CN103727082B - Hydraulic system and engineering machinery - Google Patents
Hydraulic system and engineering machinery Download PDFInfo
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- CN103727082B CN103727082B CN201310738257.2A CN201310738257A CN103727082B CN 103727082 B CN103727082 B CN 103727082B CN 201310738257 A CN201310738257 A CN 201310738257A CN 103727082 B CN103727082 B CN 103727082B
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Abstract
The invention discloses a kind of hydraulic system and engineering machinery.This hydraulic system includes hydraulic pump, main control valve, pressure-difference valve and controller；Wherein: pressure-difference valve is arranged between the oil drain out of hydraulic pump and the load feedback hydraulic fluid port of main control valve, for adjusting the pressure reduction of oil drain out and load hydraulic fluid port；The input of controller is connected with throttle, is used for receiving throttle signal；First outfan is connected with pressure-difference valve, for controlling the pressure reduction regulated quantity of pressure-difference valve according to throttle signal.Above-mentioned hydraulic system can control main control valve valve rod flow according to the size of throttle signal, the most no matter electromotor is in idling is at a high speed, the regulation of flow can be realized in whole strokes of the valve rod of main valve, the i.e. Flow-rate adjustment gain of main valve during idling is little, fine motion is good, during high speed, the Flow-rate adjustment gain of main valve is big, meets the requirement at a high speed of big flow.
Description
Technical field
The present invention relates to technical field of hydraulic pressure, particularly to a kind of hydraulic system and engineering machinery.
Background technology
Crane is a kind of facility for the conveying material that hoists, and is widely used in construction site, harbour code
Hoisting operation under the operating modes such as head, oil field, railway, warehouse, wind-powered electricity generation and lifting operation.In recent years, along with
The quickening of engineering construction step, the effect that crane plays in all conglomeraties is the most increasing, to crane
The improvement of fretting performance is the most increasingly subject to people's attention.
At present, crane uses valve control form mostly, is i.e. realized by the aperture area of change main valve valve rod
The control of flow, in limited control stroke, the maximum open design of valve rod needs to meet actuator speed
The requirement of degree.And in order to keep stablizing of flow, pressure-compensated valve is often set before the valve of main valve or after valve,
Before and after realizing main valve, pressure reduction is constant.This pressure reduction generally by the spring of pressure-compensated valve or oil pump feedback at
Spring determines (LUDV system), is a fixed value, therefore the output flow of main valve only with the opening of its valve rod
Area is correlated with.The technical problem that existing hydraulic system exists is as follows:
The input speed of most hoist pumps can pass through throttle from idling (about 800r/min) at a high speed
(2000r/min) continuously adjust.Under idling operation, at the leading portion of valve core of main valve stroke, now main valve
Output flow is less than the output flow of oil pump, and the output flow of main valve can be carried out according to the area change of valve port
Continuously adjust, and at the back segment of valve rod travel, owing to the output flow of oil pump limits, main valve output flow is permanent
Fixed, equal to the output flow of oil pump.Therefore, during idling, main valve is real merely with a part for its whole strokes
Existing Flow-rate adjustment or speed regulation.Further, since the rate request of part actuator (such as elevator), need
Main valve can export big flow when high engine speeds (such as 2000r/min), it is therefore desirable to main valve is at limited row
The big aperture area gain realized in journey.This reduces vehicle fine motion and handling when idling operation.
The most existing hydraulic system is difficult to take into account running up of complete machine and is difficult to and the requirement of good fretting performance.
Summary of the invention
In view of this, the present invention proposes a kind of to take into account running up and good fretting performance of complete machine
The hydraulic system required and engineering machinery.
For reaching above-mentioned purpose, the technical scheme is that and be achieved in that:
On the one hand, the present invention provides a kind of hydraulic system, including hydraulic pump, main control valve, pressure-difference valve
And controller；Wherein: described pressure-difference valve is arranged at the oil drain out of described hydraulic pump and described main control valve
Load feedback hydraulic fluid port between, for adjusting the pressure reduction of described oil drain out and described load hydraulic fluid port；Described control
The input of device is connected with throttle, is used for receiving throttle signal；First outfan is connected with pressure-difference valve,
For controlling the pressure reduction regulated quantity of described pressure-difference valve according to described throttle signal.
Further, described hydraulic pump is variable pump；Described pressure-difference valve includes spool control valve and the first ratio
Example electric magnet；Described first proportion electro-magnet is connected with the outer end of the valve core spring of described spool control valve；Described
First hydraulic control hydraulic fluid port of spool control valve communicates with the oil drain out of described variable pump, the second hydraulic control hydraulic fluid port and described master
The load feedback hydraulic fluid port of control valve communicates；Feedback hydraulic fluid port is connected with the Variable Control piston of variable pump；Described
One proportion electro-magnet is connected with described controller.
Further, described main control valve includes: main reversing valve and pressure-compensated valve, described pressure-compensated valve
Oil-in communicate with the oil-out of described main reversing valve；Oil-out is oily with the load feedback of described main reversing valve
Mouth communicates.
Further, described hydraulic pump is dosing pump, and described pressure-difference valve includes uniform-pressure-drop valve and second
Proportion electro-magnet: described second proportion electro-magnet is connected with the outer end of the valve core spring of described air relief valve；Described
The oil-in of air relief valve communicates with the oil drain out of described dosing pump, feedback hydraulic fluid port and the load of described main control valve
Feedback hydraulic fluid port communicates；Described second proportion electro-magnet is connected with described controller.
Further, described throttle is E-Gas.
Further, the second outfan of described controller is connected, for root with the electromotor of described hydraulic pump
The rotating speed of described electromotor is controlled according to described throttle signal.
Further, described controller includes: receives unit, is used for accepting described throttle signal；Conversion is single
Unit, for obtaining engine rotational speed signal according to described throttle signal；Processing unit, for according to described
Motivation tach signal regulates the pressure reduction regulated quantity of described pressure-difference valve.
Further, described hydraulic system also includes: the execution being connected with the actuator port of described main control valve
Mechanism,
On the other hand, the present invention also provides for a kind of engineering machinery, is provided with the hydraulic pressure described in above-mentioned any one
System.
Further, described engineering machinery is crane.
The present invention provides a kind of hydraulic system, adjusts referring now to being provided with pressure reduction in prior art, this hydraulic system
The adjustable pressure-difference valve of joint amount, for regulating the pressure reduction between hydraulic oil oil drain out and load feedback hydraulic fluid port,
It is additionally provided with controller simultaneously, the controller pressure reduction regulated quantity by throttle signal size adjustment pressure-difference valve,
And then control hydraulic pump oil drain out and the pressure reduction of load feedback hydraulic fluid port, and then finally realize whole hydraulic system
Can control main control valve valve rod flow according to the size of throttle signal, the most no matter electromotor is in idle
Speed is at a high speed, to realize the regulation of flow, i.e. idling in whole strokes of the valve rod of main valve
Time the Flow-rate adjustment gain of main valve little, fine motion is good, and during high speed, the Flow-rate adjustment gain of main valve is big, meets
The requirement at a high speed of big flow.
Accompanying drawing explanation
The accompanying drawing of the part constituting the present invention is used for providing a further understanding of the present invention, and the present invention shows
Meaning property embodiment and explanation thereof are used for explaining the present invention, are not intended that inappropriate limitation of the present invention.At accompanying drawing
In:
The theoretical pass of output flow and the slight formation of handle in the hydraulic system that Fig. 1 provides for the embodiment of the present invention
It it is curve；
The principle schematic of the hydraulic system that Fig. 2 provides for the embodiment of the present invention one；
The hydraulic schematic that Fig. 3 provides for the embodiment of the present invention two.
Description of reference numerals:
11 variable pump P0 oil drain outs
111 Variable Control piston 112 electromotors
21 main control valve LS1 load feedback hydraulic fluid ports
P1 oil-in D1 oil-out
211 main reversing valves
212 uniform-pressure-drop valve C1 oil-ins
C2 oil-out
311 spool control valve A1 the first hydraulic control hydraulic fluid ports
A2 the second hydraulic control hydraulic fluid port A3 feeds back hydraulic fluid port
312 first proportion electro-magnets
41 controllers
51 throttles
12 dosing pump P2 oil drain outs
122 electromotors
22 main control valve LS2 load feedback hydraulic fluid ports
321 air relief valve B1 oil-ins
B2 second feeds back hydraulic fluid port 322 second proportion electro-magnet
42 controllers
52 throttles
Detailed description of the invention
It should be noted that in the case of not conflicting, the embodiment in the present invention and the feature in embodiment
Can be mutually combined.
The embodiment of the present invention provides a kind of hydraulic system, including: hydraulic pump, main control valve, pressure-difference valve
And controller；Wherein,
Pressure-difference valve is arranged between the oil drain out of hydraulic pump and the load feedback hydraulic fluid port of main control valve, is used for
Adjust the pressure reduction of above-mentioned oil drain out and load feedback hydraulic fluid port；The input of controller is connected with throttle, is used for connecing
Receive throttle signal；First outfan is connected with pressure-difference valve, for controlling pressure reduction regulation according to throttle signal
The pressure reduction regulated quantity of valve.
The present embodiment provide hydraulic system in, hydraulic pump under the effect of its transmitter to whole hydraulic system
Pumping pressure oil.Main control valve can be existing reversal valve, for always being controlled by control hydraulic oil flow
The running of hydraulic actuating mechanism.This main control valve is provided with load feedback hydraulic fluid port, for the pressure of feedback load.
Pressure-difference valve is for adjusting the pressure reduction between the oil-in of main control valve and load feedback hydraulic fluid port, i.e. main control
The pressure reduction pressure reduction that the spool of valve is imported and exported, hereinafter referred to as inlet outlet pressure differential；This pressure-difference valve is arranged at hydraulic pressure
Between pump oil drain out and load feedback hydraulic fluid port, unlike the prior art: the pressure reduction of this pressure-difference valve is adjusted
Joint amount is adjustable, and the regulation of pressure reduction regulated quantity is realized by controller.The input termination of controller receives throttle letter
Number, controller controls the pressure reduction regulated quantity of pressure-difference valve according to this throttle signal.It is achieved in hydraulic pump
The pressure reduction of oil drain out and load feedback hydraulic fluid port can be adjusted accordingly according to throttle size.
Above-mentioned pressure-difference valve can be the adjustable hydraulic valve of pre compressed magnitude of valve core spring, valve core spring i.e.
Preload pressure is adjustable.Concrete Principles of Regulation are as follows: pressure-difference valve can accept the control signal that controller sends,
And accordingly by adjusting the pre compressed magnitude of valve core spring, the change of valve core spring pre compressed magnitude realizes pressure reduction regulation
The regulation of the pressure reduction regulated quantity of valve.
On the premise of main control valve aperture area is certain, the pressure reduction regulated quantity of pressure-difference valve and hydraulic system
Output flow be directly proportional, the relationship of the two is as shown in formula I:
Q=Cd×S×(ΔP)nFormula I
In above formula: Q is the output flow of hydraulic system, CdFor discharge coefficient；S is the opening of main control valve
Area；Δ P is the import and export of the pressure differential between hydraulic oil oil drain out and load feedback hydraulic fluid port, i.e. main control valve
Pressure reduction, namely the pressure reduction regulated quantity of above-mentioned pressure-difference valve, lower with；N is and main control valve restriction
The coefficient that the structure at place is relevant, takes between 0～1.
Above-mentioned pressure reduction regulated quantity Δ P can be directly proportional to throttle signal；As a example by crane, refer to Fig. 1,
Under idling operation, throttle no signal exports, and the throttle signal that controller receives is minima, correspondingly,
The valve core spring pre compressed magnitude now controlling pressure-difference valve is less, i.e. pressure reduction regulated quantity is the least, now leads
The increment of control valve flow reduces, and is conducive to improving the fretting performance of complete machine；Under high-speed working condition, controller
The throttle signal received is relatively big, and correspondingly, the valve core spring pre compressed magnitude now controlling pressure-difference valve is relatively big,
I.e. pressure reduction regulated quantity is the biggest, is thus conducive to meeting the requirement that complete machine runs up.
As shown in the above, the hydraulic system that the embodiment of the present invention provides can realize throttle by controller and believe
The amount of differential pressure of number size and pressure-difference valve associate regulation, and then adjust what main control valve was imported and exported pressure reduction,
Finally realize whole hydraulic system and can control the changes in flow rate of main control valve according to the size of throttle signal,
The most no matter electromotor is in idling is at a high speed, can in whole strokes of the valve rod of main valve
The Flow-rate adjustment gain realizing the regulation of flow, i.e. main valve during idling is little, and fine motion is good, main valve during high speed
Flow-rate adjustment gain big, meet the requirement at a high speed of big flow.
The specific constructive form of pressure-difference valve and the annexation with other Hydraulic Elements, can be according to liquid
The type of press pump selects.Below in conjunction with the accompanying drawings, respectively with variable pump hydraulic system and dosing pump hydraulic pressure
Further each preferred embodiment of the present invention is explained as a example by system:
Refer to Fig. 2, the figure shows the principle of the hydraulic system that the embodiment of the present invention one provides, this hydraulic pressure
System is load-sensitive pump hydraulic system, and the hydraulic pump in this system is variable pump 11；Pressure-difference valve includes
Spool control valve 311 and the first proportion electro-magnet 312；
First proportion electro-magnet 312 is arranged at the outer end of the valve core spring of spool control valve 311；
First hydraulic control hydraulic fluid port A1 of spool control valve 311 communicates with the oil drain out P0 of variable pump 11, the second liquid
Control hydraulic fluid port A2 communicates with the load feedback hydraulic fluid port LS1 of main control valve 21；Feedback hydraulic fluid port A3 and variable pump 11
Variable Control piston 111 be connected；
Above-mentioned first proportion electro-magnet 312 is connected with controller 41.
In the hydraulic system of the present embodiment, one end of the spool control valve 311 in pressure-difference valve (in Fig. 2 is
Left end) it is provided with the first hydraulic control hydraulic fluid port and valve core spring, the first hydraulic control hydraulic fluid port is anti-with the load of main control valve 21
Feedback hydraulic fluid port LS1, valve core spring and the first proportion electro-magnet 312 are connected；The other end (being right-hand member in Fig. 2)
Being provided with the second hydraulic control hydraulic fluid port, this second hydraulic control hydraulic fluid port is connected with the oil drain out P0 of variable pump 11.Main control
The pressure of the load feedback hydraulic fluid port LS1 of valve 21 and the valve core spring power of spool control valve 31 one end jointly act on
The pump oil drain out mouth pressure of spool control valve 311 other end balances each other, structure balanced type as shown in formula II:
P0×S1=PLS1×S2+FBulletFormula II
Here, P0 is the pressure at the oil drain out P0 of variable pump 11, PLS1Load for main control valve 21
The pressure of feedback hydraulic fluid port LS1, FBulletFor spring pre-tightening pressure；S1 is in the valve rod two ends of spool control valve 311
With the area that one end that oil phase contacts discharged by pump, S2 is the area of the valve rod other end of spool control valve 311.Its
In,
FBullet=Δ P*S2, considers generally S1=S2, it is assumed hereinafter that S1=S2=S simultaneously, thus obtains
It follows that Δ P and FBulletIt is directly proportional, understands in conjunction with formula I, the output flow of hydraulic system
Q and FBulletAlso it is directly proportional.Those skilled in the art can adjust the output flow Q of hydraulic system accordingly.
The preload pressure F of this valve core springBulletRegulation, be i.e. to hydraulic pump oil oil drain out and load feedback hydraulic fluid port
Between the regulation of pressure differential, this conciliation is realized by the first proportion electro-magnet 312.First ratio electromagnetism
Ferrum 132 is connected with controller 41, is changed into power and displacement for the control signal of telecommunication sent by controller 41,
And then promote valve core spring to move, make the preload pressure F of valve core springBulletThe control signal of telecommunication with controller 41
Association, and this control signal of telecommunication is relevant with the throttle signal that controller 41 receives, thereby through controller
The 41 preload pressure F making valve core springBulletRelevant to throttle signal, i.e. Δ P is relevant to throttle signal.Δ P is again
Determine the output flow Q of hydraulic system.Therefore, this hydraulic system be capable of output flow and throttle
Signal correction.
Additionally, in order to the pressure reduction making main control valve 21 restriction two ends is constant, permissible in this main control valve 21
It is provided with pressure-compensated valve 212, regulates equal to pressure reduction for realizing the pressure differential of main control valve 21 import and export
The pressure differential at valve two ends.Specifically, main control valve 21 may include that main reversing valve 211 and pressure compensation
Valve 212, the oil-in C1 of pressure-compensated valve 212 communicates with the oil-out D1 of main reversing valve 211；Fuel-displaced
Mouth C2 communicates with the load feedback hydraulic fluid port LS1 of main reversing valve 211.
The structure of above-mentioned main reversing valve 211 can be same as the prior art, its oil inlet P 1 and load sensitive variable
The oil drain out P0 of pump 11 communicates, and its actuator port is connected with actuator.In this enforcement, main reversing valve 211
It is three clematis stem solenoid directional control valves.
Controller noted above 41 is used for according to the throttle signal received by adjusting the pre compressed magnitude of valve core spring
Adjust the pressure reduction regulated quantity Δ P of pressure reduction regulation.Referring to Fig. 3, this controller 41 specifically may include that
Receive unit 411, be used for receiving throttle signal；
Converting unit 412, for obtaining engine rotational speed signal according to throttle signal；
Processing unit 413, for the pressure reduction regulated quantity according to engine rotational speed signal regulation pressure-difference valve.
Thus, those skilled in the art can be entered by the pressure differential that main control valve is imported and exported by this controller 41
Row continuously adjusts.When not stepping on the gas, and during idling, pressure differential is less, when engine speed rises,
Its pressure differential also can be gradually increasing accordingly, and when engine speed reaches maximum, pressure differential reaches maximum.
See Fig. 3, the figure shows the principle of the hydraulic system that the embodiment of the present invention two provides, this hydraulic pressure system
System is hydraulic system with constant displacement pump, and the hydraulic pump in this system is dosing pump 12；Pressure-difference valve includes air relief valve
321 and second proportion electro-magnet 322:
Second proportion electro-magnet 322 is connected with the outer end of the valve core spring of air relief valve 321；Air relief valve 321
Oil-in B1 communicates with the oil drain out P2 of dosing pump 12, feedback hydraulic fluid port B2 and the load of main control valve 22
Feedback hydraulic fluid port LS2 communicates；
Second proportion electro-magnet 322 is connected with controller 42.
Hydraulic pump in the hydraulic system that the present embodiment provides is dosing pump 12, and pressure-difference valve is valve core spring
The adjustable air relief valve of preload pressure 321, i.e. the adjustable air relief valve of pressure reduction.Controller 42 is by the oil obtained
Gate signal controls the displacement of the second proportion electro-magnet 322, and then the valve core spring of regulation air relief valve 321
Preload pressure, what the final amount of differential pressure controlling air relief valve 321, i.e. main control valve 22 were imported and exported pressure reduction.
The concrete structure of the controller 42 that the present embodiment provides can be identical with a upper embodiment with the process of control,
I.e. include above-mentioned receiving unit, converting unit and processing unit.Additionally, the of the controller 42 of the present embodiment
Two outfans can be connected with the electromotor 122 of dosing pump 12, and i.e. this controller 42 can also be according to reception
Throttle signal control electromotor 122 rotating speed.Above-mentioned throttle 52 preferably employs E-Gas.
Furthermore, it is necessary to explanation, the hydraulic system that above-described embodiment provides can also include existing hydraulic pressure
Other element in system, such as actuator, this actuator is connected with the actuator port of main control valve.Should
Actuator is specifically as follows oil cylinder or hydraulic motor etc..
The embodiment of the present invention three additionally provides a kind of engineering machinery, such as crane, and this engineering machinery is provided with
State any one hydraulic system, owing to any of the above-described kind of hydraulic system has above-mentioned technique effect, therefore, be provided with
The engineering machinery of this hydraulic system also should possess corresponding technique effect, its specific implementation process and above-mentioned enforcement
Example is similar to, and does not repeats.
The foregoing is only presently preferred embodiments of the present invention, not in order to limit the present invention, all at this
Within bright spirit and principle, any modification, equivalent substitution and improvement etc. made, should be included in this
Within bright protection domain.
Claims (10)
1. a hydraulic system, it is characterised in that include hydraulic pump, main control valve, pressure-difference valve and control
Device processed；Wherein:
Described pressure-difference valve is arranged at the oil drain out of described hydraulic pump and the load feedback oil of described main control valve
Between Kou, for adjusting the pressure reduction of described oil drain out and load feedback hydraulic fluid port；
The input of described controller is connected with throttle, is used for receiving throttle signal；First outfan and pressure reduction
Regulation valve is connected, for controlling the pressure reduction regulated quantity of described pressure-difference valve according to described throttle signal.
Hydraulic system the most according to claim 1, it is characterised in that described hydraulic pump is variable pump
(11)；Described pressure-difference valve includes spool control valve (311) and the first proportion electro-magnet (312)；
The outer end phase of described first proportion electro-magnet (312) and the valve core spring of described spool control valve (311)
Even；First hydraulic control hydraulic fluid port (A1) of described spool control valve (311) and the oil extraction of described variable pump (11)
Mouth (P0) communicates, the second hydraulic control hydraulic fluid port (A2) and the load feedback hydraulic fluid port (LS1) of described main control valve (21)
Communicate；Feedback hydraulic fluid port (A3) is connected with the Variable Control piston (111) of variable pump (11)；
Described first proportion electro-magnet (312) is connected with described controller (41).
Hydraulic system the most according to claim 2, it is characterised in that described main control valve (21) wraps
Include: main reversing valve (211) and pressure-compensated valve (212), the oil-in of described pressure-compensated valve (212)
(C1) communicate with the oil-out (D1) of described main reversing valve (211)；Oil-out (C2) and described master
The load feedback hydraulic fluid port (LS1) of reversal valve (211) communicates.
Hydraulic system the most according to claim 1, it is characterised in that described hydraulic pump is dosing pump
(12), described pressure-difference valve includes uniform-pressure-drop valve (321) and the second proportion electro-magnet (322):
Described second proportion electro-magnet (322) is connected with the outer end of the valve core spring of described air relief valve (321)；
The oil-in (B1) of described air relief valve (321) communicates with the oil drain out (P2) of described dosing pump (12),
Feedback hydraulic fluid port (B2) communicates with the load feedback hydraulic fluid port (LS2) of described main control valve (22)；
Described second proportion electro-magnet (322) is connected with controller (42).
5. according to the hydraulic system described in Claims 1-4 any one, it is characterised in that described throttle
For E-Gas.
Hydraulic system the most according to claim 5, it is characterised in that the second output of described controller
End is connected with the electromotor of described hydraulic pump, for controlling the rotating speed of described electromotor according to described throttle signal.
Hydraulic system the most according to claim 6, it is characterised in that described controller includes:
Receive unit, be used for accepting described throttle signal；
Converting unit, for obtaining engine rotational speed signal according to described throttle signal；
Processing unit, for regulating the pressure reduction regulation of described pressure-difference valve according to described engine rotational speed signal
Amount.
Hydraulic system the most according to claim 5, it is characterised in that also include: with described main control
The actuator that the actuator port of valve is connected.
9. an engineering machinery, it is characterised in that be provided with the liquid described in claim 1 to 8 any one
Pressure system.
Engineering machinery the most according to claim 9, it is characterised in that it is crane.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310738257.2A CN103727082B (en) | 2013-12-27 | 2013-12-27 | Hydraulic system and engineering machinery |
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|---|---|---|---|
| CN201310738257.2A CN103727082B (en) | 2013-12-27 | 2013-12-27 | Hydraulic system and engineering machinery |
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| CN103727082B true CN103727082B (en) | 2016-08-31 |
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Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013206977A1 (en) * | 2013-04-18 | 2014-11-06 | Robert Bosch Gmbh | Flow control valve assembly |
| CN105604996B (en) * | 2016-03-18 | 2017-09-19 | 徐州重型机械有限公司 | Load sensitive control system, control method and hydraulic system |
| CN106168234B (en) * | 2016-07-13 | 2018-06-29 | 柳州柳工挖掘机有限公司 | A kind of constant displacement pump variable delivery hydraulic system |
| CN107725505A (en) * | 2017-09-25 | 2018-02-23 | 柳工常州机械有限公司 | Hydraulic system with different accessory flow regulating functions |
| CN107740747A (en) * | 2017-10-13 | 2018-02-27 | 三汽车起重机械有限公司 | The control method of speed limit hydraulic motor, crane and motor rotary speed |
| CN107630871A (en) * | 2017-11-13 | 2018-01-26 | 柳工常州机械有限公司 | Hydraulic system |
| CN108980130A (en) * | 2018-08-06 | 2018-12-11 | 中联重科股份有限公司 | Differential pressure regulating valve unit, hydraulic control system and engineering machinery |
| CN108916138B (en) * | 2018-09-21 | 2021-05-11 | 徐州重型机械有限公司 | Hydraulic system, control method thereof and engineering machinery |
| CN109595204B (en) * | 2018-12-07 | 2020-09-29 | 中联重科股份有限公司 | Variable pump hydraulic system, control method thereof and crane |
| CN111059091B (en) * | 2019-12-20 | 2021-04-13 | 中联重科股份有限公司 | Load-sensitive oil supply module, load-sensitive system and control method thereof |
| CN114483677B (en) * | 2021-12-27 | 2024-01-23 | 湖南中联重科应急装备有限公司 | Telescopic motor hydraulic system and aerial ladder fire truck |
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| US5245827A (en) * | 1992-08-03 | 1993-09-21 | Deere & Company | Supply valve arrangement for closed center hydraulic system |
| CN202833364U (en) * | 2012-09-20 | 2013-03-27 | 三一重工股份有限公司 | Variable pump hydraulic circuit and engineering machinery |
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| CN103727082A (en) | 2014-04-16 |
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