EP0563514B1 - Lastdruckunabhängige, hydraulische Antriebsvorrichtung für Arbeitsgeräte an Baumaschinen - Google Patents

Lastdruckunabhängige, hydraulische Antriebsvorrichtung für Arbeitsgeräte an Baumaschinen Download PDF

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Publication number
EP0563514B1
EP0563514B1 EP93100534A EP93100534A EP0563514B1 EP 0563514 B1 EP0563514 B1 EP 0563514B1 EP 93100534 A EP93100534 A EP 93100534A EP 93100534 A EP93100534 A EP 93100534A EP 0563514 B1 EP0563514 B1 EP 0563514B1
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EP
European Patent Office
Prior art keywords
pressure
load
line
control
displacement 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.)
Revoked
Application number
EP93100534A
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German (de)
English (en)
French (fr)
Other versions
EP0563514A1 (de
Inventor
Josef Ratzinger
Gustav Keidinger
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CNH Industrial Baumaschinen GmbH
Original Assignee
O&K Orenstein and Koppel GmbH
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Filing date
Publication date
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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
    • E02F9/2278—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
    • F15B11/16—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
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-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
    • F15B2211/30535—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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31529—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and a single output member
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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
    • 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
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check 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
    • F15B2211/60—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

Definitions

  • the invention relates to a hydraulic drive device for work equipment on construction machines, agricultural machinery, industrial trucks and the like which is independent of the load pressure. According to the preamble of patent claim 1.
  • Such drive devices are used as mobile hydraulics, for example, in degrees and are used there to actuate the share, the front plate, the rear ripper and other functions.
  • the "load pressure independent" attribute relates to the adjustment speed of the individual work tools, which acts on the work tools independently of the load pressure of the substrate being treated.
  • This independence is achieved by a so-called load sensing system, which essentially comprises a central, hydraulically adjustable adjusting 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 to the adjusting element of the adjusting pump.
  • This pressure signaling device transmits the pending load pressure to the actuator of the variable displacement 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 are actuated at the same time, the highest load pressure is reported to the actuator 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, the working device actuated by the working cylinder is moved at a substantially constant speed which is dependent on the position of the control spool, which considerably facilitates the operation of such working devices.
  • the variable displacement pump due to the load sensing system, the variable displacement pump only has to be operated at partial load with a comparatively low flow rate requirement, as a result of which no flow rate-dependent losses occur and the efficiency of the hydraulic drive device is increased.
  • Load pressure-independent, hydraulic drive devices with load sensing systems have the disadvantage, due to the associated adjustment speed of the work tools, that faster movements of the work tools, such as those when positioning or returning, during empty strokes or when evading, especially of the work tools, are desirable or necessary in dangerous situations , cannot be carried out.
  • the system-related, design-based adjustment speed of the work tools is not sufficient for a quick reaction to non-operational occurrences, which is e.g. also has an adverse effect on the working speed when avoiding or bypassing obstacles such as shafts, curbs etc.
  • EP-A 439 621 discloses a device for loading the cylinders of work machines, with which the purpose is achieved of being able to reduce the oil flow to the cylinders for fine work.
  • the control described for the cylinders should respond so that an extremely small amount of oil is supplied to them.
  • the connection of the pump line to the pump controller is in this case analogous to the subject matter of the invention, but the objective of increasing the speed of the working tools is not desired and is also not achievable.
  • the object of the invention is to develop a hydraulic drive device of the type mentioned at the outset that is independent of the load pressure in such a way that a significantly higher adjustment speed of the implements is achieved independently of the load sensing system. So a so-called “rapid traverse” should be created for the tools.
  • the invention is embodied by the basic idea that the control element of the variable displacement pump can be acted upon with a control pressure which is significantly above the load pressure present, independently of the pressure signaling device.
  • the variable displacement pump thus works in this operating state with a significantly higher delivery pressure than the pressure given by the load sensing system, so that a controlled working cylinder is moved with a correspondingly significantly increased adjustment speed.
  • the higher control pressure can be taken from any pressure accumulator or generator available in the hydraulic system.
  • the drive device according to the invention consequently has a "rapid traverse", with the help of which the machine operator moves to the entry can react quickly to non-operational incidents mentioned and position or return the tools in a shorter time and in particular can perform rapid idle strokes.
  • variable displacement pump delivers abruptly within its actuating time with maximum nominal pressure, so that a maximum adjustment speed of the controlled implements is achieved.
  • the delivery pressure of the pump which is higher by a design-dependent differential pressure, is placed on the actuator of the pump, which in turn leads to the delivery pressure of the Pump rises.
  • the feedback means that the pump is set to the maximum nominal pressure within its actuating time, which is in the range of fractions of a second.
  • the blocking element in the pressure signaling line prevents the pressure medium under high pressure from flowing to the pressure medium tank against the pressure signaling direction of the load sensing system when the rapid traverse is actuated.
  • the blocking element can advantageously be a check valve or a throttle.
  • a throttle has no preferred direction in its blocking effect, it is suitable as a blocking element acting counter to the pressure signaling direction.
  • the load sensing system is effective - that is, when the rapid traverse is inactive - the throttle practically does not resist the pressure transmission within the pressure signaling line without any appreciable flow of pressure medium.
  • the throttling effect is sufficient to prevent any significant outflow of pressure medium in the opposite direction in the pressure signaling direction.
  • the further claim characterizes an advantageous further development of drive devices in which pressure scales are provided in connection with the load sensing system, each of which is connected upstream of one or more control slides of the working cylinders combined into blocks.
  • pressure compensators the control input of which is each acted upon by a corresponding load pressure, have the function that the pressure medium is only passed on at its outlet with a pressure which is higher than the load pressure by a design-related differential pressure.
  • variable pump delivers pressure medium with a delivery pressure that is higher by the design-related differential pressure than the higher of the load pressures applied to the two working cylinders, but the action of the pressure compensator that acts on the lower load pressure Working cylinder is assigned, the delivery pressure of the variable pump is reduced to a value which is higher than the load pressure by the design-related differential pressure.
  • the delivery flow is therefore supplied to both control slides with different pressures, which are both, however, at the same differential pressure above the respective load pressure. This means that both working cylinders are actuated at the adjustment speed preselected via the position of the corresponding control slide.
  • control inputs of the pressure compensators can also be acted upon by the increased control pressure acting on the control element of the variable displacement pump.
  • FIGS. 1 to 3 show circuit diagrams of three drive devices according to the invention in different embodiments.
  • FIG. 1 shows a hydraulic drive device with a load sensing system that is independent of the load pressure and is used, for example, to actuate the working cylinders (not shown) on the blade of a grader.
  • the drive device comprises a central variable displacement pump 1, which pumps the pressure medium from a tank 2 as a pressure medium reservoir into the flow line 3 with a controllable delivery pressure p F.
  • the variable displacement pump 1 is of a conventional type. To regulate the delivery pressure, it has a hydraulically actuated actuator in the form of a pressure delivery flow regulator 4, the control input of which is connected to the hydraulic pressure signaling device 5.
  • the flow line 3 branches to the three identically constructed, conventional control slides 6, which are actuated by mechanical devices. Hydraulic actuation is usually also possible.
  • a return line 7 opening into the tank 2 extends from this control slide 6.
  • Two connecting lines 8, 9 continue to lead from the control slide 6 to the corresponding (not shown) working cylinders. These connecting lines 8, 9 can be connected to the supply or return line 3 or 7 depending on the desired actuation direction of the working cylinder.
  • Each control slide 6 is also provided with a pressure signaling connection 10, via which the load pressure present on the consumer side can be tapped when the control slide 6 is actuated.
  • the branched pressure signaling line 11 of the pressure signaling device 5 is connected to the pressure signaling connections 10 of the control slide 6, which line leads to the pressure flow control device 4.
  • shuttle valves 12 are installed, with the aid of which the highest load pressure p LS present at the pressure signaling connections 10 of the individual control spools 6 is fed to the pressure-flow regulator 4 as control pressure while simultaneously actuating several control spools 6.
  • the pressure signaling line 11 is also connected to the return line 7 via a tank connecting line 13.
  • the load sensing systems described above with pressure signaling devices 6 are common St.dT and are widely used in mobile hydraulic devices of construction machines, agricultural machinery, Industrial trucks and the like. Used.
  • the unit consisting of variable pump 1, pressure-flow controller 4 and pressure signaling device 5 has the function that the delivery pressure p F of the variable pump 1 is set so that it is a constant, design differential pressure ⁇ p LS above the highest of the load sensing pressure signaling device 5 Pressure flow controller 4 reported load pressure p LS is.
  • ⁇ p LS is in the order of 10 to 25 bar.
  • the adjustment speed proportional to the root of the pressure difference ⁇ p LS is therefore also constant and cannot be increased per se due to the system.
  • a feedback line 14 is provided between the flow line 3 and the pressure detection line 11.
  • this feedback line 14 there is a control valve 15 for opening and closing this line, which is actuated electromagnetically. Manual, hydraulic or pneumatic actuation is also possible.
  • the delivery output of the variable displacement pump 1 can be connected directly to the pressure delivery flow controller 4 of the pump 1.
  • the pressure regulator setting which is generally the maximum nominal pressure of the pump 1.
  • This automatic setting is based on the effect of the pressure flow regulator 4 of the variable displacement pump 1, namely that the delivery pressure p F is always built up by a design differential pressure ⁇ p LS higher than the load pressure p LS reported on the pressure flow regulator 4.
  • a check valve 16 is so that when the rapid traverse is actuated and the control valve 15 is switched through, no pressure medium can flow via the pressure reporting line 11, which is pressurized with the maximum system pressure, depending on the random position of the shuttle valves 12, via one of the control slide 6 or the tank connecting line 13 to the tank 2 installed in the pressure signaling direction D in front of the junction point of the feedback line 14 in the pressure signaling line 11, the blocking direction of the check valve 16 pointing counter to the pressure signaling direction D. If the rapid traverse via the control valve 15 is not actuated, the feedback line 14 and in particular the check valve 16 are ineffective, since in the load sensing pressure message in the pressure reporting line 11 an oil flow only flows from the control slide valve 6 to the pressure / flow rate controller 4.
  • two separate control slide blocks 17, 18 are each connected in parallel hydraulically Control slide 6.6 'provided.
  • the blocks 17, 18 are each constructed essentially in accordance with the exemplary embodiment according to FIG. 1.
  • the same components are provided with the same reference symbols (if necessary with the addition of an apostrophe). To avoid repetitions, only the differences from the exemplary embodiment according to FIG. 1 are explained:
  • each control slide block 17, 18 is provided on the input side with a pressure compensator 19, 19 'in the branching supply line 3.
  • These pressure compensators 19, 19 ' have control inputs which are acted upon by the load pressure present on the outlet side.
  • the task of the pressure compensators 19, 19 ' is to throttle the flow rate through the feed line 3 to such an extent that the pressure on the output side of the pressure compensator 19, 19' is a constant differential pressure above the load pressure present at its control input, regardless of the input pressure.
  • This differential pressure is preferably selected in accordance with the differential pressure of the load sensing system.
  • the pressure signal line 11 is also branched towards the two control slide blocks 17, 18 (line branches 11, 11 ') in accordance with the flow line 3, a further shuttle valve 20 being arranged at the branching point.
  • the control valve is a branch valve 21 which divides the feedback line 14 into two partial branches 22, 23 on the part of the pressure-flow regulator 4. These each open into the two branches 11, 11 'of the pressure reporting line in relation to the pressure reporting direction D before the shuttle valve 20.
  • stub lines 24, 24 ' are provided from the two branches 11, 11' of the pressure signal line to the control inputs of the pressure compensator 19, 19 '.
  • check valves 16, 16' are again provided.
  • the pressure compensator 19 in this spool block 17 remains ineffective.
  • the delivery pressure of the variable displacement pump 1 is passed to the pressure delivery line controller 4 via the feedback line 14, the two branch branches 22, 23 and the section of the pressure detection line 11 leading to the pressure delivery flow controller 4, so that the variable displacement pump 1 - as described - brings the maximum delivery pressure within fractions of a second within its control time.
  • this pressure is supplied via the two branches 11, 11 'of the pressure signal line and the stub lines 24, 24' to the two pressure compensators 19, 19 ', so that these become inoperative, since from the supply line 3 to the pressure compensators 19, 19' as well only the delivery pressure can act.
  • the flow rate thus passes the pressure compensators 19, 19 'without throttling and thus without any significant pressure loss.
  • FIG. 3 essentially corresponds to that shown in FIG. 1 with the difference that a pressure compensator 19 is connected upstream of each control slide 6. Otherwise, the same reference numerals designate the same components, so that a repeated description of these components is unnecessary.
  • a branch valve 21 is provided in the feedback line 14, which divides the feedback line 14 into two partial branches 22, 23 on the part of the pressure-flow regulator 4.
  • Partial branch 22 opens directly into the pressure signaling line 11 of the signaling device 5.
  • the second partial branch 23 branches via branch lines 25 to the control inputs of the pressure compensators 19.
  • a connecting branch 26 to the spool-side branches of the pressure signaling line 11 is provided between the branch lines 25.
  • both in the branch lines 25 and in the connecting branches 26 are each before the junction of the connecting branches 26 installed in the branch lines 25 check valves 27, 28, the blocking direction of which points counter to the pressure signaling direction D.
  • variable displacement pump 1 When the rapid traverse is actuated by a corresponding actuation of the branch valve 21, the output of the variable displacement pump 1 is in turn fed via the feedback line 14, its partial load 22 and the pressure signaling line 11 to the pressure flow regulator 4 of the variable displacement pump 1, so that the latter delivers the maximum delivery pressure.
  • This is placed simultaneously on the branch 23 and the branch lines 25 on the control inputs of the pressure compensators 19, so that these - as already described above - become ineffective.
  • the check valves 28 are provided in the connecting branches 26 so that the maximum delivery pressure cannot escape via the connecting branches 26 to the tank 2.
  • the check valves 27 shut off the branch lines 25 against the pressure detection direction D, so that the load pressure applied to the control slide 6 is reliably fed to the control inputs of the pressure compensators 19.

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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)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
EP93100534A 1992-03-28 1993-01-15 Lastdruckunabhängige, hydraulische Antriebsvorrichtung für Arbeitsgeräte an Baumaschinen Revoked EP0563514B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4210252A DE4210252C1 (enrdf_load_stackoverflow) 1992-03-28 1992-03-28
DE4210252 1992-03-28

Publications (2)

Publication Number Publication Date
EP0563514A1 EP0563514A1 (de) 1993-10-06
EP0563514B1 true EP0563514B1 (de) 1996-05-22

Family

ID=6455337

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93100534A Revoked EP0563514B1 (de) 1992-03-28 1993-01-15 Lastdruckunabhängige, hydraulische Antriebsvorrichtung für Arbeitsgeräte an Baumaschinen

Country Status (3)

Country Link
EP (1) EP0563514B1 (enrdf_load_stackoverflow)
AT (1) ATE138439T1 (enrdf_load_stackoverflow)
DE (2) DE4210252C1 (enrdf_load_stackoverflow)

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DE4307872C2 (de) * 1993-03-12 2001-05-17 Orenstein & Koppel Ag Lastdruckunabhängige Steuerung der Geschwindigkeit von hydraulischen Stellelementen
DE4406318A1 (de) * 1994-02-26 1995-08-31 Rexroth Mannesmann Gmbh Regeleinrichtung für eine Hydropumpe
FR2744497B1 (fr) * 1996-02-07 1998-04-03 Rexroth Sigma Dispositif de distribution hydraulique multiple
DE19821808A1 (de) 1998-05-15 1999-11-25 Daimler Chrysler Ag Mobilhydraulik-Ventilanordnung
DE19930618A1 (de) * 1999-07-02 2001-01-04 Mannesmann Rexroth Ag Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
GB2352275B (en) * 1999-07-17 2004-02-18 Agco Gmbh & Co Hydraulic system for utility vehicles
DE102014215549A1 (de) * 2014-08-06 2016-02-11 Robert Bosch Gmbh Hydrostatischer Antrieb

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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
KR920010875B1 (ko) * 1988-06-29 1992-12-19 히다찌 겐끼 가부시기가이샤 유압구동장치
JPH0374605A (ja) * 1989-08-16 1991-03-29 Komatsu Ltd 作業機シリンダの圧油供給装置

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EP0563514A1 (de) 1993-10-06
DE4210252C1 (enrdf_load_stackoverflow) 1993-09-02
ATE138439T1 (de) 1996-06-15
DE59302645D1 (de) 1996-06-27

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