal, even if in the first control valve
Unit 51' occurs certain unknowable mistake, in the first actuator 13, also accesses the pressure of guide's working oil
Power.Therefore, having without exception unrelated with the first control valve unit 51', the discharge flow of the first main pump 11 is permissible
Maintain minimum.
<driving mode-overload>
Referring to Fig. 5, illustrating under driving mode, overload acts on the situation of traveling.
Such as, as engineering machinery is when upward trend travels, if load acts on driving motors 80,
So, the pump pressure of the first main pump 11 or the second main pump 12 rises.Now, the pump pressure of the first main pump 11
Power can be detected as ps1 force value by means of the first pressure transducer 15, the pump pressure of the second main pump 12
Ps2 force value can be detected as by means of the second pressure transducer 16.If the first main pump 11 or the second
The pump pressure of main pump 12 rises, then access the second current signal from control portion to the 3rd control valve unit 53'.
If the second current signal accesses the 3rd control valve unit 53', then by the elder generation of the 5th hydraulic line 95 supply
The pressure leading working oil is depressurized, and therefore, the pressure of the 6th hydraulic line 96 reduces.Therefore, first
In actuator 13, access the pressure lower than the pressure of guide working oil.Access the pressure of the first actuator 13
Power reduces, thus the swash plate angle of the first main pump 11 increases.Thus, the discharge flow of the first main pump 11 increases
Adding, the flow of increase collaborates the second hydraulic line 22, it is provided that to driving motors 80.Therefore, even if such as
When upward trend travels like that, travel load increases, owing to can provide more various flow to driving motors 80
Working oil, thus driving performance can keep good.
On the other hand, the 3rd control valve 53' is controlled according to current signal, due in the 3rd control valve
There is certain unknowable mistake in 53', the guide's working oil by the 5th hydraulic line 95 supply cannot be by the
Three control valve 53' decompressions.Even if in this case, owing to accessing guide's work in the first actuator 13
The pressure of oil, thus the discharge flow of the first main pump 11 minimizes.It is therefore prevented that the row of engineering machinery
Sailing the improper hypervelocity of speed, riding stability is improved.
Above by reference to accompanying drawing, illustrate embodiments of the invention, but the technology people of the technical field of the invention
Member is appreciated that the present invention, in the case of not changing its technological thought or required feature, can have with other
Volume morphing is implemented.
Therefore, the embodiment of above description is interpreted as only being exemplary rather than limiting in all respects, the present invention
Scope represented by claims described later, from the meaning of claims and scope and its equivalent concepts
The all changes derived or the form of deformation, also should be interpreted that and be included in the scope of the present invention.
Industrial utilizes probability
The hydraulic system of the engineering machinery of the present invention may be used for improving the driving performance of engineering machinery.
Claims (10)
1. the hydraulic system of an engineering machinery, it is characterised in that including:
First main pump (11), the second main pump (12), the working oil of its high pressure that spues respectively；
Donkey pump (70), its discharge guide's working oil；
First hydraulic line (21), it is connected with described first main pump (11)；
Second hydraulic line (22), it is connected with described second main pump (12)；
Travel control valve unit (31), it is configured on described second hydraulic line (22), controls to row
Sail the flow direction of the working oil that motor (80) is supplied；
First relief valve (41), it is configured on described first hydraulic line (21), makes described first liquid
The pressure of pressure pipeline (21) is maintained at below safe pressure；
First control valve unit (51), when selecting driving mode, this first control valve unit (51) is opened
Put and make described guide's working oil pass through；
Second control valve unit (52), its described by means of via described first control valve unit (51)
Guide's working oil and operate, make the working oil spued from described first main pump (11) be connected to described second liquid
Pressure pipeline (22)；And
Shuttle valve (60), at its two ends, the pressure of described guide's working oil is competed with described safe pressure, makes
The working oil of relatively large pressure is connected to first actuator (13) of described first main pump (11).
The hydraulic system of engineering machinery the most according to claim 1, it is characterised in that
The elder generation that the safe pressure arranged in described first relief valve (41) and described donkey pump (70) spue
The pressure leading working oil arranges identical.
The hydraulic system of engineering machinery the most according to claim 1, it is characterised in that
Including the 3rd control valve unit (53), it is at described first main pump (11) or described second main pump (12)
In a certain pump pressure higher than when arranging pressure, the working oil that provides to described first actuator (13) is provided
Pressure.
The hydraulic system of engineering machinery the most according to claim 3, it is characterised in that
Described 3rd control valve unit (53) is to arrange the difference of pressure proportionally with described pump pressure with described
The electrical proportional control valve of the pressure of the working oil that reduction provides to described first actuator (13).
The hydraulic system of engineering machinery the most according to claim 1, it is characterised in that
When selecting work pattern,
Described first control valve unit (51) connect the compression zone of the spool of the second control valve unit (52) with
Discharging slot,
Described second control valve unit (52) disconnects described first hydraulic line (21) and described second hydraulic pressure
The connection of pipeline (22).
6. the hydraulic system of an engineering machinery, it is characterised in that including:
First main pump (11), the second main pump (12), the working oil of its high pressure that spues respectively；
Donkey pump (70), its discharge guide's working oil；
First hydraulic line (21), it is connected with described first main pump (11)；
Second hydraulic line (22), it is connected with described second main pump (12)；
Travel control valve unit (31), it is configured on described second hydraulic line (22), controls to row
Sail the flow direction of the working oil that motor (80) is supplied；
First relief valve (41), it is configured on described first hydraulic line (21), makes described first liquid
The pressure of pressure pipeline (21) is maintained at below safe pressure；
First control valve unit (51), when selecting driving mode, this first control valve unit (51) is opened
Put and make described guide's working oil pass through；
Second control valve unit (52), its described by means of via described first control valve unit (51)
Guide's working oil and operate, make the working oil spued from described first main pump (11) be connected to described second liquid
Pressure pipeline (22)；
3rd control valve unit (53'), described guide's working oil is reduced pressure and exports by it；And
Shuttle valve (60), at its two ends, the pressure of described first hydraulic line (21) controls with the described 3rd
The output pressure competition of valve cell (53'), makes the working oil of relatively large pressure be connected to described first
First actuator (13) of main pump (11).
The hydraulic system of engineering machinery the most according to claim 6, it is characterised in that
The elder generation that the safe pressure arranged in described first relief valve (41) and described donkey pump (70) spue
The pressure leading working oil arranges identical.
The hydraulic system of engineering machinery the most according to claim 7, it is characterised in that
A certain pump pressure in described first main pump (11) or described second main pump (12) is higher than arranging pressure
During power, described 3rd control valve unit (53') then reduces the pressure of the working oil of output.
The hydraulic system of engineering machinery the most according to claim 8, it is characterised in that
Described 3rd control valve unit (53') sets with described with the pump pressure exceeding the described pump arranging pressure
Put the pressure that the difference of pressure proportionally reduces the working oil of output.
The hydraulic system of engineering machinery the most according to claim 6, it is characterised in that
When selecting work pattern,
Described first control valve unit (51') connects the compression zone of the second control valve unit (52') and releases
Groove,
Described second control valve unit (52') disconnects described first hydraulic line (21) and described second liquid
The connection of pressure pipeline (22).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020140047451A KR102156447B1 (en) | 2014-04-21 | 2014-04-21 | Hydraulic system of construction machinery |
| KR10-2014-0047451 | 2014-04-21 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105003475A CN105003475A (en) | 2015-10-28 |
| CN105003475B true CN105003475B (en) | 2016-12-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510190974.5A Active CN105003475B (en) | 2014-04-21 | 2015-04-21 | The hydraulic system of engineering machinery |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP2937474B1 (en) |
| KR (1) | KR102156447B1 (en) |
| CN (1) | CN105003475B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102540110B1 (en) * | 2017-01-10 | 2023-06-05 | 에이치디현대인프라코어 주식회사 | Hydraulic system for construction machinery |
| KR20180107350A (en) * | 2017-03-16 | 2018-10-02 | 한국로봇융합연구원 | Hydraulic system with optional redundancy |
| KR102461096B1 (en) * | 2017-07-20 | 2022-10-31 | 현대두산인프라코어 주식회사 | Method and apparatus for controlling travelling speed of construction machinery |
| WO2020013358A1 (en) * | 2018-07-12 | 2020-01-16 | Volvo Construction Equipment Ab | Hydraulic machine |
| CN215927944U (en) * | 2021-09-09 | 2022-03-01 | 湖南三一华源机械有限公司 | Hydraulic control system and working machine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06306892A (en) * | 1993-04-23 | 1994-11-01 | Yutani Heavy Ind Ltd | Travel controlling of construction machinery |
| KR20030008069A (en) * | 2001-07-16 | 2003-01-24 | 대우종합기계 주식회사 | Hydraulic apparatus for controlling complex work mode of travel and front works |
| CN101644288A (en) * | 2008-08-08 | 2010-02-10 | 沃尔沃建造设备控股（瑞典）有限公司 | Hydraulic flow sharing system for excavating and pipe laying work |
| CN102011416A (en) * | 2010-11-03 | 2011-04-13 | 三一重机有限公司 | Hydraulic excavator flow rate control method and control loop |
| CN102839709A (en) * | 2011-06-21 | 2012-12-26 | 株式会社久保田 | Working machine |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004027706A (en) | 2002-06-27 | 2004-01-29 | Hitachi Constr Mach Co Ltd | Hydraulic circuit device for construction machinery |
| JP2009179983A (en) * | 2008-01-30 | 2009-08-13 | Caterpillar Japan Ltd | Hydraulic control circuit of working machine |
| KR101893611B1 (en) * | 2011-12-28 | 2018-08-31 | 두산인프라코어 주식회사 | Mileage savings system of Excavator |
-
2014
- 2014-04-21 KR KR1020140047451A patent/KR102156447B1/en active IP Right Grant
-
2015
- 2015-04-21 EP EP15164484.6A patent/EP2937474B1/en active Active
- 2015-04-21 CN CN201510190974.5A patent/CN105003475B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06306892A (en) * | 1993-04-23 | 1994-11-01 | Yutani Heavy Ind Ltd | Travel controlling of construction machinery |
| KR20030008069A (en) * | 2001-07-16 | 2003-01-24 | 대우종합기계 주식회사 | Hydraulic apparatus for controlling complex work mode of travel and front works |
| CN101644288A (en) * | 2008-08-08 | 2010-02-10 | 沃尔沃建造设备控股（瑞典）有限公司 | Hydraulic flow sharing system for excavating and pipe laying work |
| CN102011416A (en) * | 2010-11-03 | 2011-04-13 | 三一重机有限公司 | Hydraulic excavator flow rate control method and control loop |
| CN102839709A (en) * | 2011-06-21 | 2012-12-26 | 株式会社久保田 | Working machine |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2937474B1 (en) | 2022-04-20 |
| CN105003475A (en) | 2015-10-28 |
| EP2937474A2 (en) | 2015-10-28 |
| KR20150121506A (en) | 2015-10-29 |
| KR102156447B1 (en) | 2020-09-15 |
| EP2937474A3 (en) | 2016-04-13 |
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