EP1288507A2 - Systeme d'entrainement a faible perte pour un actuateur hydraulique - Google Patents

Systeme d'entrainement a faible perte pour un actuateur hydraulique Download PDF

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Publication number
EP1288507A2
EP1288507A2 EP02023249A EP02023249A EP1288507A2 EP 1288507 A2 EP1288507 A2 EP 1288507A2 EP 02023249 A EP02023249 A EP 02023249A EP 02023249 A EP02023249 A EP 02023249A EP 1288507 A2 EP1288507 A2 EP 1288507A2
Authority
EP
European Patent Office
Prior art keywords
drive system
actuator
control
pump
pumps
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.)
Granted
Application number
EP02023249A
Other languages
German (de)
English (en)
Other versions
EP1288507B1 (fr
EP1288507A3 (fr
Inventor
Bernhard Zervas
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.)
Eaton Fluid Power GmbH
Original Assignee
Aeroquip Vickers International GmbH
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
Priority claimed from DE19642163A external-priority patent/DE19642163A1/de
Application filed by Aeroquip Vickers International GmbH filed Critical Aeroquip Vickers International GmbH
Priority claimed from EP96944055A external-priority patent/EP0873475B1/fr
Publication of EP1288507A2 publication Critical patent/EP1288507A2/fr
Publication of EP1288507A3 publication Critical patent/EP1288507A3/fr
Application granted granted Critical
Publication of EP1288507B1 publication Critical patent/EP1288507B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/265—Control of multiple pressure sources
    • F15B2211/2658—Control of multiple pressure sources by control of the prime movers
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30585—Assemblies of multiple valves having a single valve for multiple output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a drive system with at least two hydraulic actuators, which means at least one pump with a hydraulic fluid are available.
  • Machines with multiple actuators the whole or some sequentially different work movements are usually carried out using a control valve circuit by one or several pumps that are driven at constant speed are supplied with hydraulic energy.
  • the technical disadvantage of these systems is one poor efficiency because the control valves, due to the principle, hydraulic energy into thermal energy implement.
  • a drive system having the features of claim 1.
  • According to the invention can be a hydraulic actuator through two bidirectional speed-controlled pumps, without any control valve and therefore extremely low loss control or regulate in four-quadrant operation.
  • the two pumps have a valve circuit is assigned, especially in the case of sequential Do the two pumps run each active actuator or with single-acting operation assign two actuators.
  • the valve arrangement enables advantageously use of only two pumps that are over the valve assembly connect with the individual actuators with little loss to let. So there can be a larger number Saving pumps, which simplifies the construction and makes more economical.
  • the valve arrangement has essential the task of connecting between to produce the pumps and the actuators with little loss, the control functions directly from the pumps be taken over.
  • valve arrangement has several switching positions on, each with an actuator in double-acting Operating mode connected to the two pumps becomes.
  • valve arrangement has switch positions which a connection of the two pumps with different Actuators allows, so that Have two actuators operated at the same time.
  • the valve arrangement preferably has switch positions, in which the two pumps are connected in parallel and supply one actuator together.
  • valve arrangement can be designed with seat valves to the currently not driven Actuators free of leakage.
  • valve arrangement for single actuators with counterbalance valves.
  • An embodiment of the drive is preferred, which is characterized in that at least one the pumps have a constant displacement.
  • Such pumps are of a particularly simple construction, making it an inexpensive and trouble-free Realization results.
  • the one cooperating with the drive device Control has as a control circuit is formed and at least one sensor includes, location, speed and / or acceleration of the actuator and / or on the actuator acting pressure or that from the actuator exerted forces recorded. That way it is possible, the drive very variable to the actual Adapt conditions.
  • Figure 1 shows a hydraulic double acting Piston arrangement trained actuator 1, the one has movable piston 5 in a cylinder 3, on which a piston rod 7 is attached.
  • the piston 5 and the piston rod 7 are in the cylinder 3 used that two pressure chambers 9 and 11 be formed.
  • the first pressure chamber 9 is via a feed line 13 connected to a pump 15, which is a drive device 17 is assigned. This includes one Electric motor 19, which is only indicated here Shaft 21 connected to the first pump 15 is.
  • the first pump 15 is via a supply line 23 connected to a tank 25.
  • Parallel a valve 27 is provided for the pump 15, on the one hand with the supply line 13 and on the other hand with the supply line 23 is connected.
  • the valve 27 is designed here as a check valve that is arranged so that at a negative pressure in the Supply line 13 the hydraulic medium present in the tank 25 can be sucked up, even if the first Pump 15 should not be driven.
  • the second pressure chamber 11 is an identical supply system assigned: One feeds via a feed line 13 ' second pump 15 'a hydraulic medium from the Tank 25.
  • the second pump 15 ' is for this purpose Supply line 23 'connected to the tank 25.
  • the second pump 15 ' is a drive device 17 'assigned. It is possible to use the two pumps 15 and 15 'via a single motor, for example To drive electric motor 19.
  • the one shown here The embodiment includes the drive device 17 'a second electric motor 19 ', the via a shaft 21' indicated here drives second pump 15 '.
  • Parallel to the second Pump 15 ' is again provided with a valve, designed as a check valve 27 'and arranged so is that with a negative pressure in the supply line 13 'Hydraulic medium via the supply line 23 'are sucked out of the tank 25 can.
  • the feed line 13 ' is via a pressure relief valve 29 'connected to the return line 31, which leads to tank 25.
  • the hydraulic system assigned to the actuator 1 can be formed with a cooler 33, which here in the supply line 23 integrated to the first pump 15 is. It is also possible to use this cooler 33 to be installed anywhere in the hydraulic system. After all, it is also conceivable to have one or more the supply lines with cooling fins provided to dissipate excess heat.
  • the piston 5 moves within the cylinder 3 to the right. This also causes the piston rod 7 moved to the right.
  • the second Pump 15 ' is now operated as a motor that the coupled electric motor 19 drives. This works now as a generator and converts the drive energy into electrical energy and feeds them back into the electrical system of the drive, where they are used to supply the first electric motor 19 can be reused.
  • one of the pumps 15, 15 ' operates as a motor and the associated electric motor 19, 19 ' as a generator what the efficiency of the drive significantly improved.
  • the drive for the actuator shown in Figure 1 1 also shows a control 35, the control lines 37 and 37 'with the electric motors 19 and 19 'is connected.
  • At least one sensor 39 is assigned to the actuator 1, whose output signals via a signal line 41 fed to an evaluation circuit 43 be together with the control 35 a Control circuit 45 forms.
  • the evaluation circuit 43 can at least one external via a line 47 Signal are supplied via the drive can be influenced for the actuator 1.
  • the sensor 39 which comprise an analog / digital converter can, is capable of various physical To detect sizes of the actuator 1, for example its location, the speed and / or acceleration of the piston 5 respectively the piston rod 7, which in the supply lines 13th and / or 13 'given pressure and / or that of the Actuator 1 applied forces. It is also conceivable that physical quantities of the actuator 1 by Sensors in the feed lines 13 and 13 'respectively in the control 35 and / or the evaluation circuit 43 or the electric motors 19 and 19 'are recorded indirectly. It can also be a or several sensors, for example current or Speed sensors, in the control 35 or Electric motors 19 and 19 'can be integrated. Thereby the external sensor 39 may optionally be omitted and realized a modular construction of the drive become.
  • Figure 1 shows that overall a drive for an actuator 1 that can be implemented Allows two or four quadrant operation.
  • the control 35 is implemented as a control circuit or if this, as shown in the figure, as a control circuit is formed, for example as a single-loop control loop.
  • the control circuit can be continuous Controllers, for example PID and / or state controllers with / without observer or discontinuous controller include. It can also be constructed in such a way that one or more of the physical quantities in parallel or be regulated sequentially.
  • the means controllers with I, PI or PID behavior are preferred Regulator with integrating parts used.
  • the Control circuit is by means of analog or digital technology or a combination of analog and digital technology realizable.
  • the pumps 15 and 15 ' are constant pumps designed, that is, they exhibit a constant Displacement volume. It is conceivable also, one or both of the pumps as variable displacement pumps train, with one or two displacement rooms can be realized. It is essential that too a four-quadrant drive can be implemented without any throttle valves in the supply lines 13 and 13 'to be installed.
  • the drive for the actuator 1 therefore works particularly low loss. From what has been said it also becomes clear that the drive is very is simple and therefore inexpensive to implement, because even for a four-quadrant drive only Pumps with a constant displacement are required, that is, they can be realized relatively inexpensively Pump. All it takes is a drive for the pumps, the variable flow rates allows. This is already done with the help of one Electric motor possible, the variable speed and which is controlled via the control 35 becomes.
  • the drive for the actuator 1 can So compared to the representation in the figure be further simplified, while still having a four-quadrant drive is feasible.
  • the drive shown here also meets high safety requirements, because on the one hand pressure relief valves 29, 29 'and on the other hand as suction valves trained valves 27, 27 'are provided.
  • the valves 27, 27 ', 29 and 29' have only a safety function and are for the normal operation of the drive is not required means they are inactive.
  • a particularly simple structure can thereby be achieved that the electric motors 19 and 19 ' with the associated pumps 15 and 15 'as a unit can be trained.
  • the delivery rate of the Pumping is done by adjusting the engine speed or the speed reached what with the control 35 is possible.
  • This can also be built into the motor and pump Unit to be integrated so that one results in a particularly compact structure. Because the actuator clamped between the two pumps 15 and 15 ' there is high rigidity.
  • the areas of the piston 5, which with that in the pressure chambers 9 and 11 pressure prevailing are different sizes.
  • the area of the first pressure chamber 9 results from the piston rod 7 an annular area that is smaller than the cross-sectional area of the piston 5, which with the in the second pressure chamber 11 applied pressure becomes.
  • there may be proportions or area ratios of 2: 1 of the pressurized piston surfaces result.
  • the delivery volumes of the pumps 15 and 15 ' this area ratio can be adjusted. Thereby can in turn the electric motors 19 and 19 ' operated at the same speed. It is however, it is readily apparent that pumps with same funding volume can be used, which operated at different drive speeds become.
  • the simple Actuator drive for position and pressure control and / or for a speed and Pressure control can be designed.
  • the drive for the actuator in addition to the speed-dependent Delivery regulation by the electric motors 19 or 19 ', also controlled thereby be that the displacement of the Pumping is changed. So it turns out that the Drive for the actuator 1 in a variety of ways changed and adapted to different areas of application can be.
  • FIG. 2 shows a drive system 51 which from several, in this case four actuators 1.1 to 1.4 exists.
  • a drive system 51 is part of a machine that does different work movements in whole or in part sequential sequence performs.
  • the actuators 1.1 to 1.3 are each around a hydraulic double-acting piston cylinder, as he already did in connection with figure 1 has been described. On another description is therefore waived. Only the Actuator 1.4 differs in that it is a hydraulic motor.
  • the pump unit surrounded by a dashed line 53 is promoted from a tank 25.
  • the pump unit 53 has two pumps 15, 15 ', those with the shaft 21 or 21 'of that Electric motor 19 or 19 'driven become.
  • the two supply lines 23, 23 'of two pumps 15, 15 ' are connected to the tank 25.
  • check valves 27 shown in Figure 1, 27 ', and the pressure relief valves 29, 29' are the For clarity shown as switch block 55. However, the mode of operation corresponds to that valves 27 and 29.
  • the control unit 57 comprises a control circuit 45 for each actuator, the one control 35 and an evaluation circuit 43 includes.
  • the one assigned to an actuator Evaluation circuit 43 is connected via line 41 the signal supplied by the sensor 39 is supplied.
  • the wiring of the aforementioned components corresponds that described with reference to FIG. 1, so that on the exact functioning on this No need to go into more detail.
  • FIG. 2 also allows a valve arrangement 59 recognize that in the by the two pumps 15, 15 ' coming and leading to the actuators 13 is switched.
  • the valve arrangement has two hydraulic inputs 61.1 and 61.2, whereby the first input 61.1 with the pump 15 and the second input 61.2 connected to the pump 15 ' is.
  • two outputs 63.1, 63.1 'to 63.4, 63.4' are provided.
  • the outputs 63.1 to 63.4 are each one with the supply line 13 Actuators 1.1 to 1.4 connected, the outputs 63.1 ' to 63.4 'each with the supply line 13' of an actuator.
  • the valve assembly 59 has several, in the present Embodiment preferably four switch positions in which the inputs 61.1 and 61.2 connected to predetermined outputs 63 with little loss become.
  • the switching position of the valve arrangement 59 can for example via a control line 63 change the control unit 57.
  • the exemplary embodiment is the pump unit 53 in FIG Switch position II with the actuator 1.2, in the Switch position III with the actuator 1.3 and in one Switch position IV with the hydraulic motor 1.4 connected.
  • the pump unit 53 in FIG Switch position II with the actuator 1.2, in the Switch position III with the actuator 1.3 and in one Switch position IV with the hydraulic motor 1.4 connected.
  • Assignments of pump unit 53 and the actuators conceivable per switch position.
  • valve assembly 59 So is in the switching position of the valve assembly shown 59 the input 61.1 with the output 63.2 and the input 61.2 connected to the output 63.4.
  • the valve arrangement 59 has one Exit 65 on the line 67 to the tank 25 leads.
  • This output 65 is connected on the one hand with the output 63.2 'and on the other hand with the Exit 63.4 '.
  • the pump 15 With the help of this circuit it is possible, the pump 15 to drive the actuator 1.2 and the pump 15 'for driving the hydraulic motor 1.4 to use.
  • By using reversible Pumps 15, 15 'it is otherwise possible movement of the actuators in two directions bring about.
  • valve arrangement can be 59 so that for every desired combination of operations two actuators one switching position is provided.
  • FIG. 2 Another exemplary embodiment is shown in FIG. the basic structure of which is shown in FIG. 2 shown embodiment corresponds. On a repeated description of the same reference numerals marked parts are therefore omitted.
  • valve arrangement 59 With the help of the valve arrangement 59 is in the present Embodiment another mode allows.
  • FIG. 4 shows that the inputs 61.1 and 61.2 in the switching position of the valve arrangement shown 59 connected to the output 63.3 are, while the output 63.3 'with the output 65 connected is. Both pumps thus deliver 15, 15 ' Hydraulic fluid via the feed line 13 in the Actuator 1.3 for its actuation. In the others Switch positions of the valve arrangement 59 can be then actuators 1.1, 1.2 and 1.4 with the two Connect pumps 15, 15 '.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP02023249A 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour un actuateur hydraulique Expired - Lifetime EP1288507B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19600650A DE19600650C2 (de) 1996-01-10 1996-01-10 Antrieb für einen hydraulischen doppelwirkenden Aktuator
DE19600650 1996-01-10
DE19642163 1996-10-12
DE19642163A DE19642163A1 (de) 1996-01-10 1996-10-12 Verlustarmer Antrieb für mehrere hydraulische Aktuatoren
EP96944055A EP0873475B1 (fr) 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour plusieurs actuateurs hydrauliques

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP96944055A Division EP0873475B1 (fr) 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour plusieurs actuateurs hydrauliques

Publications (3)

Publication Number Publication Date
EP1288507A2 true EP1288507A2 (fr) 2003-03-05
EP1288507A3 EP1288507A3 (fr) 2003-05-07
EP1288507B1 EP1288507B1 (fr) 2006-01-18

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02023249A Expired - Lifetime EP1288507B1 (fr) 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour un actuateur hydraulique

Country Status (4)

Country Link
EP (1) EP1288507B1 (fr)
DE (2) DE19600650C2 (fr)
IN (1) IN188385B (fr)
ZA (1) ZA9777B (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
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DE102010017912A1 (de) * 2010-04-21 2011-10-27 Voith Patent Gmbh Hydraulischer Antrieb und Verfahren zum Betreiben eines hydraulischen Antriebs
CN104179736A (zh) * 2014-08-15 2014-12-03 徐工集团工程机械股份有限公司科技分公司 一种工程机械定量泵调速液压***
US9689407B2 (en) 2014-09-19 2017-06-27 Voith Patent Gmbh Hydraulic drive with rapid stroke and load stroke
US9903394B2 (en) 2014-09-19 2018-02-27 Voith Patent Gmbh Hydraulic drive with rapid stroke and load stroke
JPWO2017056702A1 (ja) * 2015-09-28 2018-06-14 ボッシュ・レックスロス株式会社 油圧シリンダ駆動装置
CN109915442A (zh) * 2019-03-19 2019-06-21 江门市蒙德电气股份有限公司 一种基于双向进压调节的液压缸位置控制***及控制方法
US11384777B2 (en) 2018-08-21 2022-07-12 Siemens Energy, Inc. Double-acting hydraulic actuator with different pumps for each actuation direction

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US6374606B1 (en) 1999-03-19 2002-04-23 Caterpillar S.A.R.L. Dual pump ejector system for articulated trucks and the like having horizontal discharge
DE10084361T1 (de) * 1999-03-19 2002-04-25 Caterpillar S A R L C O Caterp Fahrzeugmaterialauswurfsteuersystem und -verfahren
DE102005010638A1 (de) * 2005-03-08 2006-09-28 Bosch Rexroth Aktiengesellschaft Hydraulische Betätigungsvorrichtung, insbesondere für ein Cabriolet
DE102008039011B4 (de) * 2008-08-21 2020-01-16 MAE Maschinen- u. Apparatebau Götzen GmbH Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
DE102008053766A1 (de) * 2008-10-21 2010-04-22 Voith Patent Gmbh Hydraulischer Pressenantrieb und Verfahren zum Betreiben eines hydraulischen Pressenantriebs
EP2712688B1 (fr) 2012-09-28 2020-12-02 Siemens Aktiengesellschaft Entraînement de coussin hydraulique et procédé de fonctionnement d'un entraînement de coussin hydraulique
DE102013212937A1 (de) * 2013-07-03 2014-07-10 Voith Patent Gmbh Vorrichtung zum Öffnen und Schließen der Leitschaufeln einer hydraulischen Maschine
EP2824334A1 (fr) 2013-07-08 2015-01-14 Siemens Aktiengesellschaft Entraînement linéaire hydraulique
EP3173163A1 (fr) 2015-11-30 2017-05-31 Siemens Aktiengesellschaft Procédé de commande ou de régulation du mouvement d'un outil, système hydraulique, presse dotée de coussin de serre-flan et dispositif de commande
DE102019121974A1 (de) 2019-08-15 2021-02-18 Voith Patent Gmbh Überhitzungsschutz für hydraulische Systeme

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DE102010017912A1 (de) * 2010-04-21 2011-10-27 Voith Patent Gmbh Hydraulischer Antrieb und Verfahren zum Betreiben eines hydraulischen Antriebs
CN104179736A (zh) * 2014-08-15 2014-12-03 徐工集团工程机械股份有限公司科技分公司 一种工程机械定量泵调速液压***
CN104179736B (zh) * 2014-08-15 2016-08-24 徐工集团工程机械股份有限公司科技分公司 一种工程机械定量泵调速液压***
US9689407B2 (en) 2014-09-19 2017-06-27 Voith Patent Gmbh Hydraulic drive with rapid stroke and load stroke
US9903394B2 (en) 2014-09-19 2018-02-27 Voith Patent Gmbh Hydraulic drive with rapid stroke and load stroke
US10718357B2 (en) 2014-09-19 2020-07-21 Voith Patent Gmbh Hydraulic drive with rapid stroke and load stroke
JPWO2017056702A1 (ja) * 2015-09-28 2018-06-14 ボッシュ・レックスロス株式会社 油圧シリンダ駆動装置
EP3358202A4 (fr) * 2015-09-28 2018-10-10 Bosch Rexroth Corporation Dispositif d'entraînement à vérin hydraulique
US11384777B2 (en) 2018-08-21 2022-07-12 Siemens Energy, Inc. Double-acting hydraulic actuator with different pumps for each actuation direction
CN109915442A (zh) * 2019-03-19 2019-06-21 江门市蒙德电气股份有限公司 一种基于双向进压调节的液压缸位置控制***及控制方法

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IN188385B (fr) 2002-09-14
DE19600650C2 (de) 2003-05-28
EP1288507B1 (fr) 2006-01-18
ZA9777B (en) 1997-07-11
DE59610776D1 (de) 2003-11-20
EP1288507A3 (fr) 2003-05-07
DE19600650A1 (de) 1997-07-24

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