EP0615024A2 - Commande de vitesse, ne dépendant pas de la pression de charge pour éléments hydrauliques de réglage sur des machines de construction - Google Patents

Commande de vitesse, ne dépendant pas de la pression de charge pour éléments hydrauliques de réglage sur des machines de construction Download PDF

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Publication number
EP0615024A2
EP0615024A2 EP94101011A EP94101011A EP0615024A2 EP 0615024 A2 EP0615024 A2 EP 0615024A2 EP 94101011 A EP94101011 A EP 94101011A EP 94101011 A EP94101011 A EP 94101011A EP 0615024 A2 EP0615024 A2 EP 0615024A2
Authority
EP
European Patent Office
Prior art keywords
pressure
control
line
load
orifice
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
EP94101011A
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German (de)
English (en)
Other versions
EP0615024B1 (fr
EP0615024A3 (fr
Inventor
Walter Kolb
Gustav Leidinger
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.)
CNH Industrial Baumaschinen GmbH
Original Assignee
O&K Orenstein and Koppel 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
Application filed by O&K Orenstein and Koppel GmbH filed Critical O&K Orenstein and Koppel GmbH
Publication of EP0615024A2 publication Critical patent/EP0615024A2/fr
Publication of EP0615024A3 publication Critical patent/EP0615024A3/fr
Application granted granted Critical
Publication of EP0615024B1 publication Critical patent/EP0615024B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • E02F9/2221—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
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • 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
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • 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
    • F15B11/02—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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3055—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and return line
    • 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
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out 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
    • F15B2211/60—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
    • F15B2211/75—Control of speed of the output member

Definitions

  • the invention relates to a load pressure-independent control of the speed of hydraulic control elements, such as cylinders, hydraulic motors or the like., With premature loads on construction machines, such as wheel loaders, excavators or the like. With at least one pressure medium from a tank-delivering pump with a variable delivery volume by a controller and at least one control slide with at least one control piston for actuating the control element or elements.
  • the conventional hydraulic systems When pulling, i.e. leading load, the conventional hydraulic systems are only able to influence the speed of the adjusting element, such as cylinders, hydraulic motors or the like, by means of a throttle effect. Since the oil flow flowing through the throttle is dependent on the load pressure, the adjustment speed is therefore also dependent on the load pressure.
  • the adjusting element such as cylinders, hydraulic motors or the like
  • the term 'independent of the load pressure' refers to the adjustment speed of the individual control elements, such as in particular cylinders, which is independent of the load pressure which acts on the control elements by external forces.
  • This independence is achieved by a so-called load-sensing system, which essentially consists of a central, hydraulically adjustable variable displacement pump with a hydraulically actuated adjusting element for regulating the delivery pressure and a hydraulic pressure signaling device for transmitting the load pressure applied to a controlled working cylinder or another adjusting element to the adjusting element the variable displacement pump.
  • This pressure signaling device thus transmits the pending load pressure to the actuator of the variable pump, which acts on the corresponding control slide with a delivery pressure which is a design-dependent constant differential pressure above the pending load pressure. If several working cylinders or other control elements are actuated at the same time, the highest load pressure is reported to the control element of the variable pump via corresponding shuttle valves in the branches of the pressure signaling device.
  • variable displacement pump Due to the control of the corresponding control spool with a constant differential pressure above the load pressure applied to the working cylinder or other actuating elements, that of the working cylinder or the another actuating device operated tool moves at a substantially constant, depending on the position of the spool, which facilitates the operation of such tools.
  • the variable displacement pump due to the load-sensing system, only delivers the flow rate assigned to the respective working cylinder or control element, as a result of which no flow rate-dependent losses occur and the efficiency of the hydraulic drive device is increased.
  • the object of the invention is to be able to control the speed of a pulling load independently of the load pressure.
  • the pressure compensator is used in the connecting line of the space of the control element to the control slide, in particular to the associated control piston, that the return area of the associated control piston is designed as a differential pressure orifice, and that the pressure signal of the oil flow before it passes through the Differential pressure orifice can be brought about via a line to the side of the pressure compensator facing away from the spring chamber.
  • the goal is also achieved in that the pressure compensator is inserted into the line between the outlet of the slide, in particular the associated control piston, and the tank, that the return area of the associated control piston is designed as a differential pressure orifice, and that the pressure message of the oil flow before it passes through the differential pressure orifice via a line to the side of the pressure compensator facing away from the spring chamber.
  • the pressure compensator In the connecting line from the space of the actuator to the spool, the pressure compensator is used so that it performs its intended function when the oil flow flows from this space to the spool.
  • the return opening in the associated control piston which up to now has been designed as a free passage or, depending on requirements, also as a throttle opening, is designed here as a differential pressure orifice according to the desired flow characteristics.
  • the pressure messages for the pressure compensator are such that the pressure in the line to the differential pressure orifice is directed to the side of the pressure compensator facing away from the spring chamber.
  • FIG. 1 now shows the lowering of the working device of a wheel loader, not shown, in this example, as a bucket 1, under the dead weight G.
  • a pressure resulting from the weight G and possibly the payload of the bucket 1 builds up.
  • the control piston 5 arranged in the control slide 4 in the direction of the position shown, oil flows out via the lines 6 and 7 and further via a differential pressure orifice 8 into the tank 9.
  • the pressure of the line 7 is directed to the spring-facing side 10 of the pressure compensator 11 provided between the line 6 and the control slide 4.
  • the pressure in the control line 12 is passed through a shuttle valve 13 into the spring chamber 14 of the pressure compensator 11.
  • the shuttle valve 13 blocks the connection from the load pressure signaling line 15, which is only acted upon by the suction pressure and which taps the pressure through the differential pressure orifice 8 'which is common in load-sensing systems.
  • Different supply lines to further control pistons 21, 22 are designated by 20.
  • the pressure compensator 11 reduces the pressure in the line 6 of the cover-side space 2 to a value which is reduced so far in accordance with its spring force that a constant pressure drop which is analogous to the spring force is set at the differential pressure orifice 8.
  • the oil flow passing through the differential pressure orifice 8 and thus the lowering speed of the blade 1 is independent of the load pressure and only dependent on the opening cross section of the differential pressure orifice 8, which is predetermined by the respective position of the associated control piston 5.
  • further control pistons 21 and 22 can be provided in the control valve 4.
  • control pistons 21, 22 as well as the control piston 5 can be used in the usual way in load-sensing systems with pressure compensators, not shown here, for the mutually unaffected simultaneous actuation of pushing Loads in the lines 20 from the pump 17 to the respective control piston 5, 21, 22 can be equipped.
  • a corresponding pressure compensator - not shown here for the sake of a better overview - can also be assigned to the control pistons 21 and / or 22 if pulling loads are also to be controlled here independently of the load pressure.
  • F ground pressure
  • the delivery flow is metered by pressure into the annular space 18 of the hydraulic cylinder 3, it being necessary to ensure that the oil displaced from the cover-side space 2 of the cylinder 3 is not throttled by the pressure compensator 11, because this is as small as possible Flow resistance should flow into the tank 9.
  • the pressure of the oil flow directed to the adjustment of the cylinder 3 in the annular space 18 is passed via the load pressure signaling line 15 and the shuttle valve 13 into the spring chamber 14 of the pressure compensator 11.
  • the shuttle valve 13 blocks the connection of the control line 12, which is only pressurized in the tank 9.
  • FIG. 3 shows the lifting of the bucket 1 which may contain a payload, the same components again being provided with the same reference numerals.
  • the delivery flow is metered by pressure into the cover-side space 2 of the cylinder 3, it being necessary to ensure that the inflowing oil is not throttled by the pressure compensator 11.
  • the pressure to adjust the cylinder 3 in the room 2 oil flow is passed via the load pressure signal line 15 and the shuttle valve 13 into the spring chamber 14 of the pressure compensator 11.
  • the shuttle valve 13 blocks the connection from the control line 12 which is only acted upon by the pressure in the tank 9.
  • the pressure of the cover-side space 2 of the cylinder 3 acts, which is equal to that in the load pressure reporting line 15 .
  • the same hydraulic pressure thus acts on both end faces of the piston 23 of the pressure compensator 11. For this reason, the piston 23 of the pressure compensator 11 is guided into the end position with the spring force, the passage from the line 7 to the line 6 being released.
  • FIGS. 4 to 6 show equivalent controls according to FIGS. 1 to 3.
  • the pressure compensator 11 is inserted between the outlet 25 of the slide 4 and the tank 9, functionally the same conditions and also in all three operating states in the corresponding lines analog pressures prevail, which is described as follows:
  • FIG. 4 shows, analogously to FIG. 1, the lowering of the working device designed as a blade 1.
  • a pressure builds up resulting from the weight G and possibly the payload of the blade 1.
  • oil flows out into the tank 9 via the lines 6, 26.
  • the pressure of line 6 is passed via line 29 to the spring-side 27 of the pressure compensator 11 provided between the outlet 25 of the control slide 4 and the tank 9.
  • the pressure in line 26 is passed via a shuttle valve 13 into the spring chamber 14 of the pressure compensator 11.
  • the shuttle valve 13 blocks the connection from the load pressure signaling line 15, which is only acted upon by the suction pressure and which taps the pressure through the differential pressure orifice 8 'which is common in load-sensing systems.
  • An additional quantity of oil required to fill the annular space 18 of the cylinder 3 in addition to the flow rate of the pump 17 controlled by the regulator 16 is supplemented by a suction valve 19 which is arranged in the pressure medium supply line 20 '.
  • the pressure compensator 11 reduces the pressure in the line 6 of the cover-side space 2 of the cylinder 3 to a value so far reduced in accordance with its spring force that a constant pressure drop which is analogous to the spring force is established at the differential pressure orifice 8.
  • the oil flow passing through the differential pressure orifice 8 and thus the lowering speed of the blade 1 is thus independent of the load pressure and only dependent on the opening cross section of the differential pressure orifice 8, which is predetermined by the respective position of the control piston 5.
  • further control pistons 21 and 22 can be provided in the control valve 4.
  • control pistons 21, 22 and also the control piston 5 can, in the usual way in load-sensing systems, with pressure compensators, not shown here, for the mutually unaffected simultaneous actuation of pressing loads in the lines 20 from the pump 17 to the respective control piston 5, 21 , 22 be equipped.
  • a corresponding pressure compensator - not shown here for the sake of a better overview - can also be assigned to the control piston 21 and / or 22, provided that pulling loads are to be controlled here independently of the load pressure.
  • the shuttle valve 13 blocks the connection of the line 26 which is only pressurized in the tank 9
  • the only effect on page 27 is the low dynamic pressure in the line 29 of the oil flowing out of the cover-side space 2 into the tank 9. Therefore, the piston 23 of the pressure compensator 11 is guided into the end position, the passage from the line 26 to the tank 9 being released without the pressure compensator 11 taking effect.
  • FIG. 6 shows the lifting of the bucket 1, with the same components again being provided with the same reference symbols.
  • FIG. 7 can be seen analogously to FIG. 1, with the actuator cylinder being replaced by a hydraulic motor 28 in this example.
  • the pulling load can be predetermined here by a torque T generated by external influences, which causes the hydraulic motor 28 to become the pump, so that it pumps 6 pressure oil into the line.

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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)
EP94101011A 1993-03-12 1994-01-25 Commande de vitesse, ne dépendant pas de la pression de charge pour éléments hydrauliques de réglage sur des machines de construction Expired - Lifetime EP0615024B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4307872 1993-03-12
DE4307872A DE4307872C2 (de) 1993-03-12 1993-03-12 Lastdruckunabhängige Steuerung der Geschwindigkeit von hydraulischen Stellelementen

Publications (3)

Publication Number Publication Date
EP0615024A2 true EP0615024A2 (fr) 1994-09-14
EP0615024A3 EP0615024A3 (fr) 1996-09-25
EP0615024B1 EP0615024B1 (fr) 2001-04-11

Family

ID=6482620

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94101011A Expired - Lifetime EP0615024B1 (fr) 1993-03-12 1994-01-25 Commande de vitesse, ne dépendant pas de la pression de charge pour éléments hydrauliques de réglage sur des machines de construction

Country Status (4)

Country Link
EP (1) EP0615024B1 (fr)
AT (1) ATE200538T1 (fr)
DE (2) DE4307872C2 (fr)
ES (1) ES2155837T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0823559A3 (fr) * 1996-08-09 1998-07-15 Robert Bosch Gmbh Dispositif de commande hydraulique
CN104314896A (zh) * 2014-09-26 2015-01-28 山东恒堃机械有限公司 一种移动模架模板控制系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10321914A1 (de) 2003-05-15 2004-12-02 Bosch Rexroth Ag Hydraulische Steueranordnung

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992015799A1 (fr) 1991-03-07 1992-09-17 Caterpillar Inc. Commande de charge negative et systeme utilisant cette energie

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DE2906670A1 (de) * 1979-02-21 1980-09-04 Bosch Gmbh Robert Ventileinrichtung zur lastkompensierten steuerung eines hydraulischen verbrauchers
DE3321483A1 (de) * 1983-06-14 1984-12-20 Linde Ag, 6200 Wiesbaden Hydraulische einrichtung mit einer pumpe und mindestens zwei von dieser beaufschlagten verbrauchern hydraulischer energie
DE3532816A1 (de) * 1985-09-13 1987-03-26 Rexroth Mannesmann Gmbh Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher
DE3644737C2 (de) * 1985-09-13 1995-11-23 Rexroth Mannesmann Gmbh Steueranordnung für mindestens zwei von mindestens einer Pumpe gespeiste hydraulische Verbraucher
DE3536218A1 (de) * 1985-10-10 1987-04-16 Heilmeier & Weinlein Zweiwege-stromregler
DE3817218A1 (de) * 1987-06-11 1988-12-22 Mannesmann Ag Hydraulisches steuersystem fuer einen hydraulikbagger
DE3800188A1 (de) * 1988-01-07 1989-07-20 Danfoss As Hydraulische sicherheitsbremsventilanordnung
WO1989009343A1 (fr) * 1988-03-23 1989-10-05 Hitachi Construction Machinery Co., Ltd. Unite d'entrainement hydraulique
JP2520314B2 (ja) * 1990-01-18 1996-07-31 株式会社小松製作所 油圧掘削機の走行速度切換装置
DE4027047A1 (de) * 1990-08-27 1992-03-05 Rexroth Mannesmann Gmbh Ventilanordnung zur lastunabhaengigen steuerung mehrerer hydraulischer verbraucher
WO1992018711A1 (fr) * 1991-04-15 1992-10-29 Hitachi Construction Machinery Co., Ltd. Systeme d'entrainement hydraulique dans un engin de chantier
DE4210252C1 (fr) * 1992-03-28 1993-09-02 O & K Orenstein & Koppel Ag, 13581 Berlin, De

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992015799A1 (fr) 1991-03-07 1992-09-17 Caterpillar Inc. Commande de charge negative et systeme utilisant cette energie

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0823559A3 (fr) * 1996-08-09 1998-07-15 Robert Bosch Gmbh Dispositif de commande hydraulique
CN104314896A (zh) * 2014-09-26 2015-01-28 山东恒堃机械有限公司 一种移动模架模板控制系统

Also Published As

Publication number Publication date
DE59409720D1 (de) 2001-05-17
ES2155837T3 (es) 2001-06-01
EP0615024B1 (fr) 2001-04-11
DE4307872A1 (de) 1994-09-22
ATE200538T1 (de) 2001-04-15
EP0615024A3 (fr) 1996-09-25
DE4307872C2 (de) 2001-05-17

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