CN105221399B - Oil pressure actuated systems with failure safe function - Google Patents
Oil pressure actuated systems with failure safe function Download PDFInfo
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- CN105221399B CN105221399B CN201510352194.6A CN201510352194A CN105221399B CN 105221399 B CN105221399 B CN 105221399B CN 201510352194 A CN201510352194 A CN 201510352194A CN 105221399 B CN105221399 B CN 105221399B
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- pressure
- valve
- flow
- oil pressure
- electromagnetic proportional
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Abstract
The present invention provides the oil pressure actuated systems with failure safe function of simple structure.Oil pressure actuated systems with failure safe function control to come from the delivery flow of oil pressure pump using electromagnetic proportional valve electrical resistance.Adjusting the adjuster of the tilt angle of oil pressure pump includes servo cylinder, valve element, horsepower control piston and flow control piston.Imported by a pressure pipe road direction electromagnetic proportional valve and once pressed, secondary pressure is imported from electromagnetic proportional valve to the compression chamber for flow control piston.Electromagnetic proportional valve is controlled in the lower form of instruction current secondary pressure more high.Being used for horsepower by bifurcated pipe road direction controls the compression chamber importing of piston once to press, and bifurcated pipeline is cut off or UNICOM by switching valve with compression chamber.Switching valve has the pilot port for being moved from off-position to communicating position, and the secondary pressure for coming from electromagnetic proportional valve is imported in the pilot port.
Description
Technical field
The present invention relates to the oil pressure actuated systems as the flow for being electrically controlled the working oil discharged from oil pressure pump, can
In the oil pressure actuated systems with failure safe function of the fail-safe ground function of the disconnection that electrical system occurs etc..
Background technology
In the past, it is known to use oil pressure actuated of the electromagnetic proportional valve electrical resistance control from the flow of the working oil of oil pressure pump discharge
System.Oil pressure actuated systems are general such as Fig. 4（a）The shown instruction current for being formed as being input into electromagnetic proportional valve shows with delivery flow
Show positively related positive correlation type.In such oil pressure actuated systems, when breaking down, implementation electromagnetic proportional valve cannot work
In the case of countermeasure.For example, Patent Document 1 discloses the oil pressure actuated with failure safe function as shown in Figure 3
System 100.
Specifically, oil pressure actuated systems 100 possess the oil pressure pump 110 of variable capacity type, adjust verting for oil pressure pump 110
The adjuster 120 at angle, electromagnetic proportional valve 130 and switching valve 140.Adjuster 120 includes and watching that the swash plate of oil pressure pump 110 is connected
Convinced cylinder 121, the valve element 122 for driving servo cylinder 121, the horsepower control piston 124 of operation valve element 122 and flow control are lived
Plug 123.Also, adjuster 120 includes controlling to live for two compression chambers 126,127 of horsepower control piston 124 and for flow
The compression chamber 125 of plug 123.
Pd, horsepower control are pressed in the discharge that oil pressure pump 110 is imported in for the side compression chamber 126 of horsepower control piston 124
Piston processed 124 makes valve element 122 reduce direction movement to flow when discharge pressure Pd rises.Opposite side compression chamber 127 is when usual
Wait and fuel tank（tank）Connection.
For importing flow control pressure in the compression chamber 125 of flow control piston 123, flow controls piston 123 in flow
Control pressure makes valve element 122 be moved to flow increase direction when rising.Proportional control solenoid valve 130 is subject to once to press Psv, and defeated
Go out the secondary pressure as flow control pressure.In addition, horsepower control piston 124 and flow control piston 123 are formed as at it
Among delivery flow be controlled to a less side preferentially make valve element 122 move structure.
When generally, secondary pressure larger to a certain degree is exported from electromagnetic proportional valve 130, therefore switching valve 140 maintains Fig. 3
In left side state, come from electromagnetic proportional valve 130 secondary pressure be directed into for flow control piston 123 compression chamber
In 125.On the other hand, when breaking down, the secondary pressure for coming from electromagnetic proportional valve 130 substantially becomes zero, therefore switching valve
140 states for switching to the right side in Fig. 3.By means of this, first pilot Pp is directed into the compression chamber that piston 123 is controlled for flow
In 125, and once pressure Psv is directed into the compression chamber 127 for horsepower control piston 124.It is directed into once pressure Psv and is received
When in pressure chamber 127, such as Fig. 4（b）Shown, horsepower control characteristic transits to B lines from A lines, discharge stream during by each discharge pressure Pd
The upper limit of amount Q is suppressed to relatively low.
Prior art literature：
Patent document：
Patent document 1：Japanese Unexamined Patent Publication 2005-146969 publications.
The content of the invention
Problems to be solved by the invention：
However, in the oil pressure actuated systems 100 with failure safe function shown in Fig. 3, it is necessary to using six-way valve as
Switching valve 14 is used.Therefore, further expect that structure is simpler, be not easy to cling（stick）And carrying of positively working
The oil pressure actuated systems of failure safe function.
Also, switching valve 140 is switched over when breaking down with lower pressure, therefore presence is easily glued because of pollutant etc.
Problem firmly.Therefore, expect not allowing the cloggy oil pressure actuated systems with failure safe function.
It is therefore an object of the present invention to the work for providing simple structure and being less likely to occur to cause because clinging is bad
The oil pressure actuated systems with failure safe function.
The means of solve problem：
In order to solve the above problems, it is instruction current that the present inventor etc. contemplates the electromagnetic proportional valve for using in the past
It is higher and make the bigger so-called closed type proportioning valve of secondary pressure, if replacing higher using instruction current and making secondary pressure more
Low so-called open type proportioning valve, then can make structure simpler.The present invention is to be formed from such a viewpoint.
That is, the oil pressure actuated systems with failure safe function of the invention possess：The discharge stream corresponding with tilt angle
The oil pressure pump of the working oil of amount；Change the servo cylinder of the tilt angle of the oil pressure pump；Direction is reduced to flow and flow increases
Plus the valve element of direction movement, it is so that the form that the tilt angle reduces drives the servo cylinder that the flow reduces direction
Direction, it is so that the form of tilt angle increase drives the direction of the servo cylinder that the flow increases direction；Described
The discharge pressure of oil pressure pump makes the valve element control piston to the horsepower that the flow reduces direction movement when rising；In flow control
Pressure makes the valve element control piston to the flow that the flow increases direction movement when rising；It is that output is controlled as the flow
The electromagnetic proportional valve of the secondary pressure of pressure, and instruction current is higher and make the lower electromagnetic proportional valve of the secondary pressure；From the electricity
Magnetic proportioning valve is introduced directly into the secondary pressure pipe road of the secondary pressure to the compression chamber for flow control piston；To the electricity
Magnetic proportioning valve imports the pressure pipe road once pressed；It is directed into for institute from the once pressure line branches and by the once pressure
State the bifurcated pipeline of the compression chamber of horsepower control piston；It is to control receiving for piston by the bifurcated pipeline and for the horsepower
Off-position and the bifurcated pipeline is connected with the compression chamber for horsepower control piston that pressure chamber is cut off
Communicating position between switch switching valve, and with for the switching valve is maintained the off-position spring and use
In the pilot port for making the switching valve be moved to the communicating position from the off-position with the force confrontation of the spring
Switching valve；With the pilot line of the pilot port for connecting the secondary pressure pipe road and the switching valve.
According to said structure, secondary pressure less to a certain degree, therefore switching are exported from electromagnetic proportional valve when usual
Valve maintains off-position because of the force of the spring of switching valve.By means of this, in for the compression chamber of horsepower control piston
Do not import and once press.And, the secondary pressure for coming from electromagnetic proportional valve is imported in for the compression chamber of flow control piston, because
This can carry out the flow control of the electrical resistance corresponding with the instruction current being input into electromagnetic proportional valve.On the other hand, in event
During barrier, secondary pressure from electromagnetic proportional valve output with once press roughly equal, therefore switching valve switches to communicating position.By means of
This, once pressure is directed into the compression chamber that piston is controlled for horsepower.For flow control piston compression chamber in be also introduced into
Roughly equal secondary pressure is once pressed, but applies once to press and discharge pressure, and horsepower control piston to horsepower control piston
Attempt to reduce tilt angle compared with flow control piston, therefore only perform horsepower control.By means of this, can also in failure
By a certain degree of horsepower of driving oil pressure actuator.Additionally, as switching valve, it is possible to use the less valve of port number, because
This can realize simple structure.Additionally, magnetic valve switches to connection position because of pressure higher in failure from off-position
Put, therefore, it is difficult to occur to work bad caused by because clinging etc..
For example, the above-mentioned oil pressure actuated systems with failure safe function can also possess makes what oil pressure actuator worked
When pilot-operated type operation valve is operated, the instruction current that will be improved with the first pilot exported from the operation valve and reduced is defeated
Deliver to the control device of the electromagnetic proportional valve.
Invention effect：
According to the present invention it is possible to provide the oil pressure actuated with failure safe function positively worked with simple structure
System.
Brief description of the drawings
Fig. 1 is that a kind of oil pressure of the oil pressure actuated systems with failure safe function of embodiment of the invention is returned
Lu Tu；
Fig. 2 in Fig. 2（a）Be show in the oil pressure actuated systems shown in Fig. 1 from operation valve output first pilot Pp and
To the chart of the relation between the instruction current I that electromagnetic proportional valve is input into, Fig. 2（b）It is instruction current I to be shown and comes from electromagnetism
The chart of the relation between the secondary pressure P2 of proportioning valve, Fig. 2（c）The figure of relation of the secondary pressure between P2 and delivery flow Q is shown
Table, Fig. 2（d）Relation between instruction current I and delivery flow Q is shown（Input-output characteristic）Chart；
Fig. 3 is the oil hydraulic circuit figure of the existing oil pressure actuated systems with failure safe function；
Fig. 4 in Fig. 4（a）It is the chart of the input-output characteristic for showing common existing oil pressure actuated systems, Fig. 4（b）
It is the chart of the horsepower characteristic for showing the oil pressure actuated systems shown in Fig. 3;
Symbol description：
1 oil pressure actuated systems with failure safe function；
2 oil pressure pumps；
31 servo cylinders；
32 valve elements；
35 flows control piston；
36 horsepowers of control pistons；
37~39 compression chambers；
4 electromagnetic proportional valves；
41 pressure pipe roads；
42 2 pressure pipe roads；
43 pilot lines；
5 bifurcated pipelines；
6 switching valves；
61 pilot ports；
7 control devices.
Specific embodiment
Fig. 1 shows a kind of oil pressure actuated systems 1 with failure safe function of embodiment of the invention.The oil
Pressure drive system 1 is for example equipped in the building machinery of hydraulic excavator or oil pressure crane etc., and is performed to various oil pressure
Device（It is not shown）Supply working oil.
Specifically, oil pressure actuated systems 1 possess the oil pressure pump 2 of variable capacity type, the tune of the tilt angle of regulation oil pressure pump 2
Section device 3, electromagnetic proportional valve 4 and switching valve 6.Also, oil pressure actuated systems 1 possess the control to the conveying instruction current of electromagnetic proportional valve 4 I
Device processed 7.
Oil pressure pump 2 discharges the working oil of the flow corresponding with tilt angle.In this embodiment, as oil pressure pump 2, adopt
With the inclined rotor pump of the angle block gauge constant inclination corner by swash plate 21.However, oil pressure pump 2 can also be by the angle block gauge constant inclination corner of inclined shaft
Inclined shaft pump.
Adjuster 3 includes：Change the servo cylinder 31 of the tilt angle of oil pressure pump 2；Adjust for driving servo cylinder 31
The valve element 32 of control pressure；With the valve pocket 33 for accommodating valve element 32.Servo cylinder 31 is connected with the swash plate 21 of oil pressure pump 2.Valve element 32
And valve pocket 33 constitutes the pressure-regulating valve 34 for servo cylinder 31.
More specifically, valve element 32 is reducing direction to flow（The right direction of Fig. 1）When mobile（Switch to leftward position
When）So that the form that the tilt angle of oil pressure pump 2 reduces drives servo cylinder 31, and increasing direction to flow（The left of Fig. 1
To）When mobile（When switching to right positions）So that the form of the tilt angle increase of oil pressure pump 2 drives servo cylinder 31.Valve pocket 33
It is connected with servo cylinder 31 by the first bar 3a, pump discharge pressure Pd acts on the path side of servo cylinder 31, and is adjusted by pressure
The control pressure of the section pressure regulation of valve 34 acts on the big footpath side of servo cylinder 31.So that from the double side acting of servo cylinder 31 thereon
Power（Pressure × servo cylinder compression area）Control pressure of the form regulation for balancing each other from the output of pressure-regulating valve 34.Like this,
Pressure-regulating valve 34 is so that the relative position of valve element 32 and valve pocket 33（Measurement characteristicses）Keep certain form work.Like this,
Valve pocket 33 is moved along with the movement of valve element 32.
Also, adjuster 3 includes the flow control piston 35 of operation valve element 32 and horsepower control piston 36.Flow control is lived
Plug 35 and horsepower control piston 36 are connected by the second bar 3b and the 3rd bar 3c with valve element 32 respectively.Additionally, adjuster 3 is wrapped
Include the compression chamber 37 that piston 35 is controlled for two compression chambers 38,39 of horsepower control piston 36 and for flow.
Pd is pressed in the discharge that oil pressure pump 2 is imported in for the side compression chamber 38 of horsepower control piston 36.Horsepower control is lived
Plug 36 makes valve element 32 be moved to flow reduction direction when discharge pressure Pd rises, and valve element 32 is made to flow in discharge pressure Pd reductions
Increase direction movement.Opposite side compression chamber 39 is connected by downstream pipe 52 with switching valve 6.
Flow control pressure is imported in for the compression chamber 37 of flow control piston 35.Flow controls piston 35 in flow control
System pressure makes valve element 32 be moved to flow increase direction when rising, valve element 32 is reduced direction to flow when flow control pressure drop is low
It is mobile.In addition, horsepower control piston 36 and flow control piston 35 are formed as limiting among them a side of delivery flow Q
（Send a side of the instruction of less flow）The structure for preferentially moving valve element 32.
Compression chamber 37 for flow control piston 35 is connected by secondary pressure pipe road 42 with electromagnetic proportional valve 4, electromagnetism ratio
Example valve 4 is connected by a pressure pipe road 41 with auxiliary pump 25.That is, imported to electromagnetic proportional valve 4 by a pressure pipe road 41 and come from
In the once pressure P1 of auxiliary pump 25.
Electromagnetic proportional valve 4 exports secondary pressure P2 and controls to press as the flow.By the secondary pressure P2 by secondary pressure pipe
Road 42 imports directly and often from electromagnetic proportional valve 4 to compression chamber 37.Electromagnetic proportional valve 4 such as Fig. 2（b）Shown, instruction current I gets over
It is high and make secondary pressure P2 lower.When secondary pressure P2 is reduced, flow control piston 35 makes valve element 32 reduce direction movement to flow.
Therefore, relation of the secondary pressure between P2 and delivery flow Q is such as Fig. 2（c）It is shown, the pass between instruction current I and delivery flow Q
System is such as Fig. 2（d）It is shown.
Such as Fig. 2（d）Shown, oil pressure actuated systems 1 are that the instruction current I and delivery flow Q being input into electromagnetic proportional valve 4 shows
The negatively correlated type of negative correlation is shown.Therefore, control device 7 grasps the pilot-operated type that the oil pressure actuator that diagram is omitted works in operation
When making valve, such as Fig. 2（a）It is shown, the instruction current I for being improved with the first pilot Pp exported from operation valve and being reduced is delivered to electricity
Magnetic proportioning valve 4.
Fig. 1 is back to, one time pressure pipe road 41 is connected by upstream 51 with switching valve 6.That is, upstream 51 and on
Downstream pipe 52 is stated to constitute from a bifurcated of pressure pipe road 41 and by once pressure P1 to the compression chamber 39 for horsepower control piston 36
The bifurcated pipeline 5 of importing.
Switching valve 6 by bifurcated pipeline 5 with for horsepower control piston 36 compression chamber 39 cut off off-position,
Switch and the communicating position that bifurcated pipeline 5 is connected with the compression chamber 39 for horsepower control piston 36 between.In this reality
Apply in form, switching valve 6 is also connected with fuel tank pipeline 55, when switching valve 6 is located at off-position, downstream pipe 52 and tank tube
Road 55 connects.
More specifically, switching valve 6 has for the switching valve 6 to be maintained into the spring 62 of off-position and for making
The pilot port 61 that the switching valve 6 is moved with the force confrontation ground of spring 62 from off-position to communicating position.Pilot port 61
It is connected with secondary pressure pipe road 42 by pilot line 43.That is, the secondary pressure P2 for coming from electromagnetic proportional valve 4 leads to pilot port 61
Enter.
Spring 62 such as Fig. 2（b）It is shown, when playing based on the secondary pressure P2 decision judgement failures for coming from electromagnetic proportional valve 4
Carve（Switching switching valve 6）Threshold value effect.For example, such as Fig. 2（c）Shown, secondary pressure P2 has does not influence that delivery flow Q's is low
Pressure side non-reactive zone and high-pressure side non-reactive zone.Threshold value is preferably more than the minimum value of high-pressure side non-reactive zone, and less than two
The maximum of secondary pressure P2.The maximum of secondary pressure P2 is with once to press P1 roughly equal be self-evident.For switching switching valve 6
Threshold value using close to the high-voltage value for once pressing P1, therefore the force of spring 62 can be set as sufficiently large.Therefore, occurring
During failure, the reason for can positively prevent because of pollutant etc. and switching valve 6 is clung and causes work bad.
Then, the action of oil pressure actuated systems 1 is illustrated.
When generally, secondary pressure P2 less to a certain degree is exported from electromagnetic proportional valve 4, therefore switching valve 6 is because of spring 62
Force and maintain off-position.By means of this, the compression chamber 39 for not being directed into and piston 36 being controlled for horsepower is once pressed, be pressurized
The pressure of room 39 essentially becomes zero.By means of this, the discharge pressure Pd for being only directed into compression chamber 38 acts on horsepower control piston
36, and be based only upon the horsepower control of discharge pressure Pd.The horsepower carried out for controlling piston 36 by this horsepower is controlled, by
In with Fig. 4（b）In A lines be set as horsepower very high in the same manner, be greater than the horsepower of engine horsepower, therefore usual
When do not limit delivery flow Q.That is, when usual, the effect for only controlling piston 35 by flow controls delivery flow Q.And
And, the secondary pressure P2 for coming from electromagnetic proportional valve 4 is imported in for the compression chamber 37 of flow control piston 35, therefore can enter
The row electrical resistance flow control corresponding with the instruction current I being input into electromagnetic proportional valve 4.
On the other hand, in failure, from electromagnetic proportional valve 4 output secondary pressure with once press roughly equal, therefore switch
Valve 6 is switched to communicating position.By means of this, P1 is once pressed to be directed into the compression chamber 39 that piston 36 is controlled for horsepower.Also,
For being also introduced into the compression chamber 37 of flow control piston 35 and once pressing roughly equal secondary pressure P2.Piston is controlled to horsepower
36 apply once pressure P1 and discharge pressure Pd, make horsepower control piston 36 to work with this, and carry out a horsepower control.That is, horsepower control
Piston processed 36 attempts to reduce tilt angle compared with flow control piston 35, therefore only performs horsepower control.By means of this, in event
During barrier, horsepower that can be by a certain degree of horsepower, for example smaller than engine horsepower drives oil pressure actuator（It is not shown）.
Also, in this embodiment, as switching valve 6, it is possible to use the less valve of port number, therefore letter can be realized
Single structure.
Also, the force of spring 62 can be set as it is sufficiently large, and in failure switching valve 6 because of pressure higher from
Off-position switches to communicating position, therefore can positively prevent from switching valve 6 from being clung because of the reason for pollutant etc. causing work
Make bad.
（Variation）
The invention is not restricted to above-mentioned embodiment, various changes can be carried out without departing from the spirit and scope of the invention
More.
Although for example, diagram omission, can be two oil pressure supply that oil pressure actuated systems 1 are assembled in double pump mode
In one side of pipeline.In this case, or adjuster 3 also include for horsepower control piston 36 another compression
Room, imports the discharge pressure of the oil pressure pump of the opposing party in the compression chamber.
Industrial applicability：
Oil pressure actuated systems of the invention can apply in various oil hydraulic circuits.
Claims (2)
1. a kind of oil pressure actuated systems with failure safe function, possess：
The oil pressure pump of the working oil of the discharge flow corresponding with tilt angle；
Change the servo cylinder of the tilt angle of the oil pressure pump；
Reducing direction and flow to flow increases the valve element that direction is moved, and it is so that the tilt angle that the flow reduces direction
The form of reduction drives the direction of the servo cylinder, and it is so that the form of tilt angle increase is driven that the flow increases direction
Move the direction of the servo cylinder；
Make the valve element that the horsepower for moving in direction is reduced to the flow when the discharge pressure of the oil pressure pump rises and control piston；
The valve element is increased the flow for moving in direction to the flow when flow control pressure rises and control piston；
It is electromagnetic proportional valve of the output as the secondary pressure of flow control pressure, and instruction current is higher and make the secondary pressure
Lower electromagnetic proportional valve；
The secondary pressure of the secondary pressure is introduced directly into the compression chamber for flow control piston from the electromagnetic proportional valve
Pipeline；
The pressure pipe road once pressed is imported to the electromagnetic proportional valve；
Dividing for the compression chamber for horsepower control piston is directed into from the once pressure line branches and by the once pressure
Breeches pipe road；
It is by the bifurcated pipeline and the off-position cut off of compression chamber for horsepower control piston and by institute
The switching valve switched between the communicating position that bifurcated pipeline is connected with the compression chamber for horsepower control piston is stated, and
With for the switching valve to be maintained the spring of the off-position and right with the force of the spring for making the switching valve
The switching valve of the pilot port for being moved to the communicating position from the off-position anti-ly；With
Connect the pilot line of the pilot port of the secondary pressure pipe road and the switching valve.
2. oil pressure actuated systems with failure safe function according to claim 1, it is characterised in that
When the pilot-operated type operation valve for being also equipped with making oil pressure actuator to work is operated, the first pilot exported from the operation valve is got over
The high and smaller instruction current is delivered to the control device of the electromagnetic proportional valve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-133548 | 2014-06-30 | ||
| JP2014133548A JP2016011633A (en) | 2014-06-30 | 2014-06-30 | Hydraulic drive system with fail-safe |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105221399A CN105221399A (en) | 2016-01-06 |
| CN105221399B true CN105221399B (en) | 2017-06-20 |
Family
ID=54990585
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510352194.6A Expired - Fee Related CN105221399B (en) | 2014-06-30 | 2015-06-24 | Oil pressure actuated systems with failure safe function |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2016011633A (en) |
| CN (1) | CN105221399B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6757238B2 (en) * | 2016-11-24 | 2020-09-16 | 川崎重工業株式会社 | Hydraulic drive system |
| JP7253933B2 (en) * | 2019-02-08 | 2023-04-07 | 川崎重工業株式会社 | hydraulic drive system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002317771A (en) * | 2001-04-23 | 2002-10-31 | Kawasaki Heavy Ind Ltd | Hydraulic pump control device |
| CN1670317A (en) * | 2004-03-18 | 2005-09-21 | 神钢建设机械株式会社 | Hydraulic control device for working machine |
| JP4041789B2 (en) * | 2003-11-14 | 2008-01-30 | 株式会社カワサキプレシジョンマシナリ | Pump flow controller with fail safe |
| JP2011256814A (en) * | 2010-06-10 | 2011-12-22 | Sumitomo (Shi) Construction Machinery Co Ltd | Pump discharge amount control circuit for construction machine |
| CN202789797U (en) * | 2012-03-20 | 2013-03-13 | 龙工（上海）桥箱有限公司 | Inversely-proportional electromagnetic pressure-reducing valve |
| CN103306329A (en) * | 2013-05-28 | 2013-09-18 | 上海三一重机有限公司 | Control system for micro-controlling hydraulic shear based on excavating machine and method and excavating machine |
-
2014
- 2014-06-30 JP JP2014133548A patent/JP2016011633A/en active Pending
-
2015
- 2015-06-24 CN CN201510352194.6A patent/CN105221399B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002317771A (en) * | 2001-04-23 | 2002-10-31 | Kawasaki Heavy Ind Ltd | Hydraulic pump control device |
| JP4041789B2 (en) * | 2003-11-14 | 2008-01-30 | 株式会社カワサキプレシジョンマシナリ | Pump flow controller with fail safe |
| CN1670317A (en) * | 2004-03-18 | 2005-09-21 | 神钢建设机械株式会社 | Hydraulic control device for working machine |
| JP2011256814A (en) * | 2010-06-10 | 2011-12-22 | Sumitomo (Shi) Construction Machinery Co Ltd | Pump discharge amount control circuit for construction machine |
| CN202789797U (en) * | 2012-03-20 | 2013-03-13 | 龙工（上海）桥箱有限公司 | Inversely-proportional electromagnetic pressure-reducing valve |
| CN103306329A (en) * | 2013-05-28 | 2013-09-18 | 上海三一重机有限公司 | Control system for micro-controlling hydraulic shear based on excavating machine and method and excavating machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2016011633A (en) | 2016-01-21 |
| CN105221399A (en) | 2016-01-06 |
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Granted publication date: 20170620 Termination date: 20190624 |