EP1023508B1 - System zur lastdruckunabhängigen steuerung und lasthaltung mehrerer rotatorischer und/oder translatorischer verbraucher - Google Patents
System zur lastdruckunabhängigen steuerung und lasthaltung mehrerer rotatorischer und/oder translatorischer verbraucher Download PDFInfo
- Publication number
- EP1023508B1 EP1023508B1 EP98961094A EP98961094A EP1023508B1 EP 1023508 B1 EP1023508 B1 EP 1023508B1 EP 98961094 A EP98961094 A EP 98961094A EP 98961094 A EP98961094 A EP 98961094A EP 1023508 B1 EP1023508 B1 EP 1023508B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- load
- pressure
- throttle
- valve
- pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2271—Actuators and supports therefor and protection therefor
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
-
- 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
- F15B11/003—Systems with load-holding valves
-
- 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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
-
- 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
-
- 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
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
Definitions
- the invention relates to a system for load pressure independent Control and load maintenance of several rectifier and / or translational consumer of an eau and / or work machine with at least one regulated pump as well at least one containing a spring-loaded control piston Secondary pressure balance.
- DE 34 43 354 A1 describes a hydraulic system, the one driven, for example, by a diesel engine Pump has, the pressure medium via directional valves To consumers.
- the speed controller of the injection pump of the diesel engine is pressurized with the help Actuating cylinder affected by the purpose Speed increase of the engine generated pressure in acts on a control line.
- This pressure will work together one of the way valves for a single acting Consumer and a pressure control valve controlled so that when operating a conventional directional valve a constant pressure is generated in the line.
- the Actuation of the other directional valve for the single-acting Consumers have a special control edge Effect, making a proportional to the deflection of the Control spool generates increasing pressure in the line becomes.
- the speed of the internal combustion engine and thus the pump increased and adjusted so that the Consumers just receive the required amount of pressure medium. This is an economical operation possible.
- LSC Linde Synchro Control
- the system works on the load-sensing principle. It significantly improves simultaneous operation various functions of hydraulic systems with open circuit.
- the Linde Synchro Control (LSC) valves are individual valve sections. The right combination for different machines is achieved in that the individual sections are mounted on corresponding valve plates. These valve plates only contain the connection channels, such as. the input channel from the pump, Connection channels to and from the valves, the return line and the connection of the return to the tank. In the Valve sections are the actual functional elements accommodated.
- the valves themselves are piston-type have a spring-centered closed center position and are operated hydraulically.
- the maximum Piston stroke is adjustable, and since the pressure drop at the Control edges is kept constant, this means that the maximum oil flow that should flow through the valve, can be limited at the end stops of the valve.
- a pressure compensator is arranged inside the valve piston.
- the shuttle valves for the LS signal are located inside the pressure compensators and move in with them the valve piston.
- a generic control system for load pressure independent Control of several consumers of a mobile hydraulic Construction machine is known from EP 0 326 150 A1.
- This Control system has a spring-loaded control piston containing pressure compensator.
- the object of the invention is that in the current systems realized functional separation between the Signal generation, load holding and pressure compensation functions by reducing external individual components to optimize to an inexpensive, assembly-friendly and bring about construction that is not susceptible to faults.
- Such systems are used for load-independent systems Control and regulation of consumer speeds for mobile construction and work machines, such as. Excavators, wheel bearings, graders and the like at least two consumers, e.g. Hydraulic cylinder, one unaffected by the load pressures impressed from the outside Work movement without mutual interference must have.
- the lower housing part Is part of the control valve.
- a secondary pressure compensator is used related to the load holding function, in the opposite of the Function with conventional load compensators with separate Load holding function the signal carrying the load pressure in the consumer-side channels not for forwarding to the pressure regulator of the feed pump, as it hereby arranged without additional in the consumer channels Load holding valves to an unwanted drop the load due to the leakage of the feed pump pressure regulator or the pressure relief valve of the load sensing line comes.
- this is avoided by that to the pressure regulator of the feed pump and the compensators of consumers with lower loads a pressure signal is reported by the pump self-generated and maintained and in his Pressure level corresponds to the highest consumer pressure.
- FIG. 1 is the schematic structure of an inventive Control system using the example of a consumer shown.
- the secondary pressure compensator with load holding function is divided into two components, namely an upper housing part 78 and a lower housing part 86.
- the lower Housing part 86 is preferably part of the Control valves 7, 8, 9, i.e. forms a unified with this Casing.
- Figure 2 shows an example for two translational consumers 16, 17 (hydraulic cylinder) schematically the structure of the tax system.
- the system accordingly has two Secondary pressure compensators, the housing of each in two Housing parts 78, 79 and 86, 87 are divided, i.e. the Formation of the second secondary pressure compensator corresponds to that the secondary pressure compensator 78 shown in FIG. 1, 86th
- a pump 1 generates a pressure level in the system that by a preselectable control difference ⁇ p LS above the input pressure signal of the pressure regulator 2 of the pump 1 lies. This pressure level is present when the inlet throttle 7 is open under the piston crown 37 of the first secondary pressure compensator 78, 86.
- the inlet pressure level of the pressure regulator 2 in the line 20 drops via a load-sensing bypass valve 3 to the tank pressure level p r .
- the outlet throttle 9 is opened.
- the consumption-side pressure signal p L1 is present in the outlet channel 22 of the secondary pressure compensator 78, 86 and propagates through the channel 29, a shuttle valve 32, a channel 31 and a damping nozzle 30 to the spring-loaded piston head 27 of the secondary pressure compensator 78, 86.
- the consumer-side pressure signal p L1 which acts on the spring-loaded piston head 27 of the secondary pressure compensator 78, 86, keeps the two-part control piston 72, 73 on its valve set 36, as a result of which no leakage flow can escape from the pressure-carrying consumer-side channel 22 into the inlet channel 33.
- the inlet throttle 7 also opens with a corresponding phase shift, as a result of which the pump pressure p P , which is initially at the level of the control pressure difference ⁇ p LS , builds up on the active surface of the piston head 37.
- the seat valve seats 36, 53 of the piston heads and the piston heads 27, 44 of the two-part control pistons of the secondary pressure compensators 78, 86 and 79, 87 are surface-balanced.
- the pressure signal limited to the consumer load pressure p L1 is forwarded to the pressure regulator 2 of the pump 1 via the pump pressure-carrying channel 24, the inlet nozzle 21, the check valve 34 and the channels 25, 4 and 20.
- the pump 1 supplies an output pressure p p which has the preselected control difference ⁇ p LS compared to the pressure input signal in line 20.
- a further check valve 23 opens and thus ensures that the pressure signal in the channel 35 corresponds to the value of the consumer pressure p does not exceed L1 . This ensures that the pressure signal generated by the pump 1 and passed on to the pressure regulator 2 of the pump 1 and the secondary pressure compensator 79, 87 is limited by the level of the respective load pressure.
- the valve seat 36 of the two-part control piston 72, 73 of the secondary pressure compensator 78, 86 opens due to the excess pressure on the piston crown surface 37, whereby a volume flow Q V1 flows through the inlet throttle 7, the opened valve seat 36 and an outlet throttle 9 to the consumer 16.
- the resulting volume flow Q V1 is determined by the variable opening cross-section A D1 of the inlet throttle 7 and the differential pressure ⁇ p LS - p F1 that drops as a result according to the following equation:
- Q V1 K ° A D1 ° ⁇ ⁇ p LS - p F1 ,
- the pump pressure signal present in the channel 35 and limited to the consumer pressure level p L1 is forwarded to the second secondary pressure compensator 79, 87 via the check valve 34, the channel 25 and the lines 4, 5.
- the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87 and is effective via the channel 42, the shuttle valve 49 and the channel 48 and the damping nozzle 47 on the active surface 44 of the two-part control piston head 74, 75 is and thus holds the valve seat 53 of the two-part control piston 74, 75 securely closed.
- the outlet throttle 12 is first opened, as a result of which the load pressure p L2 through the channel 46 on the shuttle valve 49 becomes effective.
- the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87, which becomes active via the channel 42, the shuttle valve 49, the channel 48 and the damping nozzle 47 on the active surface of the control piston head 44 and thus the Valve seat 53 of the two-part control piston 74, 75 holds securely closed.
- the load pressure signal p L1 is present in the pressure signaling line 5 of the secondary pressure compensator 79, 87, which becomes active via the channel 42, the shuttle valve 49 and the channel 48 on the active surface of the control piston head 44 and thus the valve seat 53 of the two-part Control piston 74, 75 holds securely closed.
- the outlet throttle 12 is first opened, as a result of which the load pressure p L2 takes effect via the channel 46 in the lower chamber of the shuttle valve 49. Since it is presupposed that p L1 ⁇ p L2 , the load pressure p L2 prevails in the lower chamber of the shuttle valve 49 and acts via the channel 48 and the damping nozzle 47 on the head 44 of the two-part control piston 74, 75.
- the inlet throttle 10 is opened with the cross section A D2 .
- the pressure potential p L1 + ⁇ p LS offered by the pump 1 becomes effective under the piston crown 54 of the two-part control piston 74, 75 of the pressure compensator 79, 87. Since the sum of the current load pressure p L2 and equivalent pressure p F2 of the spring acting on the piston head 44 is greater than the pressure signal p L1 + ⁇ p LS which acts on the piston head 54 from the pump 1, the valve seat 53 of the two-part control piston 74, 75 remains initially closed.
- the pump pressure signal p L1 + ⁇ p LS is forwarded via the nozzle 38, the check valve 51 and the load signal line 42 and 5 to the pump regulator 2, which then reacts with a pressure increase in the pump outlet pressure p P in line 19.
- the pressure in the line 51 and in the load signaling line 42 can at most reach the load pressure level p L2 , since this leads to the opening of the check valve 40 and thus to the connection to the load-carrying consumer channel 46 or 39.
- the pressure level at the pump outlet 19 thus increases to p L2 + ⁇ p LS .
- the load pressure signal p L2 is likewise forwarded to the secondary pressure compensator 78, 87 of the consumer 16 via the load signaling line 5. Since it is presupposed that p L2 > p L1 , the load signal p L2 also acts on the piston head 27 of the two-part control piston 72, 73 of the secondary pressure compensator 78 via the channel 25, the shuttle valve 32, the channel 31 and the damping nozzle 30.
- the increased pressure signal of the pump 1 acts on the active surface of the piston head 37 of the secondary pressure compensator 78, 86, which in turn sets the constant pressure drop ⁇ p LS -p F1 via the inlet throttle 7.
- control concept shown is thus able to regardless of the applied load pressures via the inlet throttles 7, 10 preselected consumer speeds to keep constant.
- the secondary pressure compensators shown include 78, 86 and 79, 87 in addition to the load holding function all signal generating and signal comparing Functions, whereby no external logic elements, such as Check or shuttle valves are necessary.
- the two-part control pistons 72, 73 and 74, 75 Integrated seat valve function is implemented with mobile hydraulic Construction and work machines often required Load holding function without additional external components.
- Figure 4 shows an exemplary embodiment with two secondary pressure compensators 78, 86 and 79, 87 with two consumers 16, 17.
- FIG. 5 shows the opening characteristic using a diagram the outlet throttle in relation to the inlet throttle, the phase shift also depending the specified parameters is shown.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Description
- Fig. 1
- eine schematische Darstellung einer Sekundärdruckwaage mit integrierter Lasthaltefunktion,
- Fig. 2
- ein schematisches Steuerungskonzept für zwei translatorische Verbraucher,
- Fig. 3
- ein Ausführungsbeispiel einer Sekundär-Druckwaage mit integrierter Lasthaltefunktion,
- Fig. 4
- ein Ausführungsbeispiel eines Steuerungssystems mit zwei translatorischen Verbrauchern und in
- Fig. 5
- eine Öffnungscharakteristik der Ablaufdrossel im Verhältnis zur Zulaufdrossel.
- Fall I:
- Der zuerst betätigte Verbraucher 16 hat einen Lastdruck pL1, der größer ist als der des nachfolgend betätigten Verbrauchers 17 mit dem Lastdruck pL2. (pL1 > pL2).
- Fall II:
- Der zuerst betätigte Verbraucher 16 hat einen Lastdruck pL1, der dem des nachfolgend betätigten Verbrauchers 17 mit dem Lastdruck pL2 entspricht. (pL1 = pL2).
- Fall III:
- Der zuerst betätigte Verbraucher 16 hat einen Lastdruck pL1, der kleiner ist als der des nachfolgend betätigten Verbrauchers 17 mit dem Lastdruck pL2 (pL1 < pL2).
Claims (10)
- System zur lastdruckunabhängigen Steuerung und Lasthaltung mehrerer rotatorischer und/oder translatorischer Verbraucher einer Bau- und/oder Arbeitsmaschine mit mindestens einer geregelten Pumpe sowie mindestens einer einen federbelasteten Regelkolben beinhaltenden Sekundärdruckwaage,
dadurch gekennzeichnet, daß sämtliche Steuerungselemente zur Signalerzeugung und zum Signalvergleich des Load-Sensing Signales in einem oberen Gehäuseteil (78,79) und die die Lasthaltefunktion erzeugenden Bauteile (36,73,53,75) in einem mit dem oberen Gehäuseteil (78,79) lösbar verbundenen unteren Gehäuseteil (86,87) vorgesehen sind. - System nach Anspruch 1,
dadurch gekennzeichnet, daß das untere Gehäuseteil (86,87) Bestandteil des Steuerventiles (7,8,9 bzw. 10,11,12) ist. - System nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß zur Sicherstellung der Lasthalte- und Druckregelfunktion ein zweiteiliger Regelkolben (72,73 bzw. 74,75) vorgesehen ist, dessen unterer Teilkolben (73,75) aus einem Kegelsitzventil (36,53) in Verbindung mit. einem Drosselventil (84,85) gebildet ist und dessen oberer im wesentlichen im oberen Gehäuseteil (78,79) geführter Teilkolben (72,74) keine weiteren Elemente, wie z.B. Kanäle, Rückschlag-, Wechsel- bzw. Drosselventile, enthält. - System nach Anspruch 1, 2 oder 3,
dadurch gekennzeichnet, daß das für die Pumpenansteuerung und den internen Druckvergleich notwendige Drucksignal durch die in das obere Gehäuseteil (78,79) der Sekundärdruckwaagen integrierte Anordnung und entsprechende Dimensionierung von Drosseln (21 bzw. 38), Rückschlagventilen (23,34 bzw. 40,51), Wechselventilen (32 bzw. 49) sowie eines insbesondere externen LS-Bypass-Ventiles (3) aus dem Drucksignal zwischen den Zumeßdrosseln (7 bzw. 10) und der Steuerkante (84 bzw. 85) des Regelkolbens (73 bzw. 75) erzeugbar ist. - System nach Anspruch 3 oder 4,
dadurch gekennzeichnet, daß das in den unteren Teil (73 bzw. 75) des zweiteiligen Regelkolbens (72,73 bzw. 74,75) integrierte Kegelsitzventil (36,53) für die Lasthaltefunktion vorgesehen ist, welches durch das auf die Wirkfläche (27,44) des Regelkolbenkopfes wirkende verbraucherseitige Lastdrucksignal in Kanälen (22 bzw. 39) unter die Kräfte von Federn (28,45) beim Öffnen einer Ablaufdrossel (9 bzw. 12) wirksam verschließbar ist. - System nach einem oder mehreren der Ansprüche 1 bis 5,
dadurch gekennzeichnet, daß ein in das Gehäuse der jeweiligen Sekundärdruckwaage integrierter Verbindungskanal (24,41) von der Pumpe (1) zu einer den Pumpenregler (2) versorgenden Lastmeldeleitung (25,42) eine Verbindung in der Richtung vom Verbindungskanal (24,41) zur Lastmeldeleitung (25,42) aufweist und ein Rückschlagventil (34,51) zum Verschließen der entgegengesetzten Durchflußrichtung von der Lastmeldeleitung (25) zum Verbindungskanal (24) vorgesehen ist. - System nach einem oder mehreren der Ansprüche 1 bis 6,
dadurch gekennzeichnet, daß zur Begrenzung des an die Lastmeldeleitung (25,42) weitergeleiteten Drucksignales auf das Niveau des jeweiligen Verbraucherlastdruckes (pL1,2) im Kanal (22 bzw. 39) im Bypass zum Verbindungskanal (24,41) zur Lastmeldeleitung (25,42) ein mit dem lastführenden Verbraucherkanal (22,39) in Verbindung stehendes Rückschlagventil (23,40) angeordnet und eine als Drossel wirkende Blende (21,38) vorgesehen ist. - System nach einem oder mehreren der Ansprüche 1 bis 7,
dadurch gekennzeichnet, daß der den Druckraum des federbelasteten Regelkolbenkopfes (27,44) versorgende Kanal (31,48) eine Dämpfungsdüse bzw. ein Drosselrückschlagventil (30,47) zur Beeinflussung der Öffnungs- und Schließgeschwindigkeit des Regelkolbens (72,73 bzw. 74,75) beinhaltet - System nach einem oder mehreren der Ansprüche 1 bis 8,
dadurch gekennzeichnet, daß die Ablaufdrossel (9,12) der Hauptschieberachse (8,11) gegenüber einer zugeordneten Zulaufdrossel (7,10) eine definierte Phasenvoreilung aufweist, so daß die Ablaufdrossel (9,12) früher öffnet bzw. später schließt als die Zulaufdrossel (7,10). - System nach einem oder mehreren der Ansprüche 1 bis 9,
dadurch gekennzeichnet, daß die Öffnungscharakteristik der Ablaufdrossel (9,12) im Verhältnis zur Zulaufdrossel (7,10) eine Hauptschieberachse (8,11) einen vorgebbaren Verlauf aufweist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19745489 | 1997-10-15 | ||
DE19745489A DE19745489B4 (de) | 1997-10-15 | 1997-10-15 | System zur lastdruckunabhängigen Steuerung und Lasthaltung mehrerer rotatorischer und/oder translatorischer Verbraucher |
PCT/EP1998/006215 WO1999019571A1 (de) | 1997-10-15 | 1998-09-30 | System zur lastdruckunabhängigen steuerung und lasthaltung mehrerer rotatorischer und/oder translatorischer verbraucher |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1023508A1 EP1023508A1 (de) | 2000-08-02 |
EP1023508B1 true EP1023508B1 (de) | 2002-05-02 |
Family
ID=7845583
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98961094A Expired - Lifetime EP1023508B1 (de) | 1997-10-15 | 1998-09-30 | System zur lastdruckunabhängigen steuerung und lasthaltung mehrerer rotatorischer und/oder translatorischer verbraucher |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1023508B1 (de) |
JP (1) | JP2001520335A (de) |
DE (2) | DE19745489B4 (de) |
WO (1) | WO1999019571A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016215214A1 (de) * | 2016-08-16 | 2018-02-22 | Zf Friedrichshafen Ag | Getriebevorrichtung mit mehreren über hydraulisch betätigbare Kolben-Zylinder-Einrichtungen verstellbare Schaltstangen ein- und auslegbaren Übersetzungen |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10025188B4 (de) * | 2000-05-20 | 2004-07-22 | Adrian Verstallen | Druckerhöhungsanlage |
DE102004040437A1 (de) * | 2004-08-20 | 2005-09-15 | Audi Ag | Regelkolben einer Ölpumpe |
DE102006049584A1 (de) | 2006-03-13 | 2007-09-20 | Robert Bosch Gmbh | LUDV-Ventilanordnung |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2892312A (en) * | 1958-01-27 | 1959-06-30 | Deere & Co | Demand compensated hydraulic system |
DE3420990C2 (de) * | 1984-06-06 | 1994-10-27 | Bosch Gmbh Robert | Hydraulikanlage |
DE3443354A1 (de) * | 1984-11-28 | 1986-05-28 | Robert Bosch Gmbh, 7000 Stuttgart | Hydraulikanlage |
IN171213B (de) * | 1988-01-27 | 1992-08-15 | Hitachi Construction Machinery | |
DE4208256C2 (de) * | 1992-03-14 | 1994-06-30 | Guenter Richter | Hydraulische Steuereinrichtung für Messerstern-Teigteil- und Wirkmaschinen |
WO1993021446A1 (en) * | 1992-04-08 | 1993-10-28 | Kabushiki Kaisha Komatsu Seisakusho | Pressure oil supplying device |
FR2699609B1 (fr) * | 1992-12-22 | 1995-02-10 | Hydromo | Procédé et dispositif pour la mise en mouvement ou l'arrêt d'un moteur hydraulique entraînant un ensemble présentant une grande inertie. |
US5447093A (en) * | 1993-03-30 | 1995-09-05 | Caterpillar Inc. | Flow force compensation |
DE19528981C1 (de) * | 1995-08-07 | 1996-10-02 | Heilmeier & Weinlein | Verfahren zum Steuern eines Hydroverbrauchers und hydraulische Steuervorrichtung zur Durchführung des Verfahrens |
DE29604215U1 (de) * | 1996-03-07 | 1996-05-09 | Oil Control Gmbh | Hydraulisches Lasthalte- bzw. Senkbremsventil |
-
1997
- 1997-10-15 DE DE19745489A patent/DE19745489B4/de not_active Expired - Fee Related
-
1998
- 1998-09-30 JP JP2000516113A patent/JP2001520335A/ja not_active Withdrawn
- 1998-09-30 DE DE59804000T patent/DE59804000D1/de not_active Expired - Fee Related
- 1998-09-30 WO PCT/EP1998/006215 patent/WO1999019571A1/de active IP Right Grant
- 1998-09-30 EP EP98961094A patent/EP1023508B1/de not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016215214A1 (de) * | 2016-08-16 | 2018-02-22 | Zf Friedrichshafen Ag | Getriebevorrichtung mit mehreren über hydraulisch betätigbare Kolben-Zylinder-Einrichtungen verstellbare Schaltstangen ein- und auslegbaren Übersetzungen |
US10480642B2 (en) | 2016-08-16 | 2019-11-19 | Zf Friedrichshafen Ag | Multi speed transmission device with hydraulically actuated shift rods |
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DE59804000D1 (de) | 2002-06-06 |
WO1999019571A1 (de) | 1999-04-22 |
JP2001520335A (ja) | 2001-10-30 |
DE19745489B4 (de) | 2004-07-22 |
EP1023508A1 (de) | 2000-08-02 |
DE19745489A1 (de) | 1999-04-22 |
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