EP0873475A1 - Systeme d'entrainement a faible perte pour plusieurs actuateurs hydrauliques - Google Patents

Systeme d'entrainement a faible perte pour plusieurs actuateurs hydrauliques

Info

Publication number
EP0873475A1
EP0873475A1 EP96944055A EP96944055A EP0873475A1 EP 0873475 A1 EP0873475 A1 EP 0873475A1 EP 96944055 A EP96944055 A EP 96944055A EP 96944055 A EP96944055 A EP 96944055A EP 0873475 A1 EP0873475 A1 EP 0873475A1
Authority
EP
European Patent Office
Prior art keywords
drive system
control
pump
actuator
actuators
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
EP96944055A
Other languages
German (de)
English (en)
Other versions
EP0873475B1 (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 DE19600650A external-priority patent/DE19600650C2/de
Priority claimed from DE19642163A external-priority patent/DE19642163A1/de
Application filed by Aeroquip Vickers International GmbH filed Critical Aeroquip Vickers International GmbH
Priority to EP02023249A priority Critical patent/EP1288507B1/fr
Publication of EP0873475A1 publication Critical patent/EP0873475A1/fr
Application granted granted Critical
Publication of EP0873475B1 publication Critical patent/EP0873475B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F15B2211/2053—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
    • F15B2211/20576—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 can be supplied with a hydraulic fluid by means of at least one pump.
  • Machines with a plurality of actuators which are intended to perform different work movements in whole or in part sequentially, are usually supplied with hydraulic energy by means of a control valve circuit which is supplied by one or more pumps which are driven at a constant speed.
  • the technical disadvantage of these systems is poor efficiency, since the control valves convert hydraulic energy into thermal energy, depending on the principle. It is an object of the present invention to provide a drive system which is of simple construction, has excellent control properties and thereby avoids the throttle losses of control valves which are inherent in the principle and therefore works with a very high degree of efficiency.
  • a hydraulic actuator can be controlled or regulated by means of two bidirectionally speed-controlled pumps without any control valve and thus with extremely little loss in four-quadrant operation. Because a valve circuit is assigned to the two pumps, the two pumps can each be assigned to the active actuator or, in the case of simple operation, two actuators, particularly in the case of sequential processes.
  • the valve arrangement advantageously allows only two pumps to be used, which can be connected to the individual actuators with little loss via the valve arrangement. It is therefore possible to save a larger number of pumps, which simplifies the construction and makes it more economical.
  • the valve arrangement essentially has the task of establishing the connection between the pumps and the actuators with little loss, the control functions being taken over directly by the pumps.
  • the valve arrangement has a plurality of switching positions, in each of which an actuator is connected to the two pumps in double-acting mode.
  • the valve arrangement has switching positions which enable the two pumps to be connected to different actuators, so that two actuators can be operated simultaneously.
  • the valve arrangement preferably has switching positions in which the two pumps are connected in parallel and jointly supply an actuator.
  • valve arrangement can be designed with seat valves in order to fix the currently non-driven actuators without leakage.
  • valve arrangement for single-actuated actuators can be designed with counterbalance valves.
  • An embodiment of the drive is preferred, which is characterized in that at least one of the pumps has a constant displacement volume. Pumps of this type are of particularly simple construction, so that they are implemented in a cost-effective and trouble-free manner.
  • an embodiment of the drive which has a control cooperating with the drive device, which is designed as a control circuit and comprises at least one sensor, the position, speed and / or acceleration of the actuator and / or the pressure acting on the actuator or the forces exerted by the actuator are detected. That way it is possible to adapt the drive very variably to the actual circumstances.
  • more than two pumps can also be used to drive a plurality of actuators.
  • Figure 1 is a schematic diagram of the drive
  • FIG. 2 shows a basic circuit diagram of a drive system with several actuators
  • FIG. 3 shows a second exemplary embodiment of a drive system with a plurality of actuators
  • Figure 4 shows a third drive system with several actuators.
  • the drive interacts with a double-acting piston arrangement.
  • it can generally be combined with any hydraulic actuators, for example also with single-acting actuators, hydraulic motors or gear arrangements.
  • FIG. 1 shows an actuator 1 designed as a hydraulically double-acting piston arrangement, which has a piston 5 movable in a cylinder 3, to which a piston rod 7 is attached. The col ben 5 and the piston rod 7 are inserted into the cylinder 3 so that two pressure chambers 9 and 11 are formed.
  • the first pressure chamber 9 is connected via a feed line 13 to a pump 15 to which a drive device 17 is assigned.
  • the first pump 15 is connected to a tank 25 via a supply line 23.
  • a valve 27 is provided parallel to the pump 15 and is connected on the one hand to the supply line 13 and on the other hand to the supply line 23.
  • the valve 27 is designed here as a non-return valve which is arranged such that the hydraulic medium in the tank 25 can be sucked in at a negative pressure in the feed line 13, even if the first pump 15 should not be driven.
  • a pressure relief valve 29, also referred to as a relief valve, is connected to the feed line 13 and is connected to the tank 25 via a return line 31.
  • the second pressure chamber 11 is assigned a supply system of identical construction: a second pump 15 'conveys a hydraulic medium from the tank 25 via a supply line 13'.
  • the second pump 15 ' is connected to the tank 25 via a supply line 23'.
  • a drive device 17 ' is assigned to the second pump 15'. It is possible to drive the two pumps 15 and 15 'via a single motor, for example an electric motor 19.
  • the drive comprises drive device 17 • a second electric motor 19 ', which drives the second pump 15' via a shaft 21 'indicated here.
  • a valve is again provided here, which is designed as a check valve 27' and is arranged in such a way that, in the event of a negative pressure in the supply line 13 ', hydraulic medium is sucked in from the tank 25 via the supply line 23' can be.
  • the feed line 13 ' is connected to the return line 31, which leads to the tank 25, via an overpressure valve 29'.
  • the hydraulic system assigned to the actuator 1 can be designed with a cooler 33, which is integrated here in the supply line 23 to the first pump 15. It is also possible to install this cooler 33 at any point in the hydraulic system. Finally, it is also conceivable to provide one or more of the supply lines with cooling fins in order to dissipate excess heat.
  • the drive for the actuator 1 shown in FIG. 1 also has a control 35, which is connected to the electric motors 19 and 19 'via control lines 37 and 37'.
  • the actuator 1 is assigned at least one sensor 39, the output signals of which are fed via a signal line 41 to an evaluation circuit 43 which, together with the control 35, forms a control circuit 45.
  • the evaluation circuit 43 can be supplied via a line 47 with at least one external signal, via which the drive for the actuator 1 can be influenced.
  • the sensor 39 which can include an analog / digital converter, is able to detect a wide variety of physical variables of the actuator 1, for example its position, the speed and / or acceleration of the piston 5 or the piston rod 7, the pressure given in the feed lines 13 and / or 13 and / or the forces exerted by the actuator 1. It is also conceivable that physical quantities of the actuator 1 are detected directly by sensors in the feed lines 13 and 13 'or in the control 35 and / or the evaluation circuit 43 or the electric motors 19 and 19'. One or more sensors, for example current or speed sensors, can also be integrated in the control 35 or the electromotors 19 and 19 '. As a result, the external sensor 39 can optionally be omitted and a modular construction of the drive can be implemented.
  • Figure 1 shows that a drive for an actuator 1 can be realized, which allows a two or four quadrant operation.
  • the control 35 is implemented as a control circuit or when, as shown in the figure, it is in the form of a control circuit, for example as a single-loop control circuit.
  • the control circuit can comprise continuous controllers, for example PID and / or state controllers with / without observer or discontinuous controllers. It can also be constructed in such a way that one or more of the physical quantities are regulated in parallel or sequentially.
  • controllers with integrating components are preferably used, that is to say controllers with I, PI or PID behavior.
  • the control circuit is by means of analog or digital technology or a combination of analog and digital technology.
  • the pumps 15 and 15 ' are designed as constant pumps, that is, they have a constant displacement volume. It is also conceivable to design one or both of the pumps as variable displacement pumps, it being possible to implement one or two displacement spaces. It is essential that a four-quadrant drive can also be implemented without installing any throttle valves in the feed lines 13 and 13 '.
  • the drive for the actuator 1 therefore works with particularly little loss. From the above it is also clear that the drive is very simple and therefore inexpensive to implement, because only pumps with a constant displacement volume are required for a four-quadrant drive, that is to say pumps which can be implemented relatively inexpensively. All that is required is a drive for the pumps that enables variable delivery rates. This is already possible with the aid of a single electric motor which has a variable speed and which is controlled via the control 35.
  • the drive for the actuator 1 can thus be further simplified compared to the illustration in the figure, although a four-quadrant drive can still be implemented.
  • the drive shown here also meets high safety requirements because, on the one hand, overpressure valves 29, 29 'and, on the other hand, valves 27, 27' designed as suction valves are provided.
  • the valves 27, 27 ', 29 and 29' have only a safety function and are used for the normal operation of the drive is not required, that is, they are inactive.
  • a particularly simple construction can be achieved in that the electric motors 19 and 19 'with the associated pumps 15 and 15' can be designed as one unit.
  • the delivery rate of the pumps is achieved by adapting the motor speed or the speed, which is possible with the control 35.
  • This can additionally be integrated into the unit consisting of motor and pump, so that a particularly compact construction results. Since the actuator is clamped between the two pumps 15 and 15 ', the rigidity is high.
  • the areas of the piston 5 which are subjected to the pressure prevailing in the pressure chambers 9 and 11 are of different sizes.
  • the area of the first pressure chamber 9 due to the piston rod 7, there is an annular area which is smaller than the cross-sectional area of the piston 5 which is acted upon by the pressure present in the second pressure chamber 11.
  • size ratios or area ratios of 2: 1 of the pressurized piston areas can result.
  • the delivery volumes of the pumps 15 and 15 * can be adapted to this area ratio. This in turn allows the electric motors 19 and 19 'to be operated at the same speed.
  • pumps with the same delivery volume can be used which are operated at different drive speeds.
  • the simple drive for the actuator can be designed for position and pressure control and / or for speed and pressure control.
  • the drive for the actuator can also be controlled, in addition to the speed-dependent regulation of the delivery rate by the electric motors 19 or 19', in that the displacement volume the pumps are changed. It can thus be seen that the drive for the actuator 1 can be changed in a variety of ways and can be adapted to different areas of use.
  • FIG. 2 shows a drive system 51 which consists of several, in the present case four actuators 1.1 to 1.4.
  • a drive system 51 is part of a machine which carries out various work movements in a completely or partially sequential sequence.
  • the actuators 1.1 to 1.3 are each a hydraulic double-acting piston cylinder, as has already been described in connection with FIG. 1. A repeated description is therefore omitted. Only the actuator 1.4 differs in that it is a hydraulic motor. Like the actuator 1 described in FIG. 1, each of the four actuators 1.1. to 1.4 are supplied with a hydraulic fluid via feed lines 13 and 13 *, which is conveyed from a tank 25 by a pump unit 53 surrounded by a dashed line. Corresponding to the exemplary embodiment according to FIG. 1, the pump unit 53 has two pumps 15, 15 'which are driven by the electric motor 19 or 19' with the shaft 21 or 21 '. The two supply lines 23, 23 'of the two pumps 15, 15' are connected to the tank 25.
  • the check valves 27, 27 'shown in FIG. 1 and the pressure relief valves 29, 29' are shown as a switching block 55 for the sake of clarity. However, the mode of operation corresponds to that of valves 27 and 29.
  • a regulation and control unit 57 is only shown as a function block.
  • the control unit 57 comprises a control circuit 45 for each actuator, which comprises a control 35 and an evaluation circuit 43.
  • the signal supplied by the sensor 39 is fed to the evaluation circuit 43 assigned to an actuator via the line 41.
  • the circuitry of the aforementioned components corresponds to that described with reference to FIG. 1, so that the precise mode of operation need not be discussed in more detail here.
  • FIG. 2 furthermore shows a valve arrangement 59 which enters the supply lines coming from the two pumps 15, 15 'and leading to the actuators. gen 13 is switched.
  • the valve arrangement has two hydraulic inputs 61.1 and 61.2, the first input 61.1 being connected to the pump 15 and the second input 61.2 being connected to the pump 15 '.
  • two outputs 63.1, 63.1 'to 63.4, 63.4' are also provided for each actuator 1.1 to 1.4.
  • the outputs 63.1 to 63.4 are each connected to the supply line 13 of an actuator 1.1 to 1.4, the outputs 63.1 'to 63.4' each to the supply line 13 'of an actuator.
  • the valve arrangement 59 has a plurality of, preferably four switching positions in the present exemplary embodiment, in which the inputs 61.1 and 61.2 are connected to predetermined outputs 63 with little loss.
  • the switching position of the valve arrangement 59 can be changed by the control unit 57, for example, via a control line 63.
  • the pump unit 53 is in the switching position II with the actuator 1.2, in the Switch position III connected to the actuator 1.3 and in a switch position IV to the hydraulic motor 1.4.
  • the actuators per switching position are also conceivable.
  • FIG. 3 shows an embodiment which essentially corresponds to the aforementioned exemplary embodiment according to FIG. 2. A repeated description of the parts marked with the same reference numerals is therefore omitted. The only difference is that the valve arrangement 59 permits a different assignment of the inputs 61.1 and 61.2 to the outputs 63.1 to 63.4.
  • the input 61.1 is connected to the output 63.2 and the input 61.2 is connected to the output 63.4.
  • the valve arrangement 59 has an outlet 65 which leads to the tank 25 via a line 67.
  • This output 65 is connected on the one hand to the output 63.2 'and on the other hand to the output 63.4'.
  • valve arrangement 59 can be designed such that a switching position is provided for each desired operating combination of two actuators.
  • FIG. 4 A further exemplary embodiment is shown in FIG. 4, the basic structure of which corresponds to the exemplary embodiment shown in FIG. A repeated description of the parts identified by the same reference numerals is therefore omitted.
  • a further operating mode is made possible in the present exemplary embodiment with the aid of the valve arrangement 59.
  • the two pumps 15, 15 ' can be connected in parallel in order to supply an actuator 1.
  • FIG. 4 shows that the inputs 61.1 and 61.2 are connected to the output 63.3 in the switching position of the valve arrangement 59 shown, while the output 63.3 * is connected to the output 65.
  • Both pumps 15, 15 'thus convey hydraulic fluid via the feed line 13 into the actuator 1.3 for its actuation.
  • actuators 1.1, 1.2 and 1.4 can then be connected to the two pumps 15, 15 '.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un système d'entraînement comportant au moins deux actuateurs hydrauliques alimentés en milieu hydraulique à l'aide d'au moins une pompe. Ce système d'entraînement comprend au moins une autre pompe (15') parallèle à la première (15), la régulation de la vitesse de rotation des pompes étant bidirectionnelle, et un ensemble soupape (59) est relié à une admission (61.1, 61.2) par pompe, chacune des admissions étant reliée à une pompe (15), et à un certain nombre de sorties (63.1, 63.1', ... 63.4, 63.4') qui sont reliées aux actuateurs (1.1 ... 1.4). Lesdites admissions (61) sont reliées aux sorties d'une manière prédéterminée.
EP96944055A 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour plusieurs actuateurs hydrauliques Expired - Lifetime EP0873475B1 (fr)

Priority Applications (1)

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

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19600650 1996-01-10
DE19600650A DE19600650C2 (de) 1996-01-10 1996-01-10 Antrieb für einen hydraulischen doppelwirkenden Aktuator
DE19642163A DE19642163A1 (de) 1996-01-10 1996-10-12 Verlustarmer Antrieb für mehrere hydraulische Aktuatoren
DE19642163 1996-10-12
PCT/EP1996/005801 WO1997025532A1 (fr) 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour plusieurs actuateurs hydrauliques

Related Child Applications (1)

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

Publications (2)

Publication Number Publication Date
EP0873475A1 true EP0873475A1 (fr) 1998-10-28
EP0873475B1 EP0873475B1 (fr) 2003-10-15

Family

ID=26021974

Family Applications (1)

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

Country Status (6)

Country Link
US (1) US6205780B1 (fr)
EP (1) EP0873475B1 (fr)
AU (1) AU1377997A (fr)
DE (1) DE59611324D1 (fr)
TW (1) TW401486B (fr)
WO (1) WO1997025532A1 (fr)

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US20090090102A1 (en) * 2006-05-03 2009-04-09 Wilfred Busse Method of reducing the load of one or more engines in a large hydraulic excavator
GB0614534D0 (en) * 2006-07-21 2006-08-30 Artemis Intelligent Power Ltd Fluid power distribution and control system
DK1911979T3 (da) 2006-10-11 2011-10-10 Studio Tecnico 6M Srl Dynamisk fluidanordning
US8206134B2 (en) * 2008-06-02 2012-06-26 Maradyne Corporation Combined power pack unit
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
CN102459919A (zh) * 2009-04-08 2012-05-16 派克汉尼芬公司 多泵液压回路
US20110056192A1 (en) * 2009-09-10 2011-03-10 Robert Weber Technique for controlling pumps in a hydraulic system
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US9032724B2 (en) * 2010-06-21 2015-05-19 Husco International Inc. Command based method for allocating fluid flow from a plurality of pumps to multiple hydraulic functions
DE102010034187A1 (de) * 2010-08-12 2012-02-16 Lukas Hydraulik Gmbh Steuereinrichtung für erstes und zweites Arbeitsgerät
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WO1997025532A1 (fr) 1997-07-17
DE59611324D1 (de) 2006-04-06
TW401486B (en) 2000-08-11
AU1377997A (en) 1997-08-01
EP0873475B1 (fr) 2003-10-15
US6205780B1 (en) 2001-03-27

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