EP0656447B1 - Steuerung zur Aufteilung des Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher - Google Patents
Steuerung zur Aufteilung des Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher Download PDFInfo
- Publication number
- EP0656447B1 EP0656447B1 EP94117578A EP94117578A EP0656447B1 EP 0656447 B1 EP0656447 B1 EP 0656447B1 EP 94117578 A EP94117578 A EP 94117578A EP 94117578 A EP94117578 A EP 94117578A EP 0656447 B1 EP0656447 B1 EP 0656447B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- consumers
- consumer
- degree
- control
- hydraulic
- 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
- 239000012530 fluid Substances 0.000 title 1
- 238000010276 construction Methods 0.000 claims description 10
- 238000006073 displacement reaction Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 210000003746 feather Anatomy 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
- 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
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
-
- 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
-
- 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
- F15B2211/20546—Type of pump variable capacity
-
- 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
- F15B2211/25—Pressure control functions
-
- 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
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
- F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
-
- 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
- F15B2211/40—Flow control
- F15B2211/455—Control of flow in the feed line, i.e. meter-in control
-
- 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
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
-
- 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
- F15B2211/50—Pressure control
- F15B2211/57—Control of a differential pressure
-
- 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
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
- 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
-
- 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
- F15B2211/75—Control of speed of the output member
Definitions
- the invention relates to a controller for dividing the through at least one pump provided flow for hydraulic systems to multiple consumers the principle independent of load pressure, especially for construction machines, like wheel loaders, graders or excavators, each one a predeterminable control cross-section having control spool at least one compensator containing a piston is connected downstream and each downstream of the compensator Consumer a predeterminable proportion of the flow receives by the pistons of the compensators by different the passage cross-sections exerted on these forces to consumers with different opening pressures release.
- Hydraulic systems with spool valves according to the throttle principle are unable to To divide the flow rate when the spool is switched on, because even with a small pressure difference between the lower the total flow rate to consumers flows to.
- the load pressure independent system offers the possibility of the flow according to certain criteria to distribute to individual consumers.
- the hydraulic consumers e.g. cylinder
- the hydraulic consumers e.g. cylinder
- the hydraulic consumers e.g. Lifting frame, To receive booms, etc.
- Pressure compensators connected in parallel to each control piston (O + P Oil Hydraulics and Pneumatics, 35 (1991) No. 9, Pages 717 to 723 - Control of hydraulic drives with variable supply pressure). If there is insufficient supply, it flows the consumer with the lower pressure requirement with increasing Differential pressure between consumers is increasing higher proportion of the flow rate. With a 50% Degree of supply for two consumers with the same nominal flow rate receives the lower pressure-loaded consumer already at a pressure corresponding to the pressure compensator control pressure Pressure difference to the more heavily loaded consumer the whole Flow rate. Because the pressure compensator pressure is of the order of magnitude of 5-20 bar, is therefore already low changing pressure differences the total flow rate each flow to another consumer.
- Priority pressure compensators connected in series in the inlet to each spool. With simultaneous actuation of receives two or more consumers according to the training the pressure compensator piston the predetermined preferred consumer each the target amount, while the residual current is offered to other consumers. With a 50% Degree of supply for two consumers with the same nominal flow rate therefore the preferred consumer receives the full Flow rate (off highway capability - wheeled loaders der Vickers).
- LUDV Flow pressure independent flow distribution
- EP-A 491 050 is a generic hydraulic Control for dividing the available by a pump set flow rate in hydraulic systems several consumers according to the principle independent of load pressure, especially known for construction machinery.
- This publication settles only with the supply of hydraulic medium to the individual consumers in every operating state with sufficient supply to all consumers apart.
- To achieve this goal are in the field of the individual Compensators each provided stepped pistons that form different pressure spaces on the sides. With every piston acts a spring together, but not an actuator forms, but is intended exclusively for to keep the piston on its seat.
- By different hydraulic actuation of the respective pressure rooms inside the expansion joints are of different sizes cross sections to the individual consumers independent of load pressure switched.
- the object of the invention is a generic Control to evolve so that the requirements to the working hydraulics, especially of construction machinery be fulfilled automatically in the event of undersupply the ratio when two or for several consumers the flow flowing in differently is as the ratio of the nominal flow rates of these Consumers, this ratio also unaffected by the load (consumer) pressures.
- each piston each cooperates with a spring as an actuating element, the springs each having a different spring force have, such that in the event of a shortage of consumers through these different spring forces of the springs the flow rate is automatically divided into Dependence on the degree of the flow rate the degree of undersupply resulting from the pump the full supply changes.
- the invention has an equally advantageous effect Arrangement off, if the hydraulic system is operated that for a consumer the full cross section of the spool is released and for one or optionally also several other consumers of the tax cross-section to be released is constantly changing. For example, as with the operation of a wheel loader, the hand lever for the Hoist fully pulled, while the lever for the tipper depending on the current requirements of material intake is operated, the previously described arises Condition on.
- FIG. 1 shows a wheel loader 1, which consists essentially of the following components: a front end 2, a rear end 3, both of which are connected to one another via an articulated joint 4.
- a lifting frame 5 which carries a loading shovel 7 at its free end.
- the mast 5 can be raised and lowered via hydraulic cylinders 8 designed as consumers, while the bucket 7 can be tilted on and off by another consumer in the form of a hydraulic cylinder 9.
- Figure 2 shows a hydraulic excavator 10, one opposite an undercarriage 11 rotatable superstructure 12, one on the superstructure 12
- Boom 13 and arm 14 existing equipment is articulated.
- the stem 14 in turn carries a pivotable loading shovel 15 at its free end.
- the boom 13 is opposite the superstructure 12 via hydraulic cylinders 16 movable, while the stem 14 can be actuated by means of a further cylinder 17 is.
- the pivoting movement of the loading shovel 15 relative to the stick 14 is also brought about by a hydraulic cylinder 18.
- the hydraulic system shown in FIG. 3, which can be used, for example, for a wheel loader 1 according to FIG. 1, contains a single variable pump 20 equipped with a load-sensing controller 19, which is operatively connected to control slides 22, 23 via an inflow line 21.
- the control spools 22, 23 are provided with the same or different control cross sections A 1 and A 2 , depending on the design.
- a compensator 26, 27 is connected downstream of the control slides 22, 23 via further lines 24, 25, which in this example contains a piston 28, 29 and a spring 30, 31 as an actuating element in a simplified representation.
- Other actuating elements such as hydraulically, pneumatically or electromagnetically actuatable plungers, can also be implemented.
- the compensators 26, 27 are operatively connected to the downstream consumers, here the hydraulic cylinders 8, 9 according to FIG. 1, via further lines 32, 33.
- the consumers 8, 9 are subjected to different pressures p 1 and p 2 by the external forces acting on them. In the case of a wheel loader 1 or excavator 10, these are, for example, the lifting and tearing or digging forces when picking up material, in the case of a grader these can be the cutting forces acting on the coulter.
- the flow rate is the variable displacement pump 20 divided in a predeterminable ratio, by the opening pressures of the pistons 28, 29 selected differently Forces of the springs 30.31 are different.
- the closing pressure of the piston 28 is thus composed of the highest consumer pressure p 1 and the pressure p F1 that comes from the associated spring 30; that of the piston 29 is p 1 plus p F2 , where p F1 and p F2 correspond to those pressures on the piston end which keep the respective spring force in equilibrium.
- the variable displacement pump 20 delivers a delivery flow with a pressure p p that is higher than the highest load pressure p 1 by the load sensing differential pressure p LS , as long as the control cross sections A 1 released when the control slides 22, 23 are actuated.
- a 2 are kept so small that the total flow rate is less than or at most equal to the maximum flow rate Q max of the variable displacement pump 20.
- each of the consumers 8, 9 receives the target quantity Q 1S , Q 2S predetermined by the cross section A 1 , A 2 , which is calculated for the consumer 8
- Q 1S kx A 1S x p p - (p 1 + p F1 )
- the value for the consumer is analogous to 9
- Q 2S kx A 2S x p p - (p 1 + p F2 ) .
- the value k takes into account the physical quantities and the conversion factors of the flow equation as well as the number of jet contractions.
- the resulting differential pressure at the respective control cross section A 1 , A 2 which determines the flow rate, is therefore p p - (p 1 + p F1 ) respectively.
- the state of undersupply occurs because the variable displacement pump 20 is no longer able due to its design, which the control slides 22 To provide 23 requested flow rates.
- the delivery flow supplied by the variable displacement pump 20 will then have a value with p x which is less than p LS above the highest load pressure p 1 and therefore lower than the pump pressure p p when saturated. This is because the maximum oil flow Q max supplied by the variable displacement pump 20 now only requires a smaller pressure drop to pass through the cross sections A 1 and A 2 .
- Q 2nd kx A 2nd x p x - p F2 .
- Q 1S kx A 2S x p LS - p F2 kx A 1S x p LS - p F1 it is with undersupply
- Q 2nd Q 1 kx A 2nd x p x - p F2 kx A 1 x p x - p F1 ie in the event of undersupply, a larger part of the oil flow flows to the consumer 9 with Q 2 , which is supplied via the compensator 27 with the lower spring force and thus with the opening pressure p F2 of the piston 29.
- FIG. 4 shows a graphical representation of the proportion Q 2 of the consumer 9 in the total flow Q max according to FIG. 1, assuming that the control cross section A 1 is fully open for the consumer 8 in all operating states.
- FIG. 4 is based on the assumption that the control cross section A 1 , A 2 of each control spool 22, 23 is designed such that, when actuated alone, the maximum pump delivery flow Q max can pass at the given load sensing differential pressure p LS .
- the percentage Q 2 of the throttled consumer 9 in the total flow Q max is plotted on the ordinate, while the ratio A 2 / A 2max of the instantaneous opening cross section to the largest possible control cross section of the control slide 23 is shown on the abscissa.
- This ratio is selected according to the specific requirements of the respective machine.
- the control cross section A 1 of the control slide 22 is fully open.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Fluid-Pressure Circuits (AREA)
Description
- Fig. 1 -
- Prinzipskizze eines Radladers,
- Fig. 2 -
- Prinzipskizze eines Baggers,
- Fig. 3 -
- Prinzipskizze eines LUDV-Schiebers mit den erfindungsgemäßen Merkmalen,
- Fig. 4 -
- graphische Darstellung der Aufteilung des Förderstromes für einen der Verbraucher gemäß Figur 1.
- Figur 5 -
- graphische Darstellung der Versorgungsgrade von zwei Verbrauchern sowie des Gesamtsystems.
einem Vorderwagen 2, einem Hinterwagen 3, die beide über ein Knickgelenk 4 miteinander verbunden sind. Im Bereich des Vorderwagens 2 ist ein Hubgerüst 5 vorgesehen, das an seinem freien Ende eine Ladeschaufel 7 trägt. Das Hubgerüst 5 ist über als Verbraucher ausgebildete Hydraulikzylinder 8 heb-und senkbar, während die Schaufel 7 durch einen weiteren Verbraucher in Form eines Hydraulikzylinders 9 an- und auskippbar ist.
- load sensing Differenzdruck: pLS = 14 bar
- Öffnungsdruck durch Federkraft: pF1 = 10 bar
- Öffnungsdruck durch Federkraft: pF2 = 4 bar.
A2 / A2max | Q2 | Q1 | V2 | V1 | Vg |
- | l/min | l/min | - | - | - |
0,0 | 100 | 1,00 | 1,00 | 1,00 | |
0,1 | 9,6 | 90,4 | 0,960 | 0,904 | 0,909 |
0,2 | 18,6 | 81,4 | 0,930 | 0,814 | 0,833 |
0,3 | 27,0 | 73,0 | 0,900 | 0,730 | 0,769 |
0,4 | 35,1 | 64,9 | 0,878 | 0,649 | 0,714 |
0,5 | 42,8 | 57,2 | 0,858 | 0,572 | 0,667 |
0,6 | 50,2 | 49,8 | 0,837 | 0,498 | 0,625 |
0,7 | 57,4 | 42,6 | 0,820 | 0,426 | 0,588 |
0,8 | 64,5 | 35,5 | 0,806 | 0,355 | 0,556 |
0,9 | 71,6 | 28,4 | 0,796 | 0,284 | 0,526 |
1,0 | 78,6 | 21,4 | 0,786 | 0,214 | 0,500 |
Claims (4)
- Steuerung zur Aufteilung des durch mindestens eine Pumpe zur Verfügung gestellten Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher (8,9) nach dem lastdruckunabhängigen Prinzip, insbesondere für Baumaschinen, wie Radlader (1), Grader oder Bagger, wobei einem jeden einen vorgebbaren Steuerquerschnitt (A1,A2) aufweisenden Steuerschieber (22,23) zumindest ein einen Kolben (28,29) beinhaltender Kompensator (26,27) nachgeschaltet ist und jeder dem Kompensator (26,27) nachgeschaltete Verbraucher (8,9) einen vorgebbaren Anteil des Förderstromes (Qmax) erhält, indem die Kolben (28,29) der Kompensatoren (26,27) durch unterschiedlich auf diese ausgeübte Kräfte die Durchtrittsquerschnitte zu den Verbrauchern (8,9) mit unterschiedlichen Öffnungsdrücken freigeben,
dadurch gekennzeichnet,
daß jeder Kolben (28,29) jeweils mit einer Feder (30,31) als Betätigungselement zusammenwirkt, wobei die Federn (30,31) jeweils eine unterschiedliche Federkraft aufweisen, derart, daß bei Unterversorgung der Verbraucher (8,9) durch diese unterschiedlichen Federkräfte der Federn (30,31) sich die Aufteilung des Förderstromes automatisch in Abhängigkeit vom Maß des durch den jeweiligen Förderstrom der Pumpe (20) sich ergebenden Grades der Unterversorgung gegenüber der Vollversorgung ändert. - Steuerung nach Anspruch 1,
dadurch gekennzeichnet,
daß mit dem Grad der Unterversorgung entsprechend der Wahl der Federkräfte der Federn (30,31) der Grad der Priorität der einzelnen Verbraucher (9) gegenüber den anderen Verbrauchern (8) ansteigt. - Steuerung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der jeweilige Kolben (28,29) durch eine Kombination aus mechanischer Feder und pneumatischer bzw. hydraulischer oder elektromagnetischer Betätigung mit Kraft beaufschlagbar ist.
- Steuerung nach Anspruch 3, dadurch gekennzeichnet, daß das Aufteilungsverhältnis der Kräfte aus mechanischer Feder und pneumatischer bzw. hydraulischer oder elektromagnetischer Betätigung, welche den Gesamtöffnungsdruck bewirken, vorgebbar einstellbar ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4341244 | 1993-12-03 | ||
DE4341244A DE4341244C2 (de) | 1993-12-03 | 1993-12-03 | Steuerung zur Aufteilung des durch mindestens eine Pumpe zur Verfügung gestellten Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0656447A1 EP0656447A1 (de) | 1995-06-07 |
EP0656447B1 true EP0656447B1 (de) | 1998-05-20 |
Family
ID=6504109
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94117578A Expired - Lifetime EP0656447B1 (de) | 1993-12-03 | 1994-11-08 | Steuerung zur Aufteilung des Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher |
Country Status (4)
Country | Link |
---|---|
US (1) | US5609089A (de) |
EP (1) | EP0656447B1 (de) |
AT (1) | ATE166411T1 (de) |
DE (2) | DE4341244C2 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1996002707A1 (de) * | 1994-07-13 | 1996-02-01 | O & K Orenstein & Koppel Ag | Verfahren und einrichtung zur lagegerechten positionierung der an einem abwärts sich bewegenden hubgerüst einer mobilen arbeitsmaschine kippbar angeordneten arbeitsausrüstung |
KR970007735B1 (ko) * | 1995-06-13 | 1997-05-16 | 대우중공업 주식회사 | 휠로다의 조향유압시스템 |
DE19939796C1 (de) | 1999-08-21 | 2000-11-23 | Orenstein & Koppel Ag | Verfahren und Arbeitsmaschine zur Herstellung von Bodenflächen |
CN100402763C (zh) * | 2002-09-26 | 2008-07-16 | 日立建机株式会社 | 建筑机械 |
DE102007028864A1 (de) * | 2007-03-27 | 2008-10-02 | Robert Bosch Gmbh | Hydraulische Steueranordnung |
US20080288989A1 (en) * | 2007-05-14 | 2008-11-20 | Zheng Yu Brian | System, Methods and Apparatus for Video Communications |
US7854115B2 (en) * | 2008-04-25 | 2010-12-21 | Husco International, Inc. | Post-pressure compensated hydraulic control valve with load sense pressure limiting |
JP6292979B2 (ja) * | 2014-05-26 | 2018-03-14 | Kyb株式会社 | ロードセンシング制御回路 |
DE102019216771A1 (de) * | 2019-10-30 | 2021-05-06 | Robert Bosch Gmbh | Hydraulische Steueranordnung zur Druckmittelversorgung wenigstens zweier hydraulischer Verbraucher |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3603630A1 (de) * | 1986-02-06 | 1987-08-13 | Rexroth Mannesmann Gmbh | Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher |
JPH0826883B2 (ja) * | 1989-05-24 | 1996-03-21 | 株式会社小松製作所 | 油圧回路 |
JPH0826882B2 (ja) * | 1989-05-24 | 1996-03-21 | 株式会社小松製作所 | 油圧回路 |
US5209063A (en) * | 1989-05-24 | 1993-05-11 | Kabushiki Kaisha Komatsu Seisakusho | Hydraulic circuit utilizing a compensator pressure selecting value |
US5279122A (en) * | 1989-08-16 | 1994-01-18 | Kabushiki Kaisha Komatsu Seisakusho | Hydraulic circuit apparatus for supplying fluid under pressure into hydraulic cylinders for work implement |
EP0551513A1 (de) * | 1990-02-28 | 1993-07-21 | Hitachi Construction Machinery Co., Ltd. | Hydraulisches betätigungssystem für baumaschinen |
EP0657656B1 (de) * | 1990-05-15 | 2000-03-22 | Kabushiki Kaisha Komatsu Seisakusho | Hydraulisches system |
KR940008823B1 (ko) * | 1990-07-05 | 1994-09-26 | 히다찌 겐끼 가부시기가이샤 | 유압구동장치 및 밸브장치 |
US5067389A (en) * | 1990-08-30 | 1991-11-26 | Caterpillar Inc. | Load check and pressure compensating valve |
DE4036720C2 (de) * | 1990-11-17 | 2001-09-13 | Linde Ag | Steuerschaltung für die lastunabhängige Aufteilung eines Druckmittelstromes |
JPH04210101A (ja) * | 1990-11-30 | 1992-07-31 | Komatsu Ltd | 油圧回路 |
DE4041288C1 (en) * | 1990-12-21 | 1992-06-11 | Mannesmann Rexroth Gmbh, 8770 Lohr, De | Hydraulic control system for several users - uses movable piston to match pump output to demand |
JP3101830B2 (ja) * | 1991-06-12 | 2000-10-23 | 株式会社小松製作所 | 旋回式作業装置の油圧回路 |
US5207059A (en) * | 1992-01-15 | 1993-05-04 | Caterpillar Inc. | Hydraulic control system having poppet and spool type valves |
JP2579202Y2 (ja) * | 1992-04-10 | 1998-08-20 | 株式会社小松製作所 | 圧力補償弁を備えた操作弁 |
US5446979A (en) * | 1992-04-20 | 1995-09-05 | Hitachi Construction Machinery Co., Ltd. | Hydraulic circuit system for civil engineering and construction machines |
JPH06123123A (ja) * | 1992-05-22 | 1994-05-06 | Hitachi Constr Mach Co Ltd | 油圧駆動装置 |
FR2694606B1 (fr) * | 1992-08-04 | 1994-11-04 | Bennes Marrel | Ensemble de commande d'une pluralité de récepteurs hydrauliques. |
JP3179596B2 (ja) * | 1992-11-17 | 2001-06-25 | 日立建機株式会社 | 流量制御装置 |
-
1993
- 1993-12-03 DE DE4341244A patent/DE4341244C2/de not_active Expired - Fee Related
-
1994
- 1994-11-08 AT AT94117578T patent/ATE166411T1/de not_active IP Right Cessation
- 1994-11-08 DE DE59406014T patent/DE59406014D1/de not_active Expired - Lifetime
- 1994-11-08 EP EP94117578A patent/EP0656447B1/de not_active Expired - Lifetime
- 1994-12-01 US US08/352,774 patent/US5609089A/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
US5609089A (en) | 1997-03-11 |
DE4341244C2 (de) | 1997-08-14 |
DE4341244A1 (de) | 1995-06-08 |
EP0656447A1 (de) | 1995-06-07 |
ATE166411T1 (de) | 1998-06-15 |
DE59406014D1 (de) | 1998-06-25 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE10109510B4 (de) | Vorrichtung zur Aktuatorensteuerung von Hydraulik-Antriebsmaschinen | |
EP2541072B1 (de) | Steueranordnung und Verfahren zum Ansteuern von mehreren hydraulischen Verbrauchern | |
DE102004050294B3 (de) | Hydraulische Ventilanordnung | |
DE60113002T2 (de) | Hydraulische antriebseinrichtung | |
DE4137963C2 (de) | Ventilanordnung zur lastunabhängigen Steuerung mehrerer hydraulischer Verbraucher | |
EP1574474A2 (de) | Hydraulische Anordnung | |
EP1450048A1 (de) | Ventilanordnung | |
DE112006002560T5 (de) | Hydrauliksystem mit verstärkter Druckkompensation | |
DE10330869A1 (de) | Hydraulisches System | |
DE102012207422A1 (de) | Hydraulische Steueranordnung mit Lastdruckminderungund hydraulischer Ventilblock dafür | |
EP0141301B1 (de) | Hydraulischer Kreislauf für einen eine Last bewegenden Motor | |
EP0656447B1 (de) | Steuerung zur Aufteilung des Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher | |
DE4235707B4 (de) | Hydrostatisches Antriebssystem | |
DE4027047C2 (de) | ||
EP2142808B1 (de) | Hydraulische steueranordnung | |
DE3508339A1 (de) | Aus zwei steuerbloecken bestehende steuerventileinrichtung fuer mehrere hydraulische antriebe, insbesondere von mobilgeraeten | |
EP2171289A1 (de) | Steuervorrichtung für mindestens zwei hydraulische antriebe | |
EP1565658B1 (de) | Hydraulisches zweikreissystem | |
DE102013214734A1 (de) | Hydraulische Steueranordnung und Verfahren zur Versorgung mehrere Verbraucher damit | |
DE19720454B4 (de) | Hydrostatisches Antriebssystem | |
DE19548943B4 (de) | Ventilanordnung | |
DE4210252C1 (de) | ||
EP1576241B1 (de) | Steuereinrichtung für ein arbeitsgerät mit einer ausleger gehaltenen schaufel | |
DE19541190A1 (de) | Hydraulische Anordnung zur Steuerung des Hubwerks einer mobilen Arbeitsmaschine | |
EP0615024B1 (de) | Lastdruckunabhängige Steuerung der Geschwindigkeit von hydraulischen Stellelementen an Baumaschinen |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 19950329 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT CH DE FR LI SE |
|
17Q | First examination report despatched |
Effective date: 19960311 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT CH DE FR LI SE |
|
REF | Corresponds to: |
Ref document number: 166411 Country of ref document: AT Date of ref document: 19980615 Kind code of ref document: T |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: NV Representative=s name: BOVARD AG PATENTANWAELTE |
|
REF | Corresponds to: |
Ref document number: 59406014 Country of ref document: DE Date of ref document: 19980625 |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: AT Payment date: 20061124 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: CH Payment date: 20061127 Year of fee payment: 13 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20071130 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20071130 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20071108 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: CJ Ref country code: FR Ref legal event code: CD |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20101018 Year of fee payment: 17 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20101013 Year of fee payment: 17 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20101123 Year of fee payment: 17 |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: EUG |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20120731 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 59406014 Country of ref document: DE Effective date: 20120601 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20111109 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20111130 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120601 |