CN103727082A - Hydraulic system and engineering machine - Google Patents
Hydraulic system and engineering machine Download PDFInfo
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- CN103727082A CN103727082A CN201310738257.2A CN201310738257A CN103727082A CN 103727082 A CN103727082 A CN 103727082A CN 201310738257 A CN201310738257 A CN 201310738257A CN 103727082 A CN103727082 A CN 103727082A
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Abstract
The invention discloses a hydraulic system and an engineering machine. The hydraulic system comprises a hydraulic pump, a main control valve, a pressure-difference adjusting valve and a controller. The pressure-difference adjusting valve is arranged between an oil discharging port of the hydraulic pump and a load feedback oil port of the main control valve and used for adjusting the differential pressure between the oil discharging port and the load feedback oil port; the input end of the controller is connected with an accelerator and used for receiving signals of the accelerator; the first output end is connected with the pressure-difference adjusting valve and used for controlling the pressure-difference adjusting amount of the pressure-difference adjusting valve according to the signals of the accelerator. According to the hydraulic system, the flow of a valve rod of the main control valve can be controlled according to the signals of the accelerator, so that an engine is either at an idle speed or at a high speed, and the adjustment on the flow within the whole stroke of the valve rod of the main control valve can be achieved, namely the flow adjusting gain of the main control valve is small at the idle speed, and the jogging performance is good; the flow adjusting gain of the main control valve is large at the high speed, and the requirements for large flow and high speed are met.
Description
Technical field
The present invention relates to hydraulics field, particularly a kind of hydraulic system and engineering machinery.
Background technique
Hoist is a kind of facility for the conveying material that hoists, and is widely used in hoisting operation and lifting operation under the operating modes such as building site, port and pier, oil field, railway, warehouse, wind-powered electricity generation.In recent years, along with the quickening of engineering construction step, the effect that hoist is brought into play in all conglomeraties is also increasing, and the improvement of hoist fretting performance is also more and more subject to people's attention.
At present, hoist adopts valve control form mostly, by changing the opening area of main valve valve rod, realizes the control of flow, and in limited control stroke, the maximum open design of valve rod need to meet the requirement of actuator's speed.And in order to keep the stable of flow, before the valve of the main valve of being everlasting or after valve, pressure-compensated valve is set, realize main valve front and back pressure reduction constant.This pressure reduction is determined (LUDV system) by the spring at pressure-compensated valve place or the spring at oil pump feedback place conventionally, is a fixed value, and therefore the output flow of main valve is only relevant to the opening area of its valve rod.The technical problem that existing hydraulic system exists is as follows:
The input speed of most hoist pumps can regulate from idling (800r/min left and right) to high speed (2000r/min) continuously by throttle.Under idling operation, at the leading portion of valve core of main valve stroke, now the output flow of main valve is less than the output flow of oil pump, the output flow of main valve can regulate continuously according to the area change of valve port, and at the back segment of valve rod travel, due to the output flow restriction of oil pump, main valve output flow is constant, equals the output flow of oil pump.Therefore, main valve has only utilized a part for its whole strokes to realize Flow-rate adjustment or speed regulates during idling.In addition, due to the rate request of part actuator (as elevator), need main valve when high engine speeds (as 2000r/min), to export large flow, the large opening area gain that therefore needs main valve to realize in limited stroke.This has just reduced vehicle fine motion and handling when idling operation.Be that existing hydraulic system is difficult to take into account that running up of complete machine is difficult to and the requirement of good fretting performance.
Summary of the invention
In view of this, the present invention proposes a kind ofly can take into account running up and hydraulic system and the engineering machinery of the requirement of good fretting performance of complete machine.
For achieving the above object, technological scheme of the present invention is achieved in that
On the one hand, the invention provides a kind of hydraulic system, comprise oil hydraulic pump, main control valve, pressure-difference valve and controller; Wherein: described pressure-difference valve is arranged between the oil drain out of described oil hydraulic pump and the load feedback hydraulic fluid port of described main control valve, for adjusting the pressure reduction of described oil drain out and described load hydraulic fluid port; The input end of described controller is connected with throttle, for receiving throttle signal; The first output terminal is connected with pressure-difference valve, for according to the pressure reduction regulated quantity of pressure-difference valve described in described throttle signal control.
Further, described oil hydraulic pump is variable displacement pump; Described pressure-difference valve comprises controls guiding valve and the first proportion electro-magnet; Described the first proportion electro-magnet is connected with the outer end of the valve core spring of described control guiding valve; The first hydraulic control hydraulic fluid port of described control guiding valve communicates with the oil drain out of described variable displacement pump, and the second hydraulic control hydraulic fluid port communicates with the load feedback hydraulic fluid port of described main control valve; Feedback hydraulic fluid port is connected with the Variable Control piston of variable displacement pump; Described the first proportion electro-magnet is connected with described controller.
Further, described main control valve comprises: main reversing valve and pressure-compensated valve, and the filler opening of described pressure-compensated valve communicates with the oil outlet of described main reversing valve; Oil outlet communicates with the load feedback hydraulic fluid port of described main reversing valve.
Further, described oil hydraulic pump is metering pump, and described pressure-difference valve comprises Fixed differential reducing valve and the second proportion electro-magnet: described the second proportion electro-magnet is connected with the outer end of the valve core spring of described reduction valve; The filler opening of described reduction valve communicates with the oil drain out of described metering pump, and feedback hydraulic fluid port communicates with the load feedback hydraulic fluid port of described main control valve; Described the second proportion electro-magnet is connected with described controller.
Further, described throttle is E-Gas.
Further, the second output terminal of described controller is connected with the motor of described oil hydraulic pump, for according to the rotating speed of motor described in described throttle signal control.
Further, described controller comprises: receiving element, 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 regulated quantity of described pressure-difference valve according to described engine rotational speed signal.
Further, described hydraulic system also comprises: the actuator being connected with the actuator port of described main control valve,
On the other hand, the present invention also provides a kind of engineering machinery, is provided with the hydraulic system described in above-mentioned any one.
Further, described engineering machinery is hoist.
The invention provides a kind of hydraulic system, now for prior art, in this hydraulic system, be provided with the adjustable pressure-difference valve of pressure reduction regulated quantity, for the pressure reduction between regulator solution force feed oil drain out and load feedback hydraulic fluid port, also be provided with controller simultaneously, controller is by the pressure reduction regulated quantity of throttle signal size adjustment pressure-difference valve, and then controlled the pressure reduction of oil hydraulic pump oil drain out and load feedback hydraulic fluid port, and then finally realize whole hydraulic system and can control main control valve valve rod flow according to the size of throttle signal, no matter motor is in idling or in high speed thus, in whole strokes of the valve rod of main valve, can realize the adjusting of flow, the Flow-rate adjustment gain of the main valve while being idling is little, fine motion is good, during high speed, the gain of the Flow-rate adjustment of main valve is large, meet the requirement at a high speed of large flow.
Accompanying drawing explanation
The accompanying drawing that forms a part of the present invention is used to provide a further understanding of the present invention, and schematic description and description of the present invention is used for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
The theory relation curve of output flow and the slight formation of handle in the hydraulic system that Fig. 1 provides for the embodiment of the present invention;
The principle schematic of the hydraulic system that Fig. 2 provides for the embodiment of the present invention one;
The hydraulic system schematic diagram that Fig. 3 provides for the embodiment of the present invention two.
Description of reference numerals:
11 variable displacement pump P0 oil drain outs
111 Variable Control piston 112 motors
21 main control valve LS1 load feedback hydraulic fluid ports
P1 filler opening D1 oil outlet
211 main reversing valves
212 Fixed differential reducing valve C1 filler openings
C2 oil outlet
311 control guiding valve A1 the first hydraulic control hydraulic fluid port
A2 the second hydraulic control hydraulic fluid port A3 feedback hydraulic fluid port
312 first proportion electro-magnets
41 controllers
51 throttles
12 metering pump P2 oil drain outs
122 motors
22 main control valve LS2 load feedback hydraulic fluid ports
321 reduction valve B1 filler openings
B2 second feeds back hydraulic fluid port 322 second proportion electro-magnets
42 controllers
52 throttles
Embodiment
It should be noted that, in the situation that not conflicting, the feature in embodiment and embodiment in the present invention can combine mutually.
The embodiment of the present invention provides a kind of hydraulic system, comprising: oil hydraulic pump, main control valve, pressure-difference valve and controller; Wherein,
Pressure-difference valve is arranged between the oil drain out of oil hydraulic pump and the load feedback hydraulic fluid port of main control valve, for adjusting the pressure reduction of above-mentioned oil drain out and load feedback hydraulic fluid port; The input end of controller is connected with throttle, for receiving throttle signal; The first output terminal is connected with pressure-difference valve, for according to the pressure reduction regulated quantity of throttle signal control pressure-difference valve.
In the hydraulic system that the present embodiment provides, oil hydraulic pump under the effect of its transmitter to whole hydraulic system pumping pressure oil.Main control valve can be existing selector valve, for flow to control the running of hydraulic actuator by controlling hydraulic oil.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 filler opening and the load feedback hydraulic fluid port of main control valve, and the pressure reduction pressure reduction that spool of main control valve is imported and exported, hereinafter to be referred as inlet outlet pressure differential; This pressure-difference valve is arranged between oil hydraulic pump oil drain out and load feedback hydraulic fluid port, unlike the prior art: the pressure reduction regulated quantity of this pressure-difference valve is adjustable, and the adjusting of pressure reduction regulated quantity is realized by controller.The input termination of controller receives throttle signal, and controller is controlled the pressure reduction regulated quantity of pressure-difference valve according to this throttle signal.The pressure reduction of realizing thus oil hydraulic pump oil drain out and load feedback hydraulic fluid port can be according to corresponding adjusting of throttle size.
Above-mentioned pressure-difference valve can be the adjustable hydrovalve of pre compressed magnitude of valve core spring, and valve core spring preload pressure is adjustable.Concrete Principles of Regulation are as follows: pressure-difference valve can be accepted 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 the adjusting of the pressure reduction regulated quantity of pressure-difference valve.
Under the certain prerequisite of main control valve opening area, the pressure reduction regulated quantity of pressure-difference valve is directly proportional to the output flow of hydraulic system, and the relationship of the two is suc as formula shown in (I):
Q=C
d× S × (Δ P)
nformula (I)
In above formula: the output flow that Q is hydraulic system, C
dfor flow coefficient; S is the opening area of main control valve; Δ P is the pressure difference between hydraulic oil oil drain out and load feedback hydraulic fluid port, i.e. the import and export of main control valve pressure reduction, be also the pressure reduction regulated quantity of above-mentioned pressure-difference valve, lower with; N is the coefficient relevant to the structure at main control valve restriction place, gets between 0～1.
Above-mentioned pressure reduction regulated quantity Δ P can be directly proportional to throttle signal; Take hoist as example, refer to Fig. 1, under idling operation, the output of throttle no signal, the throttle signal that controller receives is minimum value, correspondingly, the valve core spring pre compressed magnitude of now controlling pressure-difference valve is less, be that pressure reduction regulated quantity is also less, now the increment of main control valve flow reduces, and is conducive to improve the fretting performance of complete machine; Under high-speed working condition, the throttle signal that controller receives is larger, and correspondingly, the valve core spring pre compressed magnitude of now controlling pressure-difference valve is larger, and pressure reduction regulated quantity is also larger, is conducive to thus meet 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 by controller the associated adjusting of throttle signal size and the amount of differential pressure of pressure-difference valve, and then adjust main control valve import and export pressure reduction, finally realize whole hydraulic system and can control according to the size of throttle signal the changes in flow rate of main control valve, no matter motor is in idling or in high speed thus, in whole strokes of the valve rod of main valve, can realize the adjusting of flow, the Flow-rate adjustment gain of the main valve while being idling is little, fine motion is good, during high speed, the gain of the Flow-rate adjustment of main valve is large, meet the requirement at a high speed of large flow.
The specific constructive form of pressure-difference valve and with the annexation of other hydraulic element, can select according to the type of oil hydraulic pump.Below in conjunction with accompanying drawing, as an example of variable displacement pump hydraulic system and hydraulic system with constant displacement pump example, further each preferred embodiment of the present invention is explained respectively:
Refer to Fig. 2, the figure shows the principle of the hydraulic system that the embodiment of the present invention one provides, this hydraulic system is load-sensitive pump hydraulic system, and the oil hydraulic pump in this system is variable displacement pump 11; Pressure-difference valve comprises controls guiding valve 311 and the first proportion electro-magnet 312;
The first proportion electro-magnet 312 is arranged at the outer end of the valve core spring of controlling guiding valve 311;
The the first hydraulic control hydraulic fluid port A1 that controls guiding valve 311 communicates with the oil drain out P0 of variable displacement pump 11, and the second hydraulic control hydraulic fluid port A2 communicates with the load feedback hydraulic fluid port LS1 of main control valve 21; Feedback hydraulic fluid port A3 is connected with the Variable Control piston 111 of variable displacement pump 11;
Above-mentioned the first proportion electro-magnet 312 is connected with controller 41.
In the hydraulic system of the present embodiment, one end (being left end in Fig. 2) of control guiding valve 311 in pressure-difference valve is provided with the first hydraulic control hydraulic fluid port and valve core spring, the load feedback hydraulic fluid port LS1 of the first hydraulic control hydraulic fluid port and main control valve 21, valve core spring is connected with the first proportion electro-magnet 312; The other end (being right-hand member in Fig. 2) is provided with the second hydraulic control hydraulic fluid port, and this second hydraulic control hydraulic fluid port is connected with the oil drain out P0 of variable displacement pump 11.The pressure of the load feedback hydraulic fluid port LS1 of main control valve 21 and the valve core spring power acting in conjunction of controlling guiding valve 31 one end balance each other with the pump oil drain out mouth pressure of controlling guiding valve 311 the other ends, and structure is suc as formula the balanced type shown in (II):
P0 × S1=P
lS1× S2+F
bulletformula (II)
Here, P0 is the pressure at the oil drain out P0 place of variable displacement pump 11, P
lS1for the pressure of the load feedback hydraulic fluid port LS1 of main control valve 21, F
bulletfor spring pre-tightening pressure; S1 is the area of controlling the one end contacting with pump discharge oil phase in the valve rod two ends of guiding valve 311, and S2 is the area of controlling the valve rod the other end of guiding valve 311.Wherein,
F
bullet=Δ P*S2 considers generally S1=S2 simultaneously, below supposes to obtain S1=S2=S thus
Hence one can see that, Δ P and F
bulletbe directly proportional, then convolution (I) is known, output flow Q and the F of hydraulic system
bulletalso be 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 spring
bulletadjusting, be the adjusting to the pressure difference between oil hydraulic pump oil oil drain out and load feedback hydraulic fluid port, this conciliation is realized by the first proportion electro-magnet 312.The first proportion electro-magnet 132 is connected with controller 41, for the control electrical signal that controller 41 is sent, changes power and displacement into, so promote valve core spring move, make the preload pressure F of valve core spring
bulletassociated with the control electrical signal of controller 41, and this control electrical signal is relevant with the throttle signal that controller 41 receives, thereby by controller 41, make the preload pressure F of valve core spring
bulletrelevant to throttle signal, Δ P is relevant to throttle signal.Δ P has determined again the output flow Q of hydraulic system.Therefore, this hydraulic system can to realize output flow relevant to throttle signal.
In addition,, in order to make the pressure reduction at main control valve 21 restriction two ends constant, this main control valve 21 is interior can be provided with pressure-compensated valve 212, equals the pressure difference at pressure-difference valve two ends for realizing the pressure difference of main control valve 21 import and exports.Particularly, main control valve 21 can comprise: main reversing valve 211 and pressure-compensated valve 212, and the filler opening C1 of pressure-compensated valve 212 communicates with the oil outlet D1 of main reversing valve 211; Oil outlet 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, and its oil inlet P 1 communicates with the oil drain out P0 that carries responsive variable displacement pump 11, and its actuator port is connected with actuator.In this enforcement, main reversing valve 211 is three six electric change valves.
Above-mentioned controller 41 is for adjusting by adjusting the pre compressed magnitude of valve core spring the pressure reduction regulated quantity Δ P that pressure reduction regulates according to the throttle signal receiving.Refer to Fig. 3, this controller 41 specifically can comprise:
Receiving element 411, for receiving throttle signal;
Converting unit 412, for obtaining engine rotational speed signal according to throttle signal;
Processing unit 413, for regulating the pressure reduction regulated quantity of pressure-difference valve according to engine rotational speed signal.
Thus, the pressure difference that those skilled in the art can import and export main control valve by this controller 41 regulates continuously.When not stepping on the gas, and during idling, pressure difference is less, and when engine speed rises, its pressure difference also can rise accordingly gradually, and when engine speed reaches maximum, pressure difference reaches maximum value.
Referring to Fig. 3, the figure shows the principle of the hydraulic system that the embodiment of the present invention two provides, this hydraulic system is hydraulic system with constant displacement pump, the oil hydraulic pump in this system is metering pump 12; Pressure-difference valve comprises reduction valve 321 and the second proportion electro-magnet 322:
The second proportion electro-magnet 322 is connected with the outer end of the valve core spring of reduction valve 321; The filler opening B1 of reduction valve 321 communicates with the oil drain out P2 of metering pump 12, and feedback hydraulic fluid port B2 communicates with the load feedback hydraulic fluid port LS2 of main control valve 22;
The second proportion electro-magnet 322 is connected with controller 42.
Oil hydraulic pump in the hydraulic system that the present embodiment provides is metering pump 12, the adjustable reduction valve 321 of preload pressure that pressure-difference valve is valve core spring, the i.e. adjustable reduction valve of pressure reduction.Controller 42 is controlled the displacement amount of the second proportion electro-magnet 322 by the throttle signal obtaining, and then regulates the preload pressure of the valve core spring of reduction valve 321, finally controls the amount of differential pressure of reduction valve 321, main control valve 22 import and export pressure reduction.
The concrete structure of the controller 42 that the present embodiment provides can be identical with a upper embodiment with control procedure, comprises above-mentioned receiving unit, converting unit and processing unit.In addition, the second output terminal of the controller 42 of the present embodiment can be connected with the motor of metering pump 12 122, and this controller 42 can also be according to the rotating speed of the throttle signal control engine 122 receiving.Above-mentioned throttle 52 preferably adopts E-Gas.
In addition, it should be noted that, the hydraulic system that above-described embodiment provides can also comprise other element in existing hydraulic system, and as actuator, this actuator is connected with the actuator port of main control valve.This actuator is specifically as follows oil cylinder or oil hydraulic motor etc.
The embodiment of the present invention three also provides a kind of engineering machinery, for example hoist, this project machinery is provided with above-mentioned any hydraulic system, because above-mentioned any hydraulic system has above-mentioned technique effect, therefore, the engineering machinery that is provided with this hydraulic system also should possess corresponding technique effect, and its specific implementation process is similar to the above embodiments, does not hereby repeat.
The foregoing is only preferred embodiment of the present invention, in order to limit the present invention, within the spirit and principles in the present invention not all, any modification of doing, be equal to replacement, improvement etc., within all should being included in protection scope of the present invention.
Claims (10)
1. a hydraulic system, is characterized in that, comprises oil hydraulic pump, main control valve, pressure-difference valve and controller; Wherein:
Described pressure-difference valve is arranged between the oil drain out of described oil hydraulic pump and the load feedback hydraulic fluid port of described main control valve, for adjusting the pressure reduction of described oil drain out and described load hydraulic fluid port;
The input end of described controller is connected with throttle, for receiving throttle signal; The first output terminal is connected with pressure-difference valve, for according to the pressure reduction regulated quantity of pressure-difference valve described in described throttle signal control.
2. hydraulic system according to claim 1, is characterized in that, described oil hydraulic pump is variable displacement pump (11); Described pressure-difference valve comprises controls guiding valve (311) and the first proportion electro-magnet (312);
Described the first proportion electro-magnet (312) is connected with the outer end of the valve core spring of described control guiding valve (311); The first hydraulic control hydraulic fluid port (A1) of described control guiding valve (311) communicates with the oil drain out (P0) of described variable displacement pump (11), and the second hydraulic control hydraulic fluid port (A2) communicates with the load feedback hydraulic fluid port (LS1) of described main control valve (21); Feedback hydraulic fluid port (A3) is connected with the Variable Control piston (111) of variable displacement pump (11);
Described the first proportion electro-magnet (312) is connected with described controller (41).
3. hydraulic system according to claim 2, it is characterized in that, described main control valve (21) comprising: main reversing valve (211) and pressure-compensated valve (212), and the filler opening (C1) of described pressure-compensated valve (212) communicates with the oil outlet (D1) of described main reversing valve (211); Oil outlet (C2) communicates with the load feedback hydraulic fluid port (LS1) of described main reversing valve (211).
4. hydraulic system according to claim 1, is characterized in that, described oil hydraulic pump is metering pump (12), and described pressure-difference valve comprises Fixed differential reducing valve (321) and the second proportion electro-magnet (322):
Described the second proportion electro-magnet (322) is connected with the outer end of the valve core spring of described reduction valve (321); The filler opening (B1) of described reduction valve (321) communicates with the oil drain out (P2) of described metering pump (12), and feedback hydraulic fluid port (B2) communicates with the load feedback hydraulic fluid port (LS2) of described main control valve (22);
Described the second proportion electro-magnet (322) is connected with described controller (42).
5. according to the hydraulic system described in claim 1 to 4 any one, it is characterized in that, described throttle is E-Gas.
6. hydraulic system according to claim 5, is characterized in that, the second output terminal of described controller is connected with the motor of described oil hydraulic pump, for according to the rotating speed of motor described in described throttle signal control.
7. hydraulic system according to claim 6, is characterized in that, described controller comprises:
Receiving element, 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 regulated quantity of described pressure-difference valve according to described engine rotational speed signal.
8. hydraulic system according to claim 5, is characterized in that, also comprises: the actuator being connected with the actuator port of described main control valve.
9. an engineering machinery, is characterized in that, is provided with the hydraulic system described in claim 1 to 8 any one.
10. engineering machinery according to claim 9, is characterized in that, it is hoist.
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| CN201310738257.2A CN103727082B (en) | 2013-12-27 | 2013-12-27 | Hydraulic system and engineering machinery |
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Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104006019A (en) * | 2014-05-15 | 2014-08-27 | 安徽博一流体传动股份有限公司 | Load-sensitive control valve capable of remotely adjusting pressure difference |
| CN104110412A (en) * | 2013-04-18 | 2014-10-22 | 罗伯特·博世有限公司 | Flow Regulating Valve Assembly |
| CN105604996A (en) * | 2016-03-18 | 2016-05-25 | 徐州重型机械有限公司 | Load-sensitive control system, control method and hydraulic system |
| CN106168234A (en) * | 2016-07-13 | 2016-11-30 | 柳州柳工挖掘机有限公司 | A kind of dosing pump variable delivery hydraulic system |
| CN107630871A (en) * | 2017-11-13 | 2018-01-26 | 柳工常州机械有限公司 | 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 |
| CN108916138A (en) * | 2018-09-21 | 2018-11-30 | 徐州重型机械有限公司 | Hydraulic system and its control method, engineering machinery |
| CN108980130A (en) * | 2018-08-06 | 2018-12-11 | 中联重科股份有限公司 | Differential regulating valuve unit, hydraulic control system and engineering machinery |
| CN109595204A (en) * | 2018-12-07 | 2019-04-09 | 中联重科股份有限公司 | Variable pump hydraulic system and its control method and crane |
| CN111059091A (en) * | 2019-12-20 | 2020-04-24 | 中联重科股份有限公司 | Load-sensitive oil supply module, load-sensitive system and control method thereof |
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| CN104110412A (en) * | 2013-04-18 | 2014-10-22 | 罗伯特·博世有限公司 | Flow Regulating Valve Assembly |
| CN104006019A (en) * | 2014-05-15 | 2014-08-27 | 安徽博一流体传动股份有限公司 | Load-sensitive control valve capable of remotely adjusting pressure difference |
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| 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 regulating valuve unit, hydraulic control system and engineering machinery |
| CN108916138A (en) * | 2018-09-21 | 2018-11-30 | 徐州重型机械有限公司 | Hydraulic system and its control method, 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 |
| CN109595204A (en) * | 2018-12-07 | 2019-04-09 | 中联重科股份有限公司 | Variable pump hydraulic system and its control method and crane |
| 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 |
| CN111059091A (en) * | 2019-12-20 | 2020-04-24 | 中联重科股份有限公司 | Load-sensitive oil supply module, load-sensitive system and control method thereof |
| CN114483677A (en) * | 2021-12-27 | 2022-05-13 | 湖南中联重科应急装备有限公司 | Telescopic motor hydraulic system and aerial ladder fire truck |
| 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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