CN103307060B - The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method - Google Patents

The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method Download PDF

Info

Publication number
CN103307060B
CN103307060B CN201310241735.9A CN201310241735A CN103307060B CN 103307060 B CN103307060 B CN 103307060B CN 201310241735 A CN201310241735 A CN 201310241735A CN 103307060 B CN103307060 B CN 103307060B
Authority
CN
China
Prior art keywords
oil
hydraulic cylinder
way
control
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201310241735.9A
Other languages
Chinese (zh)
Other versions
CN103307060A (en
Inventor
张党龙
余继军
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nanjing Estun Automation Co Ltd
Original Assignee
Nanjing Estun Automation Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nanjing Estun Automation Co Ltd filed Critical Nanjing Estun Automation Co Ltd
Priority to CN201310241735.9A priority Critical patent/CN103307060B/en
Publication of CN103307060A publication Critical patent/CN103307060A/en
Application granted granted Critical
Publication of CN103307060B publication Critical patent/CN103307060B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method, control system comprises driven by servomotor module, pump control cylinder module and auxiliary oil way module, control driven by servomotor two-way pump by servo driver and produce hydraulic energy, the rod chamber of the two-way oil circuit difference connecting fluid cylinder pressure of two-way pump and rodless cavity, fuel tank be used for rod chamber and rodless cavity flow uneven time repairing and draining, by the piston rod movement direction of the positive and reverse steering hydraulic control cylinder of actuating motor.The present invention effectively can solve the flow nonsymmetry problem in pump control hydraulic control system, the pressure loss that the circulation of minimizing system produces with fluid amount and fluid flowing, whole system is compact, easy realization integration, and the pressure loss and heating that considerably reduce that electrohydraulic servo system in the past brings because of the differential pressure flow characteristic of Proportional valve or servovalve.

Description

The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method
Technical field
The invention belongs to technical field of motors, relate to electrohydraulic servo system, is oil hydraulic cylinder control system and the controlling method of the combination drive of a kind of directly driving type servo-pump control electricity liquid.
Background technique
When current electrohydraulic servo system works, by the valve of a series of various function, must particularly need Proportional valve, servovalve etc. to control pressure, flow velocity, the flow direction of working liquid body, thus make each oil hydraulic cylinder complete due action according to technological requirement.Meanwhile, defects such as unavoidably there is complex structure, energy consumption is large, heating value is serious, noise is high, vibration is large, oil filtrating required precision is high, restriction loss is large.
Pump control hydraulic control system, be pump control by original control mode by the revolutionary change of valve control, by original throttle grverning principle, energy loss is large, the shortcomings such as system is easily generated heat, and efficiency is low are abandoned, and make full use of volumetric speed control, energy-conserving and environment-protective, synchronization accuracy is high, and response is fast.Due to double-acting hydraulic cylinder Area comparison large (can 12:1 be reached), upper and lower cavity oil extraction and oil-feed flow differ greatly, therefore and the flow nonsymmetry produced becomes pump control system control problem urgently to be resolved hurrily and pump is because its volumetric void fraction, thus oil absorption is determined and oil drain quantity is equal.
Current domestic each colleges and universities carry out the fundamental research of pump control system respectively in the application such as boats and ships and energy-conserving elevator.Current pump prosecutor case adopts single or two Pilot operated check valves or employing double pump control solution pump control asymmetrical cylinder flow imbalance problem.Wherein Pilot operated check valve control realization mode is directly connected with fuel tank in unbalanced for an oil hydraulic cylinder flow chamber, automatically controls it from fuel tank repairing or to fuel tank oil extraction by system pressure.For to fuel tank oil extraction side, on the one hand, the quick non-loaded flowing of fluid creates the extra pressure loss and heating; On the other hand, fuel tank is because will be large enough to hold fluid amount required when oil cylinder runs fast, and thus fuel tank volume is difficult to reduce, and namely the power savings advantages that cannot embody pump control reduces consumption and the consumption of fluid medium.In addition, hydraulic control mode adds the complexity of Systematical control.
And double pump control program, address only repairing problem and fluid control pressure provides, the problem brought is that system bulk is larger, more powerful, and energy efficiency reduces, and cost performance is not high.
Summary of the invention
The problem to be solved in the present invention is: pump control hydraulic control system has energy-conserving and environment-protective in theory, synchronization accuracy is high, respond fast advantage, but prior art does not have suitable solution for the flow nonsymmetry problem of pump control hydraulic control system in actual applications, Systematical control is complicated, energy efficiency is low, cost performance is not high.
Technological scheme of the present invention is: the oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive, comprise actuating motor, two-way pump, differential unloading valve, first one-way valve, second one-way valve, fuel tank, oil hydraulic cylinder and servo driver, the ratio that the rod end chamber circular crosssection sum piston cross-section of oil hydraulic cylinder is long-pending is not 1, servo driver connects actuating motor, the output of actuating motor connects two-way pump, two-way pump divides two-way oil circuit, first oil circuit is connected to the rodless cavity of oil hydraulic cylinder, second oil circuit is connected to the rod chamber of oil hydraulic cylinder, described two-way oil circuit separates a branch road respectively and is connected to fuel tank through safety valve, second oil circuit is through the first one-way valve, differential unloading valve is unidirectional is connected to the first oil circuit, fuel tank connects the hydraulic fluid port B of differential unloading valve, fuel tank is also connected to the second oil circuit by the second one-way valve is unidirectional.
Further, described two-way oil circuit is respectively equipped with pressure transducer.
Further, the piston rod correspondence of oil hydraulic cylinder is provided with displacement transducer.
The controlling method of the oil hydraulic cylinder control system of above-mentioned directly driving type servo-pump control electricity liquid combination drive, control actuating motor Direct driver two-way pump by servo driver and produce hydraulic energy, realize the complex controll in the pressure to oil hydraulic cylinder, flow, direction, the rod chamber of the two-way oil circuit difference connecting fluid cylinder pressure of two-way pump and rodless cavity, fuel tank be used for rod chamber and rodless cavity flow uneven time repairing and draining, the piston rod movement direction by the positive and reverse steering hydraulic control cylinder of actuating motor:
When actuating motor rotates forward, drive two-way pump by the fluid sucking-off of the oil of oil hydraulic cylinder rod chamber and fuel tank, flow to the first oil circuit by the second oil circuit, finally flow into rodless cavity, piston rod is stretched out;
During actuating motor reversion, drive two-way pump by the sucking-off of the oil of oil hydraulic cylinder rodless cavity, fluid flows to the second oil circuit by the first oil circuit, and final inflow rod chamber and fuel tank, make piston rod return.
Differential unloading valve and the first one-way valve realize the quick Differential Control to oil hydraulic cylinder jointly, and realize repairing and the draining of uneven flow when hydraulic cylinder piston rod stretches out and retracts, and are specially the control of oil hydraulic cylinder:
Piston rod stretches out fast: actuating motor drives two-way pump to rotate forward, the fluid of fuel tank flows through the second one-way valve, the oil sucting cavity of two-way pump is entered by the second oil circuit, the rodless cavity of oil hydraulic cylinder is entered again by the first oil circuit, now differential unloading valve side obtains electric, and hydraulic fluid port P to hydraulic fluid port A connects, and the oil that rod chamber is discharged supplements oil mass through the first one-way valve and differential unloading valve directly to oil hydraulic cylinder rodless cavity, form differential circuit, realize stretching out fast of piston rod by the oil-feed of described two road direction rodless cavities;
Piston rod stretches out at a slow speed: actuating motor drives two-way pump to rotate forward, differential unloading valve must not be electric, keep Median Function locking, hydraulic fluid port Close All, under the hydraulic energy of two-way pump, flowed into the oil sucting cavity of two-way pump together with the fluid that fluid in fuel tank is discharged through the second one-way valve and oil hydraulic cylinder rod chamber by the second oil circuit, the oil-discharging cavity of two-way pump exports fluid to oil hydraulic cylinder rodless cavity, and piston rod stretches out;
Piston rod is return: actuating motor drives two-way pump reversion, under the hydraulic energy of two-way pump, the fluid of oil hydraulic cylinder rodless cavity flows to the oil sucting cavity of two-way pump through the first oil circuit, oil hydraulic cylinder rod chamber is flowed into again by the second oil circuit, now differential unloading valve side obtains electric, hydraulic fluid port P to hydraulic fluid port B connects, a part of fluid of rodless cavity simultaneously by differential unloading valve earial drainage to fuel tank.
Further, when piston rod is return, by controlling the rotating speed of actuating motor, controlling the fluid changes in flow rate that two-way pump is discharged, realizing the control of hydraulic cylinder piston rod being return to speed.
Further, two-way oil circuit is respectively equipped with pressure transducer, pressure transducer feeds back signal to servo driver and is formed and control the pressure closed loop of two-way oil circuit, the piston rod correspondence of oil hydraulic cylinder arranges displacement transducer, feeds back signal to servo driver form position-force control to piston rod by displacement transducer.
The present invention utilizes actuating motor Direct driver two-way pump, by controlling the moment of torsion of actuating motor, rotating speed control and direction controlling pattern, realize the control of the pressure to working liquid body, flow velocity, the flow direction, thus reach the object in regulator solution cylinder pressure movement velocity and direction.The present invention effectively can reduce the circulation fluid amount of system, and structure simple Devices is few, can shorten the route of fluid circulation, thus reduces the pressure loss that fluid flowing produces, such that whole system is compacter and easy realization integrated and effectively reduce heating; When oil hydraulic cylinder is stretched out fast, repairing is more timely, and response is faster, effectively avoids the suction sky of pump and the cavitation erosion problem of oil hydraulic cylinder, in the extension element life-span, improves the speed of response of pump.In addition, adopt the throttling considerably reduced because of Proportional valve or servovalve of the volumetric void fraction of two-way pump the to control pressure loss that differential pressure flow characteristic brings and heating.
The present invention, by differential unloading valve, on the one hand when hydraulic cylinder piston rod stretches out, can form differential circuit, improves hydraulic cylinder speed and response; On the other hand, when hydraulic cylinder piston rod is retracted, the flow that the difference of oil hydraulic cylinder two chamber oil-feed and oil drain quantity causes is uneven, and unnecessary fluid will by differential unloading valve off-load to fuel tank.
Accompanying drawing explanation
Fig. 1 is the structural representation of the oil hydraulic cylinder control system of directly driving type servo-pump control of the present invention electricity liquid combination drive.
Embodiment
Below by a specific embodiment, enforcement of the present invention is described.
As Fig. 1, oil hydraulic cylinder control system of the present invention comprises actuating motor 1, two-way pump 2, differential unloading valve 3, first one-way valve 4, second one-way valve 6, fuel tank 9, oil hydraulic cylinder 10 and servo driver 13, the ratio that wherein the rod end chamber circular crosssection sum piston cross-section of oil hydraulic cylinder 10 is long-pending is not 1, the structure of control system is: servo driver 13 connects actuating motor 1, the output of actuating motor 1 connects two-way pump 2, two-way pump 2 points of two-way oil circuits, first oil circuit is connected to the rodless cavity of oil hydraulic cylinder 10, second oil circuit is connected to the rod chamber of oil hydraulic cylinder 10, described two-way oil circuit separates a branch road respectively through safety valve 7, 8 are connected to fuel tank 9, safety valve is normal for ensureing the oil pressure of two-way oil circuit, second oil circuit is through the first one-way valve 4, differential unloading valve 3 is unidirectional is connected to the first oil circuit, fuel tank 9 connects the hydraulic fluid port B of differential unloading valve 3, fuel tank 9 is also connected to the second oil circuit by the second one-way valve 6 is unidirectional.
Wherein, two-way oil circuit is respectively equipped with pressure transducer, control the pressure closed loop of oil hydraulic cylinder for oil hydraulic cylinder control system, the piston rod correspondence of oil hydraulic cylinder 10 is provided with displacement transducer 11, for the position-force control of oil hydraulic cylinder control system to hydraulic cylinder piston rod.
Control system of the present invention comprises driven by servomotor module, pump control cylinder module and auxiliary oil way module, and wherein motor drive module comprises actuating motor 1 and servo driver 13, the control that servo driver 13 completes actuating motor rotating speed and turns to; Pump control cylinder module is made up of two-way pump 2 and oil hydraulic cylinder 10, by controlling the flow of two-way pump 2, pressure, the speed turning to hydraulic control cylinder 10, displacement and direction; Auxiliary oil way module plays overload protection and limitation function; comprise differential unloading valve 3, first one-way valve 4, second one-way valve 6 and fuel tank 9, two one-way valves and mainly solve the repairing of the asymmetric piston of oil hydraulic cylinder 10 when cylinder volumetric void fraction flow is uneven and draining problem.Such as, for vertically arranged oil hydraulic cylinder, when the piston is moving down, namely, when piston rod stretches out, the discharge capacity of low pressure oil is less than person who lives in exile's amount of high pressure oil, and namely the oil drain quantity of oil hydraulic cylinder 10 rod chamber is less than the oil inlet quantity of rodless cavity, occur that low pressure oil is for shortage of oil, loop oil pressure reduces, and the second one-way valve 6 is opened automatically, by the mode by fuel tank 9 oil suction to low tension loop repairing; Otherwise when the piston is moving up, when namely piston rod is return, the hydraulic oil discharge of rodless cavity is greater than person who lives in exile's amount of rod chamber, and now differential unloading valve 3 is opened, and carries out emptying, makes the inflow and outflow hydraulic pressure oil mass of two-way pump 2 keep balance.Displacement signal from displacement transducer 11 sends into servo driver after treatment, according to the state-driven actuating motor of piston rod, reaches the object of pressure and flow compound control.
The present invention realizes by actuating motor positive and reverse steering and its closed loop control mode the control in the direction of hydraulic pressure, flow and oil hydraulic cylinder.Wherein, the first one-way valve 4 is guaranteed only when oil hydraulic cylinder 10 piston rod stretches out, and the fluid of rod chamber discharge is unidirectional enters oil hydraulic cylinder 10 rodless cavity, and rodless cavity fluid can not flow into rod chamber.
Below by working principle, the concrete controlling method of the present invention to oil hydraulic cylinder 10 is described:
First the stretching out of piston rod is described, due to piston rod stretch out time, the oil mass that oil hydraulic cylinder 10 rod chamber (loculus) is discharged is less than the oil mass needed for rodless cavity (large chamber), therefore must repairing.Piston rod stretches out and comprises following two kinds of patterns:
Piston rod stretches out fast: actuating motor 1 drives two-way pump 2 to rotate forward, the fluid of fuel tank 9 flows through the second one-way valve 6, the oil sucting cavity of two-way pump 2 is entered by the second oil circuit, the rodless cavity of oil hydraulic cylinder 10 is entered again by the first oil circuit, now differential unloading valve 3 side obtains electric, hydraulic fluid port P to hydraulic fluid port A connects, the oil that rod chamber is discharged supplements oil mass through the first one-way valve 4 and differential unloading valve 3 directly to oil hydraulic cylinder 10 rodless cavity, form differential circuit, realize stretching out fast of piston rod by the oil-feed of described two road direction rodless cavities; Wherein, rod chamber and two-way pump have the second oil circuit to be communicated with in theory, when stretching out fast, the fluid that rodless cavity needs is greater than rod chamber, so also need repairing from fuel tank, because differential unloading valve is opened, here regarding rod chamber fluid as taps into into rodless cavity through the first one-way valve 4, differential unloading valve 3 fast direct, form differential circuit, two-way pump 2 sucks another part fluid from fuel tank 9 and supplies rodless cavity as repairing simultaneously, two paths realize the quick oil feeding of rodless cavity, make rodless cavity fluid promote piston rod fast and stretch out.
Piston rod stretches out at a slow speed: actuating motor 1 drives two-way pump 2 to rotate forward, differential unloading valve 3 must not be electric, keep Median Function locking, hydraulic fluid port Close All, second one-way valve 6 is opened, fluid in fuel tank 9 fluid of discharging through the second one-way valve 6 and oil hydraulic cylinder 10 rod chamber is by the oil sucting cavity flowing into two-way pump 2 together with the second oil circuit, and the oil-discharging cavity of two-way pump 2 exports fluid to oil hydraulic cylinder 10 rodless cavity, and piston rod stretches out.Compared with the pattern of stretching out fast, fluid only has a path, road, and all flow into rodless cavity again through two-way pump 2 and the first oil circuit, speed is slower than quick mode.
Due to piston rod stretch out time, what enter rodless cavity comprises the oil of rod chamber discharge and repairing two-part of fuel tank 9, therefore, when piston rod is return, the oil mass that rodless cavity (large chamber) is discharged is greater than the oil mass needed for rod chamber (loculus), therefore needs draining:
Piston rod is return: actuating motor 1 drives two-way pump 2 to reverse, the fluid of oil hydraulic cylinder 10 rodless cavity flows to the oil sucting cavity of two-way pump 2 through the first oil circuit, oil hydraulic cylinder 10 rod chamber is flowed into again by the second oil circuit, drive piston rod is return, now differential unloading valve 3 side obtains electric, hydraulic fluid port P to hydraulic fluid port B connects, a part of fluid of rodless cavity simultaneously by the hydraulic fluid port B earial drainage of differential unloading valve 3 to fuel tank 9.
When wherein piston rod is return, by controlling the rotating speed of actuating motor 1, controlling the fluid changes in flow rate that two-way pump 2 is discharged, realizing the control of oil hydraulic cylinder 10 piston rod being return to speed.
The present invention effectively can solve the flow nonsymmetry problem in pump control hydraulic control system, is applicable to oil hydraulic cylinder that is vertical or other non-horizontal mounting structural types.

Claims (3)

1. the controlling method of the oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive, it is characterized in that described oil hydraulic cylinder control system comprises actuating motor (1), two-way pump (2), differential unloading valve (3), first one-way valve (4), second one-way valve (6), fuel tank (9), oil hydraulic cylinder (10) and servo driver (13), the ratio that the rod end chamber circular crosssection sum piston cross-section of oil hydraulic cylinder (10) is long-pending is not 1, servo driver (13) connects actuating motor (1), the output of actuating motor (1) connects two-way pump (2), two-way pump (2) point two-way oil circuit, first oil circuit is connected to the rodless cavity of oil hydraulic cylinder (10), second oil circuit is connected to the rod chamber of oil hydraulic cylinder (10), described two-way oil circuit separates a branch road respectively and is connected to fuel tank (9) through safety valve, second oil circuit is through the first one-way valve (4), differential unloading valve (3) is unidirectional is connected to the first oil circuit, fuel tank (9) connects the hydraulic fluid port B of differential unloading valve (3), fuel tank (9) is also connected to the second oil circuit by the second one-way valve (6) is unidirectional,
Control actuating motor (1) Direct driver two-way pump (2) by servo driver (13) and produce hydraulic energy, realize the complex controll in the pressure to oil hydraulic cylinder (10), flow, direction, the rod chamber of two-way oil circuit difference connecting fluid cylinder pressure (10) of two-way pump (2) and rodless cavity, repairing when fuel tank (9) is uneven for rod chamber and rodless cavity flow and draining, the piston rod movement direction by the positive and reverse steering hydraulic control cylinder (10) of actuating motor (1):
When actuating motor (1) rotates forward, drive two-way pump (2) by the fluid sucking-off of the oil of oil hydraulic cylinder (10) rod chamber and fuel tank (9), flow to the first oil circuit by the second oil circuit, finally flow into rodless cavity, piston rod is stretched out;
During actuating motor (1) reversion, drive two-way pump (2) by the oily sucking-off of oil hydraulic cylinder (10) rodless cavity, fluid flows to the second oil circuit by the first oil circuit, and final inflow rod chamber and fuel tank (9), make piston rod return;
Wherein, differential unloading valve (3) and the first one-way valve (4) realize the quick Differential Control to oil hydraulic cylinder (10) jointly, and realize repairing and the draining of uneven flow when hydraulic cylinder piston rod stretches out and retracts, the control of oil hydraulic cylinder (10) is specially:
Piston rod stretches out fast: actuating motor (1) drives two-way pump (2) to rotate forward, the fluid of fuel tank (9) flows through the second one-way valve (6), the oil sucting cavity of two-way pump (2) is entered by the second oil circuit, the rodless cavity of oil hydraulic cylinder (10) is entered again by the first oil circuit, now differential unloading valve (3) side obtains electric, hydraulic fluid port P to hydraulic fluid port A connects, the oil that rod chamber is discharged supplements oil mass through the first one-way valve (4) and differential unloading valve (3) directly to oil hydraulic cylinder (10) rodless cavity, form differential circuit, stretching out fast of piston rod is realized to the oil-feed of rodless cavity by described two-way oil circuit,
Piston rod stretches out at a slow speed: actuating motor (1) drives two-way pump (2) to rotate forward, differential unloading valve (3) must not be electric, keep Median Function locking, hydraulic fluid port Close All, under the hydraulic energy of two-way pump (2), flowed into the oil sucting cavity of two-way pump (2) by the second oil circuit together with the fluid that fluid in fuel tank (9) is discharged through the second one-way valve (6) and oil hydraulic cylinder (10) rod chamber, the oil-discharging cavity of two-way pump (2) exports fluid to oil hydraulic cylinder (10) rodless cavity, and piston rod stretches out;
Piston rod is return: actuating motor (1) drives two-way pump (2) reversion, under the hydraulic energy of two-way pump (2), the fluid of oil hydraulic cylinder (10) rodless cavity flows to the oil sucting cavity of two-way pump (2) through the first oil circuit, oil hydraulic cylinder (10) rod chamber is flowed into again by the second oil circuit, now differential unloading valve (3) side obtains electric, hydraulic fluid port P to hydraulic fluid port B connects, a part of fluid of rodless cavity simultaneously by differential unloading valve (3) earial drainage to fuel tank (9).
2. the controlling method of the oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid according to claim 1 combination drive, when it is characterized in that piston rod is return, by controlling the rotating speed of actuating motor (1), control the fluid changes in flow rate that two-way pump (2) is discharged, realize the control of oil hydraulic cylinder (10) piston rod being return to speed.
3. the controlling method of the oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid according to claim 1 and 2 combination drive, it is characterized in that two-way oil circuit is respectively equipped with pressure transducer, pressure transducer feeds back signal to servo driver (13) formation and controls the pressure closed loop of two-way oil circuit, the piston rod correspondence of oil hydraulic cylinder (10) arranges displacement transducer (11), feeds back signal to the position-force control of servo driver (13) formation to piston rod by displacement transducer (11).
CN201310241735.9A 2013-06-18 2013-06-18 The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method Active CN103307060B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201310241735.9A CN103307060B (en) 2013-06-18 2013-06-18 The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201310241735.9A CN103307060B (en) 2013-06-18 2013-06-18 The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method

Publications (2)

Publication Number Publication Date
CN103307060A CN103307060A (en) 2013-09-18
CN103307060B true CN103307060B (en) 2016-02-03

Family

ID=49132642

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201310241735.9A Active CN103307060B (en) 2013-06-18 2013-06-18 The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method

Country Status (1)

Country Link
CN (1) CN103307060B (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103470578B (en) * 2013-09-29 2015-09-30 长春工程学院 Directly driving type differential volume control electro-hydraulic servo control system
CN103644172B (en) * 2013-12-20 2015-12-30 徐州重型机械有限公司 A kind of telescopic oil cylinder of crane detects and protective gear and method
CN104047912B (en) * 2014-06-25 2016-02-24 天津大学 The digital pump controlled hydraulic differential cylinder in self-powered source
CN104652523B (en) * 2014-12-17 2018-02-16 徐工集团工程机械股份有限公司科技分公司 A kind of loading machine electronic-hydraulic complex control hydraulic system and its control method
CN105570240A (en) * 2016-02-25 2016-05-11 河海大学常州校区 Direct-driven hydropress electro-hydraulic servo system
CN105715597B (en) * 2016-03-18 2018-07-20 中冶赛迪工程技术股份有限公司 Constant backpressure Direct Drive Electro-hydraulic Servo System and its control method
CN109915441B (en) * 2019-03-01 2020-09-18 中国飞机强度研究所 Unloading impact-resistant method and device for large-volume servo oil cylinder
KR102216916B1 (en) * 2019-08-27 2021-02-18 주식회사 케이브이엔텍 Electro hydrostatic actuator for ship
CN111075799A (en) * 2019-12-04 2020-04-28 福建工程学院 Variable-speed pump control cylinder speed closed-loop control method
CN111174889A (en) * 2020-02-04 2020-05-19 中冶南方连铸技术工程有限责任公司 Automatic casting blank weighing system and method

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4520626A (en) * 1981-01-10 1985-06-04 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for single rod cylinder
US4669266A (en) * 1983-10-05 1987-06-02 Kubik, Inc. Closed-loop system for unequal displacement cylinder
US5476031A (en) * 1991-10-10 1995-12-19 Robert Bosch Gmbh Hydraulic setting device
CN1800654A (en) * 2005-12-20 2006-07-12 武汉科技大学 Asymmetric cylinder closed-loop speed system controlled by electro-hydraulic proportional pump
CN101235836A (en) * 2008-03-05 2008-08-06 陈岩 Pump control type electrohydraulic actuator
CN101334055A (en) * 2008-07-31 2008-12-31 哈尔滨工业大学 Unpowered oil supplied direct drive displacement control electrohydraulic servo- closed type oil source system
CN101793276A (en) * 2010-02-08 2010-08-04 上海汇益控制系统股份有限公司 Electrohydraulic servo system for two-way high-speed switch
CN101865190A (en) * 2010-06-29 2010-10-20 哈尔滨工业大学 Position and flow double-close-loop direct-drive volume control electro-hydraulic servo system
CN202108817U (en) * 2011-06-23 2012-01-11 九江东升科技开发有限公司 Electro-hydraulic actuator controlled by flow regulating valve
CN102588358A (en) * 2012-02-20 2012-07-18 北京理工大学 High-performance energy saving type electro-hydraulic servo control oil line
CN203362711U (en) * 2013-06-18 2013-12-25 南京埃尔法电液技术有限公司 Hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10303360A1 (en) * 2003-01-29 2004-08-19 O & K Orenstein & Koppel Gmbh Hydraulic system for displacement-controlled linear drives

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4520626A (en) * 1981-01-10 1985-06-04 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for single rod cylinder
US4669266A (en) * 1983-10-05 1987-06-02 Kubik, Inc. Closed-loop system for unequal displacement cylinder
US5476031A (en) * 1991-10-10 1995-12-19 Robert Bosch Gmbh Hydraulic setting device
CN1800654A (en) * 2005-12-20 2006-07-12 武汉科技大学 Asymmetric cylinder closed-loop speed system controlled by electro-hydraulic proportional pump
CN101235836A (en) * 2008-03-05 2008-08-06 陈岩 Pump control type electrohydraulic actuator
CN101334055A (en) * 2008-07-31 2008-12-31 哈尔滨工业大学 Unpowered oil supplied direct drive displacement control electrohydraulic servo- closed type oil source system
CN101793276A (en) * 2010-02-08 2010-08-04 上海汇益控制系统股份有限公司 Electrohydraulic servo system for two-way high-speed switch
CN101865190A (en) * 2010-06-29 2010-10-20 哈尔滨工业大学 Position and flow double-close-loop direct-drive volume control electro-hydraulic servo system
CN202108817U (en) * 2011-06-23 2012-01-11 九江东升科技开发有限公司 Electro-hydraulic actuator controlled by flow regulating valve
CN102588358A (en) * 2012-02-20 2012-07-18 北京理工大学 High-performance energy saving type electro-hydraulic servo control oil line
CN203362711U (en) * 2013-06-18 2013-12-25 南京埃尔法电液技术有限公司 Hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
普通电液泵控差动缸系统组成;李建国;《一种新的电液泵控差动缸系统的研究》;20111215(第S2期);第9-10页 *

Also Published As

Publication number Publication date
CN103307060A (en) 2013-09-18

Similar Documents

Publication Publication Date Title
CN103307060B (en) The oil hydraulic cylinder control system of directly driving type servo-pump control electricity liquid combination drive and controlling method
CN100424361C (en) Closed electrohydraulic controlling system
CN101865190B (en) Position and flow double-close-loop direct-drive volume control electro-hydraulic servo system
CN102588358B (en) High-performance energy saving type electro-hydraulic servo control oil line
CN100553934C (en) The injection machine system of the compound control of mechanical electronic hydraulic
WO2014019272A1 (en) Membrane seawater desalination pressurization and energy recovery integrated method and device
CN102155476B (en) Regulating method of valve controlled regulating system without throttling loss based on PWM (pulse-width modulation)
CN104047912B (en) The digital pump controlled hydraulic differential cylinder in self-powered source
CN104806588B (en) Dual-pump flow-converging hydraulic control system
CN203362711U (en) Hydraulic cylinder control system conducting direct driving type servo pump control electro-hydraulic combination driving
CN103842663A (en) Control system for operating work device for construction machine
CN104632794A (en) Electro-hydraulic servo system of direct drive type hydraulic hoist
CN108506286A (en) A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect
CN203548436U (en) Directly-driven type differential-volume-controlled electro-hydraulic servo control system
CN103470578B (en) Directly driving type differential volume control electro-hydraulic servo control system
CN104564854B (en) Multi executors heavy duty digital hydraulic loop based on high-pressure common rail cabin
CN206860567U (en) A kind of loading machine joint energy supply hydraulic system
CN103062140A (en) Hydraulic device on basis of confluence control mode
CN105134573A (en) Plunger piston combined type digital variable pump
CN201560422U (en) Electro-hydraulic proportional control piston-type single-hoisting-point hydraulic hoist
CN201407049Y (en) Energy-saving shield cutterhead closed-loop hydraulic control system adopting grouped energy accumulator
CN208634118U (en) The distributed direct of the double accumulators of the double constant displacement pumps of motor driven drives excavator hydraulic system
CN103213494B (en) The double speed walking electrohydraulic control system of self-walking machinery
CN108591144A (en) The distributed direct of the double accumulators of the double constant displacement pumps of motor driving drives excavator hydraulic system
CN109083893A (en) A kind of Multi-stage cylinder luffing movement hydraulic circuit of low impact

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
SE01 Entry into force of request for substantive examination
C10 Entry into substantive examination
TA01 Transfer of patent application right

Effective date of registration: 20151020

Address after: 211100 Jiangning Economic Development Zone, Jiangsu Province, general Avenue, No. 155, No.

Applicant after: Nanjing Estun Automation Co., Ltd.

Address before: 211102 No. 178 Yan Hu Road, Jiangning Development Zone, Jiangsu, Nanjing, China

Applicant before: Aierfa Electrohydraulic Technology Co., Ltd., Nanjing City

Applicant before: Nanjing Estun Automation Co., Ltd.

C41 Transfer of patent application or patent right or utility model
GR01 Patent grant
C14 Grant of patent or utility model