EP0778419B1 - Hydraulische Ventilanordnung mit einem druckgesteuerten Wegeventil - Google Patents
Hydraulische Ventilanordnung mit einem druckgesteuerten Wegeventil Download PDFInfo
- Publication number
- EP0778419B1 EP0778419B1 EP96118169A EP96118169A EP0778419B1 EP 0778419 B1 EP0778419 B1 EP 0778419B1 EP 96118169 A EP96118169 A EP 96118169A EP 96118169 A EP96118169 A EP 96118169A EP 0778419 B1 EP0778419 B1 EP 0778419B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- pump
- control
- acting cylinder
- 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.)
- Expired - Lifetime
Links
- 238000006073 displacement reaction Methods 0.000 claims description 12
- 239000012530 fluid Substances 0.000 claims description 10
- 238000000034 method Methods 0.000 description 9
- 230000005611 electricity Effects 0.000 description 2
- 239000002245 particle Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
Definitions
- the invention relates to a hydraulic valve arrangement a pressure-controlled directional valve with two working connections and a control connection for controlling the pressure medium flow.
- the invention has for its object a valve assembly to create the type mentioned in the switching operations do not lead to pressure fluctuations in the system.
- the pressure medium that occurs when the 2-way cartridge valve is opened from the control room of the 2-way cartridge valve is displaced is not discharged into the tank but remains in the system. That is, from the control room displaced pressure medium is together with the pressure medium that flowed through the 2-way cartridge valve, according to the Flow direction of the pressure medium to the consumer or the pump fed. Since the amount of pressure medium in the system remains constant, there is no pressure drop when switching the 2-way cartridge valve. Both when opening and when closing a smooth transition without delay. The direction of the river of the pressure medium is due to the working position of two pilot valves certainly.
- the valve arrangement acts in each flow direction like a check valve.
- valve arrangement is due their function as a check valve when open for the control of safety-relevant hydraulic devices, where a single-acting cylinder from a pump is supplied with pressure medium, such as. B. hydraulic lifts, can be used advantageously. If the pressure medium supply fails the load closes when the load is lifted Valve arrangement automatically and prevents the Load. By controlling the unit of time from the pump pumped amount of pressure medium, the piston speed of the single-acting cylinder. For this a Variable displacement pump or one from a speed-controlled motor driven inexpensive constant pump serve. Using an electric motor, energy recovery is possible if when lowering the load, the pump as a hydraulic motor and the electric motor operated as a generator.
- a robust drive for the pump is obtained when using a frequency-controlled Electric motor.
- the use of only one flowing back to the tank Filter through which pressure medium flows removes dirt particles, those at the sealing points between the piston and cylinder got into the pressure medium. Because only pressure medium to the tank that has previously passed through the filter needs this from pressure medium flowing to the cylinder to the cylinder is not filtered become.
- FIG. 1 shows a schematic representation of a hydraulic device for controlling the pressure medium flow between a variable displacement pump 2 driven by an electric motor 1 and a single-acting cylinder 3, the piston 4 of which is loaded with the car 5 of an elevator.
- the variable displacement pump 2 delivers pressure medium from a tank 6 via a line 7, a valve arrangement 8, a line 9, a filter device 10, a shut-off valve 11 and a pipe rupture protection device 12 to the cylinder 3.
- the pump pressure (pressure in line 7) is p P denotes
- the load pressure (pressure in line 9) is denoted by p L.
- a pressure limiting valve 13 limits the pressure p P to a value which is greater than the greatest operational pressure in the line 7.
- the filter device 10 connected downstream of the valve arrangement 8 has a filter 16 and two check valves 17 and 18.
- the check valves 17 and 18 are arranged so that the Pressure medium only flow over the filter 16 in one direction can, although the pressure medium in both directions over the Filter device 10 flows.
- the flow direction of the over the Filter 16 flowing pressure medium is chosen so that the pressure medium flowing back from the cylinder 3 to the tank 6 is filtered. This ensures that dirt particles, the z. B. at the sealing points between the piston 4 and the Cylinder 3 have entered the pressure medium, are removed. There only pressure medium that has previously passed the filter 16 to the tank 6 flows back, that needs from the tank 6 to the cylinder 3 flowing pressure medium can no longer be filtered separately.
- the shut-off valve 11 and the pipe rupture protection 12 are at hydraulic lifts required for safety reasons.
- the Shut-off valve 11 is during normal operation of the elevator always open. It is e.g. B. during maintenance work on the The elevator system is closed.
- the pipe rupture protection 12 is during the normal operation of the elevator is also constantly open. Only when the amount of cylinder 3 in the time unit draining pressure medium is much larger than the largest operationally draining pressure medium quantity, interrupts the Pipe rupture protection prevents the pressure medium flow and thus prevents that the car goes down at an impermissibly high speed moves.
- the pipe rupture protection device 12 is as close as possible to that Cylinder 3 arranged. The construction of such pipe burst safety devices your specialist is familiar. The pipe rupture protection device 12 is therefore not shown in detail in FIG. 1.
- the valve arrangement 8 contains a pressure-controlled directional valve 19, two pilot valves 20 and 21, two check valves 22 and 23 and two throttles 24 and 25.
- the directional control valve 19 has two Working ports A and B and a control port X.
- Das Directional control valve 19 has a control piston 26, of both Forces are applied to the sides.
- On the footprint of the Control piston 26 acts at the working port A Print.
- the area surrounding the base acts from the same side Annular surface of the pressure present at the working connection B.
- the control surface acts from the opposite side pressure present at the control connection X together with the force a spring 27.
- the control surface is equal to the sum of the Base area and the surrounding ring area.
- the control piston 26 blocks the connection between the work connections A and B if the from the pilot pressure side on the spool 26 acting forces predominate, and opens the connection between the work ports A and B if the from the side of the working connections prevail.
- Directional control valve 19 is a seat valve, i. H. at When the valve is closed, the pressure medium flow is interrupted without leakage.
- the pilot valves 20 and 21 are designed as seat valves electrically controlled switching valves. You lock in their rest position also leak-free.
- the pilot valve 20 bridges the throttle 24 and that in its working position Check valve 22.
- the pilot valve 21 bridges in its Working position, the throttle 25 and the check valve 23.
- the magnets of the pilot valves 20 and 21 are connected to the switching outputs of the electrical control device 15 via lines 28 and 29, respectively.
- the lines 28 and 29 are shown interrupted.
- a first pressure transducer 30 converts the pressure p P into a proportional voltage u P.
- a second pressure transducer 29 converts the pressure p L into a proportional voltage u L.
- the voltages u P and u L are supplied to the electrical control device 15 as input signals.
- An electrical switch 32 with three positions is connected via lines 33 and 34 to two switching inputs of the control device 15. In one switch position, the switch 32 connects the line 33 to a supply voltage U. This switch position is assigned to the lifting of the car 5. In the second switch position, the switch 32 connects the line 33 to the supply voltage U. This switch position is assigned to the lowering of the car 5. In the middle switch position, neither line 33 nor line 34 is connected to supply voltage U. The car 5 stops in this switch position.
- valve assembly 8 The function of the valve assembly 8 is based on the following Figures 2 to 4 described. Only those for Pressurizing the control connection X effective components the valve assembly 8 shown.
- FIG. 2 shows the pressurization of the control piston 26 of the directional control valve 19 when the pilot valves 20 and 21 are in the rest position.
- the pilot valves 20 and 21 are not effective in their rest position. They are therefore not shown in FIG. 2.
- the pump pressure p P acts via the working connection A and the load pressure p L via the working connection B.
- the pressure at the control connection X acts together with the spring 27.
- the spring 27 is designed so that its force in relation to the control surface of the control piston 26 is of the order of one twentieth of that due to the weight and load of the car 5 and corresponds to certain load pressure p L due to the design of the cylinder 3.
- the check valves 22 and 23 act like a shuttle valve.
- the force exerted on the control piston 26 by the load pressure p L via the control connection X is already greater (without taking into account the influence of the spring 27) than the forces exerted by the pump pressure p P and the load pressure p L at the working ports A and B from the opposite side on the control piston 26, the directional control valve 19 is closed. If the pilot valves 20 and 21 are in the rest position, the directional control valve 19 is closed - regardless of whether the pump pressure p P is greater than the load pressure p L or whether the load pressure p L is greater than the pump pressure p P.
- FIG. 3 shows the pressurization of the control piston 26 of the directional control valve 19 when the pilot valve 20 is in the working position and the pilot valve 21 in the rest position.
- the pilot valve 20 bridges the check valve 22 and the throttle 24. Since the check valve 22 and the throttle 24 are not effective, they are not shown in FIG. 3.
- the pilot valve 21 is not effective in its rest position. It is therefore also not shown in FIG. 3.
- the pump pressure p P acts via the working connection A and the load pressure p L via the working connection B.
- the pressure at the control port X acts together with the spring 27.
- the pressure at the control port X is equal to the pressure at the working port B, that is to say your load pressure p L. If the pump pressure p P is less than the load pressure p L , the check valve 23 is closed. The force exerted by the load pressure p L via the control connection X on the control piston 26 (even without taking into account the influence of the spring 27) is greater than that of the pump pressure p P and your load pressure p L at the working connections A and B by the opposite Exerted forces on the control piston 26, the directional control valve 19 is closed. When the pump pressure p P increases to a value which is greater than the load pressure p L , the check valve 23 opens.
- Pressure line flows from line 7 via throttle 25, check valve 23 and pilot valve 20 to line 9.
- the amount of Pressure medium flowing through the throttle 25 is determined by the size of the throttle 25 and the difference between the pump pressure p P and the load pressure p L.
- the load pressure P L is determined by the weight and load of the car 5 and by the design of the cylinder 3.
- the directional control valve 19 is still closed, pressure medium is already flowing via the throttle 25 to the cylinder 3.
- the pump pressure p P increases to such an extent that the forces acting on the control piston 26 from the side of the working ports A and B are from the opposite side prevail acting forces, the directional control valve 19 opens the connection between the working port A and the working port B.
- the pressure medium delivered by the variable displacement pump 2 now flows via the line 7, the working connections A and B of the directional control valve 19 and the line 9 to the cylinder 3 and lifts the car 5.
- the speed of the car 5 is determined by the amount of pressure medium flowing in the time unit. If the pressure in line 7 drops below the pressure in line 9, e.g. B. because of a break in the line 7 between the variable displacement pump 2 and the valve arrangement 8 or because the pump pressure p P has been reduced by the adjusting device 14 or because the variable displacement pump 2 has been switched off, the forces acting on the control surface of the control piston 26 predominate and that Directional control valve 19 interrupts the flow of the pressure medium.
- the valve arrangement 8 since the check valve 23 also closes when the pressure in the line 9 is greater than the pressure in the line 7, the valve arrangement 8, when the pilot valve 20 is actuated, behaves like a check valve which only has a flow of the pressure medium from the line 7 to the line 9 allowed.
- FIG. 4 shows the pressurization of the control piston 26 of the directional control valve 19 when the pilot valve 21 is in the working position and the pilot valve 20 in the rest position.
- the pilot valve 21 bridges the check valve 23 and the throttle 25 in its working position. Since the check valve 23 and the throttle 25 are not effective, they are not shown in FIG.
- the pilot valve 20 is not effective in its rest position. It is therefore also not shown in FIG. 4.
- the pump pressure p P acts via the working connection A and the load pressure p L via the working connection B.
- the pressure at the control port X acts together with the spring 27.
- the pressure at the control port X is equal to the pressure at the working port A, that is to say the pump pressure p P. If the pump pressure p P is greater than the load pressure p L , the check valve 22 is closed. The force exerted by the pump pressure p P via the control connection X on the control piston 26 (even without taking into account the influence of the spring 27) is greater than that of the pump pressure p P and the load pressure p L at the working connections A and B by the opposite one Exerted forces on the control piston 26, the directional control valve 19 is closed. If the pump pressure p P is now reduced to a value which is lower than the load pressure p L , the check valve 22 opens.
- Pressure line flows from line 9 via throttle 24, check valve 22 and pilot valve 21 to line 7.
- the amount of Pressure medium flowing via the throttle 24 is determined by the size of the throttle 24 and the difference between the load pressure p L and the pump pressure p P.
- the load pressure p L is determined by the weight and load of the car 5 and by the design of the cylinder 3. If the pump pressure p P is further reduced, the forces acting from the side of the working connections A and B on the control piston 26 outweigh the forces acting from the opposite side, and the directional control valve 19 opens the connection between the working connection B and the working connection A.
- the pressure medium displaced by the weight and load of the car 5 from the cylinder 3 flows through the filter 16, the line 9, the working connections B and A of the directional control valve 19, the line 7 and the variable pump 2 to the tank 6 and the car 5 sinks .
- the variable displacement pump 2 acts as a hydraulic motor and drives the electric motor 1, which in turn acts as a generator and feeds electricity back into the network.
- the speed of the car 5 is determined by the amount of pressure medium flowing in the time unit. If the pump pressure p P increases , e.g. B. due to a malfunction of the variable displacement pump 2 via the load pressure p L , the forces acting on the control surface of the control piston 26 predominate and the directional control valve 19 interrupts the flow of the pressure medium. Since the check valve 22 also blocks when the pump pressure p P is greater than the load pressure p L , the valve arrangement 8, when the pilot valve 21 is actuated, behaves like a check valve which only allows the pressure medium to flow from line 9 to line 7.
- the valve arrangement 8 locks in both Directions when both pilot valves 20 and 21 are at rest are located. While the valve assembly from line 9 to line 7 blocks leakage-free, can with closed valve arrangement 8 from line 7 via the throttle 25 and the check valve 23 a leakage current from the control terminal X to Work port B flow, the size u. a. from the constructive Design of the directional valve 19 depends. Like the figures 3 and 4 show, the valve arrangement 8 behaves like a check valve, whose direction of flow depends on which of the Pilot valves 20 or 21 are in the working position. In addition to the important function from a security point of view as Check valve has the valve assembly 8 for both Lifting process and for the lowering process a gentle opening behavior on the occurrence of pressure vibrations by the Switching of the directional valve 19 prevented.
- the shown in the Figure 1 electrical control device 15 controls the movement of the car 5.
- the control means 15 are for this purpose by the transmitter 30, the pump pressure P P proportional voltage u P and the load pressure of the transducer 31 p L proportional voltage u L as input signals fed.
- the switch 32 supplies the control device 15 with the supply voltage U via the lines 33 and 34, depending on whether the car 5 is to be raised or lowered.
- the control device 15 controls the adjusting device 14 of the variable pump 2 and the magnets of the pilot valves 20 and 21 of the valve arrangement 8.
- the middle position of the switch 32 is assigned to the holding process.
- the solenoids of the pilot valves 20 and 21 are not activated. Since the valve assembly 8 locks as described above, no pump pressure is required to hold the car 5 in place.
- the adjusting device 14 is therefore controlled by the control device 15 so that it adjusts the variable pump 2 so that the pump pressure p P has only a minimal value.
- the control device 15 controls the magnet of the pilot valve 20.
- the valve arrangement 8 behaves like a check valve which only allows a pressure medium flow from the variable displacement pump 2 to the cylinder 3.
- the adjusting device 14 is controlled by the control device 15 in such a way that it adjusts the volume flow of the adjusting pump 2 in such a way that the pump pressure p P assumes a value which is at least larger than the load pressure p L by the amount required for opening the valve arrangement 8.
- the pilot valve 20 is first activated and then the volume flow to the valve arrangement 8 is increased via the variable pump 2.
- the car stops if the pressure supply fails due to a fault. A sinking of the car is effectively prevented by the function of the valve arrangement 8 as a check valve.
- the control device 15 controls the magnet of the pilot valve 21.
- the valve arrangement 8 behaves like a check valve which only allows a pressure medium flow from the cylinder 3 to the variable displacement pump 2.
- the adjusting device 14 is controlled by the control device 15 so that the pump pressure p P is equal to the load pressure p L.
- the pilot valve 21 is then actuated. Now the pump swivels to the minus and pumps oil into the tank 6 in accordance with the setpoint program of the control device 15. Since the direction of the volume flow reverses due to the load, the variable pump 2 works as a hydraulic motor and drives the electric motor 1. This now works as a generator and feeds electricity back into the electrical network.
- a constant pump driven by a speed-controlled electric motor in particular a frequency-controlled electric motor
- the control device for the speed of the electric motor is connected to the output of the control device 15. It is also possible to drive the constant pump at a constant speed and to control the pump pressure p P via a pressure limiting valve with an adjustable limiting pressure.
- valve arrangement according to the invention is not limited to the control of hydraulic elevators. she is in same way for the control of other safety-relevant hydraulic consumers, such as B. the forklift hoists or tractors.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Forklifts And Lifting Vehicles (AREA)
Description
- Figur 1
- eine schematische Darstellung einer hydraulischen Einrichtung zur Steuerung des Druckmittelflusses zwischen einer Pumpe und einem einfachwirkenden Zylinder,
- Figur 2
- die in der Figur 1 dargestellte Ventilanordnung reduziert auf die in der Ruhestellung der Pilotventile wirksamen Bauteile,
- Figur 3
- die in der Figur 1 dargestellte Ventilanordnung reduziert auf die beim Hebevorgang wirksamen Bauteile und
- Figur 4
- die in der Figur 1 dargestellte Ventilanordnung reduziert auf die beim Senkvorgang wirksamen Bauteile.
Claims (8)
- Hydraulische Ventilanordnung mit einem druckgesteuerten Wegeventil mit zwei Arbeitsanschlüssen und einem Steueranschluß zur Steuerung des Druckmittelflusses, dadurch gekennzeichnet,daß der an dem ersten Arbeitsanschluß (A) anstehende Druck (pP) über eine erste Drossel (25) und ein erstes Rückschlagventil (23) dem Steueranschluß (X) zugeführt ist,daß zwischen dem ersten Arbeitsanschluß (A) und dem Steueranschluß (X) ein erstes Schaltventil (21) angeordnet ist, das in seiner Arbeitsstellung die Hintereinanderschaltung der ersten Drossel (25) und des ersten Rückschlagventils (23) überbrückt,daß der an dem zweiten Arbeitsanschluß (B) anstehende Druck (pL) über eine zweite Drossel (24) und ein zweites Rückschlagventil (22) dem Steueranschluß (X) zugeführt ist unddaß zwischen dem zweiten Arbeitsanschluß (B) und dem Steueranschluß (X) ein zweites Schaltventil (20) angeordnet ist, das in seiner Arbeitsstellung die Hintereinanderschaltung der zweiten Drossel (24) und des zweiten Rückschlagventils (22) überbrückt.
- Verwendung einer Ventilanordnung nach Anspruch 1 in einer Einrichtung zur Steuerung des Druckmittelflusses zu bzw. von einem ständig mit einer Last (5) beaufschlagten einfachwirkenden Zylinder (3) mit einer von einem Motor (1) angetriebenen Pumpe (2), die Druckmittel aus einem Tank (6) zu dem einfachwirkenden Zylinder (3) fördert, wobei Pumpe (2), Ventilanordnung (8) und einfachwirkender Zylinder (3) ein geschlossenes System bilden, insbesondere für die Steuerung hydraulischer Aufzüge.
- Einrichtung zur Steuerung des Druckmittelflusses zu bzw. von einem ständig mit einer Last (5) beaufschlagten einfachwirkenden Zylinder (3) mit einer von einem Motor (1) angetriebenen Pumpe (2), die Druckmittel aus einem Tank (6) zu dem einfachwirkenden Zylinder (3) fördert und mit einer hydraulischer Ventilanordnung nach Anspruch 1, wobei Pumpe (2), Ventilanordnung (8) und einfachwirkender Zylinder (3) ein geschlossenes System bilden, dadurch gekennzeichnet, daß die über die Ventilanordnung (8) fließende Druckmittelmenge nach Betrag und Richtung einstellbar ist.
- Einrichtung nach Anspruch 3, dadurch gekennzeichnet, daß die in der Zeiteinheit von der Pumpe (2) geförderte Druckmittelmenge einstellbar ist.
- Einrichtung nach Anspruch 4, dadurch gekennzeichnet, daß die Pumpe eine volumenstromgeregelte Pumpe ist.
- Einrichtung nach Anspruch 4, dadurch gekennzeichnet, daß die Pumpe eine von einem drehzahlgeregelten Motor angetriebene Konstantpumpe ist.
- Einrichtung nach Anspruch 6, dadurch gekennzeichnet, daß der Motor ein frequenzgeregelter Elektromotor ist.
- Einrichtung nach einem der Ansprüche 3 bis 7, dadurch gekennzeichnet,daß zwischen der Ventilanordnung (8) und dem einfachwirkenden Zylinder (3) eine Filtereinrichtung (10) angeordnet ist,daß die Filtereinrichtung (10) einen Filter (16) für das von dem einfachwirkenden Zylinder (3) zum Tank (6) zurückfließenden Druckmittel aufweist unddaß das zu dem einfachwirkenden Zylinder (3) fließende Druckmittel an dem Filter (16) vorbeigeführt ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19545657A DE19545657A1 (de) | 1995-12-07 | 1995-12-07 | Hydraulische Ventilanordnung mit einem druckgesteuerten Wegeventil |
DE19545657 | 1995-12-07 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0778419A2 EP0778419A2 (de) | 1997-06-11 |
EP0778419A3 EP0778419A3 (de) | 1998-06-03 |
EP0778419B1 true EP0778419B1 (de) | 2001-01-24 |
Family
ID=7779444
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96118169A Expired - Lifetime EP0778419B1 (de) | 1995-12-07 | 1996-11-13 | Hydraulische Ventilanordnung mit einem druckgesteuerten Wegeventil |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0778419B1 (de) |
DE (2) | DE19545657A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE602006006676D1 (de) * | 2006-09-01 | 2009-06-18 | Parker Hannifin Ab | Ventilanordnung |
CN113510176B (zh) * | 2020-04-10 | 2024-01-19 | 初冠南 | 一种充压镦形成形装置 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE7512442U (de) * | Danfoss A/S, Nordborg (Daenemark) | |||
DE1775178A1 (de) * | 1968-07-13 | 1971-07-08 | Rexroth Gmbh G L | Vorgesteuertes Druckbegrenzungsventil |
US4401009A (en) * | 1972-11-08 | 1983-08-30 | Control Concepts, Inc. | Closed center programmed valve system with load sense |
JPH0246801B2 (ja) * | 1981-06-29 | 1990-10-17 | Uchida Yuatsu Kiki Kogyo Kk | Shokoshirindanoseigyokairosochi |
DE3521815A1 (de) * | 1985-06-19 | 1987-01-02 | Bosch Gmbh Robert | Steuereinrichtung fuer hydraulische arbeitsmaschinen |
IT1248792B (it) * | 1991-05-20 | 1995-01-30 | Gmv Martini Spa | Circuito idraulico per ascensori, montacarichi e simili, con sicurezza intrinseca |
DE4309901B4 (de) * | 1992-11-10 | 2010-07-01 | Zf Sachs Ag | Hydraulischer Stellantrieb - inbesondere für eine Kraftfahrzeug-Reibungskupplung |
DE4334607A1 (de) * | 1993-10-11 | 1995-04-13 | Rexroth Mannesmann Gmbh | 2-Wege-Einbauventil mit Druckbegrenzungsfunktion |
US5535588A (en) * | 1994-05-06 | 1996-07-16 | Dana Corporation | Filter arrangement for single-acting telescopic hydraulic cylinders |
-
1995
- 1995-12-07 DE DE19545657A patent/DE19545657A1/de not_active Withdrawn
-
1996
- 1996-11-13 EP EP96118169A patent/EP0778419B1/de not_active Expired - Lifetime
- 1996-11-13 DE DE59606377T patent/DE59606377D1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
DE19545657A1 (de) | 1997-06-12 |
EP0778419A2 (de) | 1997-06-11 |
DE59606377D1 (de) | 2001-03-01 |
EP0778419A3 (de) | 1998-06-03 |
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Legal Events
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