EP1588057B1 - Systeme hydraulique pour entrainements lineaires commandes par des elements deplaceurs - Google Patents

Systeme hydraulique pour entrainements lineaires commandes par des elements deplaceurs Download PDF

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Publication number
EP1588057B1
EP1588057B1 EP04701896A EP04701896A EP1588057B1 EP 1588057 B1 EP1588057 B1 EP 1588057B1 EP 04701896 A EP04701896 A EP 04701896A EP 04701896 A EP04701896 A EP 04701896A EP 1588057 B1 EP1588057 B1 EP 1588057B1
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EP
European Patent Office
Prior art keywords
valve
hydraulic system
hydraulic
high pressure
pump
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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.)
Expired - Lifetime
Application number
EP04701896A
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German (de)
English (en)
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EP1588057A1 (fr
Inventor
Monika c/o Purdue University IVANTYSYNOVA
Robert Rahmfeld
Erik Lautner
Jürgen Weber
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CNH Industrial Baumaschinen GmbH
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CNH Baumaschinen GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/082—Servomotor systems incorporating electrically operated control means with different modes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the invention relates to a hydraulic system for displacer-controlled linear drives, in particular for mobile machines with at least one differential cylinder, at least one high pressure circuit, which includes at least one pump with adjustable flow and is connected by at least two unlockable check valves with a low pressure system.
  • Hydraulic systems for mobile machines today rely predominantly on valve-controlled principles.
  • the various hydraulic consumers such as drives of the working hydraulics, steering, braking u.a. controlled.
  • one or more central pressure supplies often in the form of load-sensing pumps, are used for this purpose, which provide pressure medium flows which are influenced by single or multi-stage valve arrangements in accordance with the desired behavior of the hydraulic consumers.
  • a disadvantage of these valve-controlled hydraulic systems is in particular the poor energy efficiency.
  • pressure differences are required at the throttle edges of the valves, which in principle leads to high energy losses in hydraulic valve controls. It is not possible to use energy surpluses at a consumer of the system in the form of potential energy or braking energy for other consumers in the system and thereby improve the system efficiency, which further deteriorates the heat generation in the system.
  • a central pressure medium supply also has the disadvantage that in the case that several consumers must be operated simultaneously, the volume flows are divided, which complicates the precise control and operation of the individual components.
  • Safety-relevant circuits in which it must be ensured that individual consumers, such as the steering or brake, always have enough pressure fluid available, for example, must always be implemented on complicated priority valve arrangements. A simultaneous movement of several consumers in the system leads to a different system behavior compared to single movements. All this leads to very complex and thus cost and maintenance-intensive valve arrangements whose possibilities are limited in terms of controllability and energy utilization.
  • displacement-controlled systems for rotary drives are also used, in which a pump adjustable in the displacement volume is used to control or regulate the movement of the hydraulic motor (s).
  • the consumer is thus controlled solely by the volume flow provided by the pump, without the use of a control valve or the like in the main circuit.
  • this control principle to linear actuators with differential cylinder, the problem arises that the cylinder volume is different on both sides of the cylinder piston and thereby occur in the movement of differential flow, which must be compensated by different known solutions.
  • the object of the invention is therefore to provide a hydraulic system for linear drives with differential cylinder, especially for mobile machines, which avoids the manifold disadvantages of the prior art by the use of a displacement control of the drives and allows precise energy-efficient control of linear drives with differential cylinders, cost and easy to maintain and integrate well into the overall hydraulic system of such machines.
  • the check valves are located between the two high-pressure lines, which lead from the adjustable in their flow pump to the differential cylinder, and the common low-pressure system. If a volume flow is generated by the adjustable pump and thereby the differential cylinder is moved, the occurring depending on the direction of movement of the piston, positive or negative differential flow can flow into the low-pressure system and be sucked out of this. In the case of the intake of volume flow from the low pressure system, the corresponding check valve opens automatically. In the case of outflow from the flow to the low pressure system, the corresponding check valve is released from the system high pressure.
  • the two sides of the Differential cylinder hydraulically connected to each other, whereby a free movement of the piston is made possible.
  • the check valves are unlocked, so that pressure medium can flow through them regardless of the pump volume flow in both directions.
  • the differential volume flow is compensated in this case also by the low pressure system.
  • the hydraulic system provides that the electronic Control device for controlling the check valves has an electro-hydraulic 4/2-way valve.
  • the Entsperr- connection of the check valves can be alternately connected to one or the other side of the high pressure circuit, which corresponds to a switching between the normal differential volume compensation and the floating position of the differential cylinder.
  • two electro-hydraulic 3/2-way valves can be used.
  • control device for controlling the pump delivery rate is electronically formed.
  • the flow rate of adjustable pumps is usually controlled electro-hydraulically. Therefore, it is particularly advantageous if this control is applied integrated with the control device of the check valves, so that a safe and accurate control of the complete circular behavior is possible. Thus, for example, prevent the pump promotes a volume flow when unlocking the check valves, which would then be closed by the unblocked check valves short.
  • a particular embodiment of the hydraulic system provides that a controllable shut-off valve is provided on at least one connection of the differential cylinder.
  • a connection of the cylinder can be shut off leak-free, which is useful in particular for the realization of a holding function.
  • the cylinder is brought by the volume flow of the pump in a certain position and then shut off the high-pressure port of the differential cylinder, so that this remains in its position, even without the pump maintains the pressure.
  • a shut-off valve is also provided at the second port of the differential cylinder, the cylinder can be completely disconnected from the hydraulic circuit while remaining in position.
  • a further differential cylinder can be operated in this state, which is then also separable via shut-off valves from the circuit. This can be easily and inexpensively another function in the Implement working machine, which can be operated alternatively by the other existing cylinders.
  • the low pressure system is designed as a storage charging circuit with a storage charging valve, a pump with hydraulic accumulator and a pressure relief valve.
  • a storage charging valve characterized by a particularly high energy efficiency.
  • the pump only delivers to the low-pressure system when it falls below a set minimum pressure value.
  • the storage charging circuit ensures that a low pressure level is maintained between adjustable limits.
  • Such a low-pressure system can be designed centrally for the entire hydraulic system and supply all displacer-controlled hydraulic circuits according to the invention.
  • a further embodiment of the hydraulic system according to the invention is characterized in that the controllable shut-off valve is designed as a seat valve with 3/2-way pilot control.
  • the controllable shut-off valve is designed as a continuous valve. With such a valve, it is easy to realize the corresponding blocking function of the connection without the valve opening or closing being too jerky. This can prevent unwanted pressure peaks in the system.
  • shut-off valves are provided for alternative and / or simultaneous control of additional differential cylinders.
  • additional differential cylinders can be realized by such valves further functions on the same high-pressure circuit, which are always alternatively to each other in operation.
  • the shut-off valves are switched so that the pump with the associated protection and compensation valves each connected to a differential cylinder or more parallel connected the same function and supplies them with pressure medium.
  • a further embodiment of the invention provides that at the Hochdruckkeis connections are provided for a passive vibration damping system.
  • damping systems consist of a hydraulic circuit with memory, which reduces the vibrations of the implement occurring, for example, when driving with a raised load.
  • the vibration damping system is connected directly to at least one connection on one side of the high-pressure circuit and can be switched on and off in order to suppress the undesirable vibration states in desired operating situations.
  • the electronic control device, the controllable valves and possibly further existing hydraulic system components are formed with the adjustable pump as an integrated component.
  • Such integration of the pump with a number of the valves and the controller offers the advantage of an extremely compact design, which may be useful because these components are necessary for any hydraulic function driven by differential cylinder systems.
  • the integration reduces the number of individual components, reduces the complexity of the overall system, reduces the installation effort and thus reduces the cost of such a system compared to conventional systems.
  • sensors for detecting the system states in particular the differential cylinder position and the hydraulic pressures, are provided.
  • an electronic control device is provided for controlling the controllable system components depending on the measured system status and user preferences.
  • the linear cylinders can be operated in a closed loop, which significantly improves the positioning accuracy and the stability of the system.
  • the drive system according to the invention can also be controlled, i. operate in an open chain.
  • the invention is also directed to a mobile work machine having at least one hydraulic system as described above.
  • a mobile work machine having at least one hydraulic system as described above.
  • several high-pressure circuits are provided with a common low-pressure circuit. This has, as already explained, the advantage of additional cost savings, since a single low pressure circuit with a pump and the other components to supply all hydraulic systems of the invention is sufficient.
  • a generally designated 1 hydraulic system is used to control a hydraulic differential cylinder. 2
  • a pump 3 with adjustable delivery volume and reversal of the conveying direction is connected via two lines 4 and 5 with the two terminals of the differential cylinder 2.
  • the opposing check valve 7 or 8 between the high pressure line and low pressure system 9 is unlocked by the higher pressure, in one of the two lines 4 and 5, so that always the low pressure side of the hydraulic differential cylinder 2 is connected to the low pressure system 9. If a volume flow to the differential cylinder 2 is conveyed by the adjustable pump 3, this leads to a movement of the piston 6 of the differential cylinder 2.
  • the positive or negative differential volume flow dependent on the direction of movement is compensated via one of the two non-return valves 7 or 8 with respect to the low-pressure system 9.
  • For this basic position is one with the check valves 7 and 8 connected electro-hydraulic 4/2-way valve 10 is switched so that the unlocking of the check valves 7 and 8 are each connected to the opposite part of the high pressure circuit.
  • the electronically controllable 4/2-way valve 10 also serves to realize a floating position function. If the valve 10 is switched over (floating position function), the unlocking connections of the check valves 7 and 8 are no longer connected to the opposite, but with the lying in the direction of their passage side. As a result, the check valves 7 and 8 open as soon as in one of the two lines 4 or 5, a pressure is applied, which is slightly higher than the low pressure in the low pressure system 9. Thus, the piston 6 in the differential cylinder 2 can move freely. It makes sense, when switching the 4/2-way valve 10 in the floating position, the pump 3 is set so that it does not promote flow, since this would also be compensated by the quasi-short circuit through the check valves 7 and 8 respectively.
  • a controllable shut-off valve 11 is provided at a connection of the differential cylinder 2.
  • this side of the differential cylinder 2 can be shut off without leakage, whereby the piston 6 is fixed in this position and a load located thereon is held. As a rule, this is the more heavily loaded piston side of the differential cylinder. 2
  • the system contains pressure sensors 12 which are used to detect the conditions in serve the high pressure lines.
  • a displacement sensor 13 or an angle sensor in the kinematics of the working equipment which detects the piston position.
  • the signals of the sensors 12 and 13 are processed by an electronic control device 14 together with predetermined by user controls corresponding 15 user requests and determines the corresponding manipulated variable, which is forwarded to the electronic control device 16. This then controls the adjustable pump 3 in its displacement volume and thus the funded volume flow and possibly the switching states of the electronic valves 10 and 11 respectively.
  • a hydraulic differential cylinder 2 is again connected substantially directly with an adjustable pump 3.
  • the differential flow is compensated in promotion by the two pilot operated check valves 7 and 8, the Entsperran getting of an electro-hydraulic 4/2-way valve 10 are each alternately connected to the opposite or adjacent sides of the high pressure circuit.
  • the integrated electronic control device 14 controls the control of the individual components, such as the adjustable pump 3, taking into account the measured system states and the user preferences 15th
  • the second side of the differential cylinder 2 can also be shut off by an electronically controllable shut-off valve 17.
  • an electronically controllable shut-off valve 17 In addition, two additional electronically controllable shut-off valves 18, an additional differential cylinder 19 on High pressure circuit connected.
  • the first differential cylinder 2 is separated by the two shut-off valves 11 and 17 from the hydraulic circuit and thereby held in position. Subsequently, the two shut-off valves 18 are opened so that a volume flow delivered by the pump 3 moves the second differential cylinder 19. The difference volumes occurring are compensated again via the two pilot-operated check valves 7 and 8 in the low-pressure circuit 9.
  • the controllable shut-off valves 11, 17 and 18 may be formed in some cases as a continuous valves, so that they can be controlled continuously in particular situations during operation and thus a simultaneous operation of the two differential cylinders 2 and 19 is possible.
  • the low pressure in the low-pressure system 9 is realized with a storage charging circuit.
  • a fixed displacement pump 20 with a storage charging valve 21 and a hydropneumatic accumulator 22 is used.
  • a pressure relief valve 23 protects the system against overload.
  • the accumulator charging valve 21 ensures that the constant displacement pump 20 promotes into the low-pressure system 9 only when a set minimum value of the pressure is reached. Since the accumulator charging valve 21 ensures pure printer maintenance, the system can be implemented in an energy-efficient manner. But other combinations for the realization of the low-pressure system 9 are possible, for example via a simple combination of fixed displacement pump, memory and pressure relief valve or by means of a variable.
  • This low pressure is also used behind the port 24 of the variable displacement pump 3 to operate the electro-hydraulic adjustment system of this pump.
  • the terminals 25 and 26 serve to connect a passive vibration damper system on the differential cylinder 2.
  • a first modification of the basic principle in which instead of the electro-hydraulic 4/2-way valve two 3/2-way valves 28, 29 are used to realize the floating position by switching the Entsperran nowadays the pilot-operated check valves 7, 8 , Furthermore, the low pressure is now impressed via a constant displacement pump 20 with a hydropneumatic accumulator 22 and a pressure relief valve 23. 4, a further modification of the basic principle is shown.
  • the floating position is realized via a bypass by two valves 30, 31, i. when energizing the valves, the two cylinder chambers are connected to the low pressure and the differential cylinder 2 can move freely.
  • the low pressure is impressed here via a variable displacement pump 20 'with a hydropneumatic accumulator 22 and secured via a pressure relief valve 23.
  • this scheme also shows another way to provide the third function with the pump 3. Two 3/2-way valves 32, 33 at ports 34, 35 can simply switch the pump 3 to the third function when activated.
  • Fig. 5 shows an overall system for a mobile work machine (here wheel loader) with displacement-controlled working hydraulics according to the above-described displacement-controlled linear drive principle (valveless principle) and hydrostatic drive.
  • the simple coupling of several actuators via the low pressure and with the hydrostatic drive reduces the system complexity again.
  • FIG. 6 another overall system (here wheel loader) is shown, in which case there is a hydrostatic drive in the 2- engine concept with decoupled adjustment and the low pressure for all displacement-controlled Main functions is impressed by the return of the hydrostatic fan and a memory.
  • An accumulator charging valve connects the return of the fan to the low pressure only when low pressure volume flow is needed.
  • variable displacement pump By electrohydraulic control of the adjustable pump 3, all other functionalities that are backed by software, can be realized, such as fork parallel guide, automatic return, Hubendabscloc, variable blade stop, variable damping cylinder (soft dust), shaking or distribution functions on the blade for agricultural Inserts, etc.
  • the respective variable displacement pump is addressed directly via the controller of the device.
  • the displacer-controlled actuator can be operated both in position control and in speed control (example: parallel tool guide) or also in open-loop control.
  • the controller processes the input of the operator (eg via a joystick).
  • the invention is not limited to the above example, but in many ways modifiable without departing from the spirit.
  • a variety of designs for the pumps, valves, etc. are conceivable as long as they fulfill the functions claimed.
  • the separation of the functions of individual valves on several components is conceivable and may make sense. It is also possible to operate additional cylinders via shut-off valves on the same high-pressure system.

Claims (14)

  1. Système hydraulique pour des entraînements linéaires commandés en refoulement, en particulier pour des machines de travail mobiles, comprenant au moins un cylindre différentiel qui est agencé dans un circuit à haute pression fermé doté d'au moins une pompe avec débit quantitatif réglable et inversion de la direction de refoulement, dans lequel le circuit à haute pression, pour compenser le courant volumétrique différentiel, est relié à un système à basse pression via au moins deux clapets antiretour déblocables, le clapet antiretour respectivement opposé au côté haute pression du circuit à haute pression est débloqué par la haute pression,
    caractérisé en ce que
    les clapets antiretour (7, 8) sont reliés à un dispositif de commande électronique (16) de telle façon qu'une inversion sans à-coups est possible entre un déploiement/rétraction du cylindre différentiel (2) et une position flottante, et
    en ce que pour réaliser cette position flottante du cylindre différentiel (2), un distributeur électrohydraulique 4/2 (10) ou un distributeur électrohydraulique 3/2 (28, 29) est agencé entre le circuit à haute pression (4, 5) et les clapets antiretour déblocables (7, 8).
  2. Système hydraulique selon la revendication 1, caractérisé en ce que le système à basse pression (9) est réalisé sous forme de circuit de charge d'accumulateur avec une soupape de charge d'accumulateur (21), une pompe (20) avec accumulateur hydraulique (22), et une valve de limitation de pression (23).
  3. Système hydraulique selon la revendication 1, caractérisé en ce que le système à basse pression (9) est réalisé avec une pompe (20) dotée d'un accumulateur hydraulique (22) et avec une valve de limitation de pression (23).
  4. Système hydraulique selon la revendication 1, 2 ou 3, caractérisé en ce que le dispositif de commande électronique (16) est réalisé pour réguler le débit quantitatif et la direction de refoulement de la pompe (3) du circuit à haute pression.
  5. Système hydraulique selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu une valve d'isolement commandée (11) à au moins un raccordement du cylindre du différentiel (2).
  6. Système hydraulique selon la revendication 5, caractérisé en ce que la valve d'isolement commandée (11) est réalisée sous forme de valve à siège avec pilotage à 3/2.
  7. Système hydraulique selon la revendication 5, caractérisé en ce que la valve d'isolement commandée (11) est réalisée sous forme de valve continue.
  8. Système hydraulique selon l'une des revendications précédentes, caractérisé en ce que d'autres valves d'isolement commandées (17, 18), le cas échéant à commande continue, sont prévues pour le pilotage en alternative et/ou simultanément d'autres cylindres différentiels (19).
  9. Système hydraulique selon l'une des revendications précédentes, caractérisé en ce que des raccordements (25, 26) pour un système passif d'amortissement des oscillations sont prévus au niveau du circuit à haute pression.
  10. Système hydraulique selon l'une des revendications précédentes, caractérisé en ce que le dispositif de commande électronique (16), le distributeur à 4/2 (10) et la valve d'isolement (11), et le cas échéant d'autres composants existants du système hydraulique, sont réalisés sous forme de composants intégrés avec la pompe (3) du circuit à haute pression.
  11. Système hydraulique selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu des capteurs (12, 13) pour détecter les états du système, en particulier la position du cylindre différentiel et les pressions hydrauliques.
  12. Système hydraulique selon la revendication 11, caractérisé en ce qu'il est prévu un système de régulation électronique (14) pour réguler les composants commandés du système, en dépendance de l'état mesuré du système et d'instructions de la part d'un utilisateur.
  13. Machine de travail mobile comprenant au moins un système hydraulique selon l'une des revendications 1 à 12.
  14. Machine de travail mobile selon la revendication 13, caractérisé en ce qu'il est prévu plusieurs circuits à haute pression avec un système à basse pression commun.
EP04701896A 2003-01-29 2004-01-14 Systeme hydraulique pour entrainements lineaires commandes par des elements deplaceurs Expired - Lifetime EP1588057B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10303360A DE10303360A1 (de) 2003-01-29 2003-01-29 Hydrauliksystem für verdrängergesteuerte Linearantriebe
DE10303360 2003-01-29
PCT/DE2004/000032 WO2004067969A1 (fr) 2003-01-29 2004-01-14 Systeme hydraulique pour entrainements lineaires commandes par des elements deplaceurs

Publications (2)

Publication Number Publication Date
EP1588057A1 EP1588057A1 (fr) 2005-10-26
EP1588057B1 true EP1588057B1 (fr) 2007-04-04

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Country Status (6)

Country Link
US (1) US7543449B2 (fr)
EP (1) EP1588057B1 (fr)
AT (1) ATE358777T1 (fr)
DE (3) DE10303360A1 (fr)
ES (1) ES2285408T3 (fr)
WO (1) WO2004067969A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012101231A1 (de) 2012-02-16 2013-08-22 Linde Material Handling Gmbh Hydrostatisches Antriebssystem

Families Citing this family (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7325398B2 (en) * 2004-03-05 2008-02-05 Deere & Company Closed circuit energy recovery system for a work implement
CA2588290A1 (fr) 2004-12-01 2006-06-08 Haldex Hydraulics Corporation Systeme d'entrainement hydraulique
US7234298B2 (en) * 2005-10-06 2007-06-26 Caterpillar Inc Hybrid hydraulic system and work machine using same
US7191593B1 (en) 2005-11-28 2007-03-20 Northrop Grumman Corporation Electro-hydraulic actuator system
CN100424361C (zh) * 2006-03-07 2008-10-08 太原理工大学 闭式电液控制系统
US7467514B2 (en) * 2006-07-17 2008-12-23 Caterpillar Inc. System and method for controlling shakability of a work tool
US7707829B2 (en) * 2007-09-07 2010-05-04 Caterpillar S.A.R.L. Flushing system having a single charge relief valve
EP2055951B1 (fr) * 2007-11-01 2019-03-27 Danfoss Power Solutions Aps Système hydraulique chargé
US9410544B2 (en) 2007-11-01 2016-08-09 Danfoss Power Solutions Aps Charged hydraulic system
DE102008049181A1 (de) * 2008-09-26 2010-04-01 Schaeffler Kg Elektrohydraulische Ventilsteuerung
US8453441B2 (en) 2008-11-06 2013-06-04 Purdue Research Foundation System and method for pump-controlled cylinder cushioning
US7942208B2 (en) * 2008-11-06 2011-05-17 Purdue Research Foundation System and method for blade level control of earthmoving machines
US8474254B2 (en) 2008-11-06 2013-07-02 Purdue Research Foundation System and method for enabling floating of earthmoving implements
US8191290B2 (en) * 2008-11-06 2012-06-05 Purdue Research Foundation Displacement-controlled hydraulic system for multi-function machines
US9194107B2 (en) 2009-09-29 2015-11-24 Purdue Research Foundation Regenerative hydraulic systems and methods of use
US8641399B2 (en) 2009-12-23 2014-02-04 Husky Injection Molding Systems Ltd. Injection molding system having a digital displacement pump
DE102010040755A1 (de) * 2010-09-14 2012-03-15 Zf Friedrichshafen Ag Antriebsanordnung
WO2012145401A1 (fr) * 2011-04-18 2012-10-26 Concentric Rockford, Inc Augmentation de moteur de système de commande hydraulique
US8887499B2 (en) * 2011-06-29 2014-11-18 Caterpillar Inc. Electronic high hydraulic pressure cutoff to improve system efficiency
DE112012003500B4 (de) * 2011-08-24 2017-07-27 Komatsu Ltd. Hydraulisches Antriebssystem
JP5752526B2 (ja) * 2011-08-24 2015-07-22 株式会社小松製作所 油圧駆動システム
US20130081382A1 (en) * 2011-09-30 2013-04-04 Bryan E. Nelson Regeneration configuration for closed-loop hydraulic systems
US9057389B2 (en) * 2011-09-30 2015-06-16 Caterpillar Inc. Meterless hydraulic system having multi-actuator circuit
US9096115B2 (en) 2011-11-17 2015-08-04 Caterpillar Inc. System and method for energy recovery
CN102588358B (zh) * 2012-02-20 2015-01-21 北京理工大学 一种高性能节能型的电液伺服控制油路
CN102606562A (zh) * 2012-03-20 2012-07-25 王凡 双作用气缸垂直负载的定位控制机构
JP6021144B2 (ja) * 2012-07-17 2016-11-09 株式会社小松製作所 油圧駆動システム
CN104903595B (zh) * 2013-01-08 2017-03-08 日立建机株式会社 工作机械的液压系统
CN103307060B (zh) * 2013-06-18 2016-02-03 南京埃斯顿自动化股份有限公司 直驱式伺服泵控电液混合驱动的液压缸控制系统及控制方法
CN106133332B (zh) * 2014-02-04 2018-05-25 意大利德纳股份有限公司 集成到液压混合系统内的行进和作业功能
CN103899316B (zh) * 2014-03-21 2016-06-08 中铁工程装备集团有限公司 钻井法竖井钻机
GB2529909B (en) 2014-09-30 2016-11-23 Artemis Intelligent Power Ltd Industrial system with synthetically commutated variable displacement fluid working machine
US10927856B2 (en) * 2016-11-17 2021-02-23 University Of Manitoba Pump-controlled hydraulic circuits for operating a differential hydraulic actuator
CN112128153B (zh) * 2020-09-03 2022-08-05 徐州重型机械有限公司 一种新型定量泵变压差负载敏感系统及其控制方法

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2706091A1 (de) * 1977-02-12 1978-08-17 Orenstein & Koppel Ag Antrieb mit einem an einen geschlossenen hydraulischen kreislauf angeschlossenen differentialzylinder
JPS57144344A (en) * 1981-03-02 1982-09-06 Hitachi Constr Mach Co Ltd Flushing valve
SE437861B (sv) * 1983-02-03 1985-03-18 Goran Palmers Anordning vid medelst hydraul-cylinder drivna maskiner med en av en drivkella via en energiackumulatordriven pump
JPS6081502A (ja) * 1983-10-11 1985-05-09 Hitachi Constr Mach Co Ltd 油圧アクチユエ−タの閉回路駆動装置
US5819574A (en) * 1996-06-07 1998-10-13 Kabushiki Kaisha Opton Hydraulic device for bending work and a bending device with the hydraulic device mounted thereon
DE19755120A1 (de) * 1997-02-27 1998-09-03 Mannesmann Rexroth Ag Vorgesteuertes Sperrventil
DE19716081C1 (de) * 1997-04-17 1998-08-13 Hydac Technology Gmbh Antrieb für einen hydraulischen Differentialzylinder
WO2002004820A1 (fr) * 2000-07-10 2002-01-17 Kobelco Construction Machinery Co., Ltd. Circuit de verin hydraulique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012101231A1 (de) 2012-02-16 2013-08-22 Linde Material Handling Gmbh Hydrostatisches Antriebssystem
US9334884B2 (en) 2012-02-16 2016-05-10 Linde Hydraulics Gmbh & Co. Kg Hydrostatic drive system

Also Published As

Publication number Publication date
US20060218913A1 (en) 2006-10-05
ATE358777T1 (de) 2007-04-15
DE502004003395D1 (de) 2007-05-16
WO2004067969A1 (fr) 2004-08-12
ES2285408T3 (es) 2007-11-16
DE112004000521D2 (de) 2005-12-15
DE10303360A1 (de) 2004-08-19
EP1588057A1 (fr) 2005-10-26
US7543449B2 (en) 2009-06-09

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