EP0053323A1 - Système de transmission hydrostatique comprenant une pompe variable et plusieurs utilisateurs - Google Patents

Système de transmission hydrostatique comprenant une pompe variable et plusieurs utilisateurs Download PDF

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Publication number
EP0053323A1
EP0053323A1 EP81109744A EP81109744A EP0053323A1 EP 0053323 A1 EP0053323 A1 EP 0053323A1 EP 81109744 A EP81109744 A EP 81109744A EP 81109744 A EP81109744 A EP 81109744A EP 0053323 A1 EP0053323 A1 EP 0053323A1
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EP
European Patent Office
Prior art keywords
pressure
line
control
valve
consumer
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
EP81109744A
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German (de)
English (en)
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EP0053323B1 (fr
Inventor
Alfred Krusche
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Linde GmbH
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Linde GmbH
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Publication date
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    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • 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
    • E02F9/2221—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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20523—Internal combustion engine
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple 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
    • F15B2211/30—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
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid 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
    • F15B2211/35—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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40546—Flow control characterised by the type of flow control means or valve with flow combiners
    • 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
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back 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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid 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
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/60—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
    • F15B2211/60—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
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief 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
    • F15B2211/6058—Load sensing circuits with isolator 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
    • F15B2211/615—Filtering 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • 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
    • F15B2211/76—Control of force or torque of the output member

Definitions

  • the invention relates to a hydrostatic drive system with a preferably adjustable pump, in the case of an adjustable pump whose setting member is connected to a pump control piston which is displaceable in a pump control cylinder and whose position is determined by a pressure medium controlled by means of a servo control valve, the drive system having a plurality of consumers of hydrostatic energy and a delivery line between the pump and these consumers as well as a return line leading to a container and switching elements, whereby several consumers are connected to the delivery line emanating from the pump, each via a delivery branch line originating from the delivery line and each by means of an arbitrarily actuatable switching element are connectable to the pump.
  • the invention relates to a hydrostatic drive system for a construction machine, in particular for an excavator, in which the consumer has one or more cylinders for lifting the boom, at least one cylinder for actuating the bucket, at least one further cylinder for kinking the arm, at least another consumer can be a motor for the chassis and / or at least one other consumer can be a hydraulic motor for pivoting the excavator.
  • the pump emits a delivery line, from which branch lines each lead to an arbitrarily actuated control valve, the branch lines emerging from these control valves leading to the individual consumers.
  • the individual control valves are usually combined to form a block control device, the individual sections of which form the control valves to the individual branch lines.
  • the pump is only regulated depending on the delivery pressure in the delivery line.
  • the delivery flow flowing to the individual consumers is only arbitrarily controlled by opening the respectively associated control valve to a greater or lesser extent. Any repercussions that result from changes in the working pressure in a consumer must be compensated for by the operator through control interventions.
  • the invention has for its object to provide a drive system in which several consumers can be acted upon from one pump at the same time and the flow leading to each individual consumer can be set arbitrarily, with changes in pressure caused by loading on a consumer , do not affect other consumers, but despite the parallel connection to each consumer, the pressure medium flows with the pressure determined by the load of the respective consumer with the arbitrarily selected current.
  • an adjustable parallel circuit throttle point is arranged in each branch line, the adjusting member each of these parallel circuit throttle points on one side is acted upon by the pressure in the delivery line or delivery branch line and on the other side by a control pressure and a compression spring (or a tension spring on the first-mentioned side) and the control pressure on all of these setting elements is also the same and the side of the adjusting elements acted upon by the control pressure are connected to a common control pressure line.
  • the control pressure is not the same at all setting elements of the throttling points, but the control pressure at the individual setting elements is set depending on the speed of movement of the pistons in the individual cylinders, so that different throttling effects result at the individual throttling points depending on the different control pressures , depending on the different piston speeds in the working cylinders.
  • the setting elements of all parallel throttle points are acted upon by the same control pressure. It may be expedient that this control pressure acting on all setting elements of the parallel connection throttle points is the same control pressure which also influences the setting element of the adjustable pump.
  • the control pressure can be obtained in an expedient embodiment according to the invention in that a branch line is connected to each line between a parallel connection throttle point and the associated consumer and all these branch lines are connected to the control pressure line, with one opening to the total control pressure line in each branch line Check valve is arranged, with the result that the pressure prevailing at the consumer with the highest pressure in each case acts via the open check valve on the total control pressure line and thus the adjusting elements of all parallel connection throttle points, while all other check valves in the other control branch lines remain closed with the result that that the lower consumer pressures have no effect on the parallel connection throttle points.
  • a hydrostatic drive system for excavators has become known, in which the switching element in the branch line leading to a consumer is designed as an arbitrarily adjustable measuring throttle point, the pressure drop at this measuring throttle point acting on the pump adjusting element and regulating the flow rate of the pump so that it is arbitrary the measuring throttle point ge given width at this measuring throttle point, a predetermined pressure drop always occurs.
  • the application of the basic features of this invention is particularly advantageous in such a hydrostatic drive system, i.e. there is a particularly advantageous embodiment of a hydrostatic drive system, in particular for excavators or similar machines, if the control system described above is combined with a measuring throttle with the system with parallel throttle points according to the invention.
  • the claim 4 relates to such an appropriate combination.
  • the specified arrangement with a collective return line also allows a different, expedient refinement in that a prestressed pressure accumulator is connected to this collective return line. It can thereby be achieved that the interior of the pump is kept under the pretensioning pressure of the accumulator, so that the suction is facilitated with high flow velocities.
  • the volume of the pressure accumulator is expediently chosen such that changes in the drive system at a given time n the oil volume given can be compensated for the whole, that is to say that the storage take up the volume can, even if simultaneously a plurality of working cylinder side and piston rod in the pressure chamber with Are pressurized and vice versa.
  • a particularly expedient embodiment results when all the parallel circuit throttle points assigned to a consumer are combined in one control unit. That is to say, both the parallel connection throttle point in the line which is the conveying line in one direction of movement and the parallel circuit throttle point in the line which is conveying line in the other direction when moving are combined in one control unit. The same applies if several consumers are combined in a consumer group. It is particularly expedient if this control unit is attached directly to the consumer. It is already known to install control units, specifically solenoid valves, directly to the consumer. However, since control units of the type mentioned here are not known, it is also not known to arrange them directly on the consumer.
  • a particularly expedient embodiment results if, in the control unit, not only the parallel connection throttle point but also the measuring throttle point or Parallel circuit throttling points and measuring throttling points are combined and preferably attached to the assigned consumer.
  • a particularly simple embodiment of the parallel connection throttle points is obtained if, as is known, the parallel connection throttle point is provided with a valve slide body, which is also the adjusting element, on the end face of which the pressure in the delivery line and on the rear side the control pressure and the compression spring act.
  • this can be achieved particularly expediently in connection with the parallel connection throttle points of the invention in that a controlled throttle point, preferably a controlled pressure relief valve, is provided in the return line, the control taking place as a function of the pressure in the delivery line, so that when the pressure in the delivery line drops below a predetermined pressure level due to the advance of the consumer, this pressure the throttle point or the pressure relief valve in the return line in
  • Direction to the closed position controls with the result that the flowing current is throttled and thus the consumer is prevented from overtaking the intended speed of movement.
  • the consumer makes unintentional movements when the line leading to the consumer becomes depressurized, for example as a result of a line break.
  • a check valve is arranged in the delivery line in the immediate vicinity of the consumer, which closes when the pressure in the pressure space connected to the delivery line becomes greater than the pressure in the delivery line.
  • Such pipe break fuse - check valves are always required or at least useful, if the consumer can perform a movement under power and can result in unwanted movement in the opposite direction of a danger. This applies, for example, to excavators when lifting the boom, while when lowering it is more important that the return movement can be controlled by throttling the drain line.
  • This operating condition which triggers the connection is preferably a specific, predetermined pressure difference between the delivery line and the associated control pressure line, this pressure difference being smaller than the pressure difference intended at the measuring throttle.
  • the Da means that if / measurement throttle point is arbitrarily given a certain width and the pump delivery flow is not sufficient, even when the pump is fully swung out, to achieve the intended pressure drop at the measurement throttle point and this pressure drop becomes smaller than a planned limit value, the interconnection device responds and connects the control pressure lines and the delivery lines to one another, preferably first connects the control pressure lines and then the delivery lines to one another.
  • This type of control has two major disadvantages, namely that the power that is taken up by power take-offs, for example other pumps, compressors or alternators, is not recorded by the controller.
  • the power to which the controller adjusts must therefore be so much less than the power that a maximum of all power take-offs can absorb at the same time.
  • the drive power installed in the primary energy source cannot normally be consumed, and the primary energy source therefore almost always runs in an unfavorable part-load mode.
  • Another disadvantage arises from the coupling of the two pumps in such a way that they always pivot back to the same extent. If two movements are carried out at the same time, which overlap each other, and the controller intervenes in this operating state, the overlaid resulting direction of movement is changed.
  • the slewing gear is switched on when lifting, the controller intervenes in the acceleration phase and swivels both pumps back by the same amount in the direction of a smaller stroke volume per revolution.
  • the targeted direction of movement changes and the operator must intervene in a corrective manner.
  • both pumps swivel in the direction of a larger stroke volume per revolution due to the decreasing delivery pressure.
  • the ratio of the two consumer speeds changes again and the targeted direction is changed again.
  • regulators which act as a control variable based on the speed of the Start the output shaft of the primary energy source or the drive shaft of the pump and determine whether this speed corresponds to a speed that is predetermined, for example, by the respective setting of the primary energy source, for example the injection pump of a diesel engine. If the speed of the drive shaft falls below the specified limit due to overloading of the primary energy source, the limit load controller intervenes and regulates the pump or pumps to a smaller stroke volume per revolution and thus less torque consumption. This system also records power consumption on power take-offs.
  • the combination with the device according to the invention is particularly advantageous and expedient in such a way that a second pressure relief valve is connected to the control pressure line leading to the servo control valve controlling the setting of the pump setting element, the response pressure of which is set so much lower than the response pressure of the pressure relief valve connected to the delivery line (whereby in the case of a circuit with such a pressure drop the intended pressure drop at the measuring throttle must be taken into account) that the pressure relief valve immediately reducing the control pressure at the servo control valve opens before the pressure in the delivery line has reached such a value that this connected pressure relief valve opens.
  • This has the consequence that the pump is reduced to a smaller stroke volume per revolution and thus a smaller flow rate before the pressure relief valve connected to the delivery line responds.
  • control devices which are acted upon by the delivery pressure of the pump and act on their setting member in such a way that the pump is set to a lower stroke volume per revolution with increasing delivery pressure.
  • These devices are so far known only in a closed circuit and in such a way that the delivery pressure of the pump is preselected with the arbitrarily given setting of an actuator and thus the moment occurring at the consumer or the force occurring is predetermined. With these facilities, energy losses can be reduced.
  • the device with a control pressure line is used by several consumers, which can be arbitrarily connected in parallel to one another, pressure regulation being effected by a valve, the valve slide of this valve on the one hand by an arbitrarily actuatable control pressure transmitter and on the other hand, is acted upon by the pressure of the consumer, so that when the control pressure transmitter is actuated, an equilibrium state is established on the valve slide between the control pressure transmitter pressure and the pressure in the line which is pressurized and leads to the consumer. If the pressure in this line leading to the consumer, which is pressurized, drops, the valve is opened further, so that a larger current flows to the consumer and the pressure at the consumer is increased due to the expected consumer detection.
  • This valve can also be used arbitrarily a setting given a control pressure transmitter arbitrarily a certain pressure occurring at the consumer can be preselected - also here presupposed that with increasing flow rate, the force reaction at the consumer increases.
  • the pressure control is effected by a valve with the advantage that this device can be connected to the line system according to the invention with the delivery line emanating from the pump, a return line and a control pressure line leading to the control pressure acting on the servo control valve of the pump .
  • this control unit can be connected / attached directly to the consumer and additionally contain suction check or pipe rupture protection valves and pressure relief valves, in which case the control pressure line is also given to the line via a check valve.
  • the purpose of these devices is a regulation to constant, arbitrarily selectable pressure and thus constant force or constant moment. These devices can also reduce energy losses.
  • the pumps 3 and 4 are driven by the internal combustion engine 1 by means of the shaft 2.
  • the actuator 5 of the pump 3 is connected to a pump actuating piston 6 which is displaceable in a pump actuating cylinder 7 and divides it into two pressure chambers 8 and 9.
  • the pump 3 feeds into a delivery line 12, from which the pressure chamber 9 is acted on via branch lines 13 and 14, in which a spring 11 is arranged.
  • the pressure on the pressure chamber 8 is controlled by a hydraulically controlled servo control valve 10.
  • the pump 4 feeds into a delivery line 15.
  • the setting member 16 of the pump 4 is connected to a pump actuating piston 17 which is displaceable in a pump actuating cylinder 18 and divides it into two pressure chambers 19 and 20, a spring 21 being arranged in the pressure chamber 20.
  • This pressure chamber 20 is connected to the delivery line 15 via a branch line 321 and a further branch line 22.
  • the application of pressure to the pressure chamber 19 is controlled by a hydraulically controlled servo control valve 23.
  • Both pumps 3 and 4 are arranged in a common housing 24.
  • Two further pumps 25 and 26 configured as constant pumps are driven by the shaft 2 (the pump 26 can also be driven by a power take-off of the internal combustion engine 1 in another embodiment).
  • a branch conveyor line 28 branches off from the conveyor line 12 and leads to a partial control unit 27 in which the conveyor branch line 28 is divided into two partial lines 29 and 30.
  • Each of the two sub-lines 29 and 30 leads to a single-edge control slide 31 and 32, respectively, the single-edge control slide 31 being hydraulically controlled and by a pressure control line 33 from one arranged in the driver's cab of the excavator, arbitrarily operable control pressure transmitter 92 is pressurized.
  • the hydraulically controlled single-edge control slide 32 is acted upon by control pressure via a pressure transmitter control line 34, the pressure transmitter control line 34 leading to another control pressure transmitter 93, which is also arranged in the driver's cab and can be actuated arbitrarily.
  • the single-edge control slide valve 31 and 32 each act as a measuring throttle point, through which a throttled current is conducted from the partial line 29 to the line 35 or from the partial line 30 to the line 36.
  • the single-edge control slide 31 connects the line 35 to the return line 37 and in the same way in the other position, the single-edge control slide 32 connects the lines 36 and 38, the two return lines 37 and 38 leading together to the return branch line 39.
  • the line 35 leads to a parallel connection throttle point 40 with a slide body 41, the rear side of which is acted upon by a spring 42 and by the control pressure present in a control pressure line 53.
  • a line 43 extends from the parallel connection throttle point 40 and separates into two lines 44 and 45, each of which leads to a pressure chamber 46 or 47 of the two working cylinders 48 and 49 which are connected in parallel to one another and are provided on the excavator for "lifting".
  • the line 36 leads to a parallel connection throttle point 50 with a slide body 51, the rear side of which is acted upon by a spring 52 and by the pressure present in a control line 53.
  • a line goes from the parallel connection Drosstelle 50 53, which is divided into two lines 54 and 55, of which line 54 leads to pressure chamber 56 of working cylinder 48 and line 55 leads to pressure chamber 57 of working cylinder 49.
  • a check valve 58 opening towards the working cylinder 48 is arranged in the line 54.
  • a line 59 is connected to line 54, which leads to a controlled pressure relief valve 60, the outlet of which leads via line 61 and line 62 to the return partial line 39.
  • a line 63 is connected to the line 54, in which a suction check valve 64 is arranged, which on the other hand is connected to the line 62.
  • a check valve 68 is arranged in line 44 and a line 65 is connected between it and working cylinder 48, in which a suction suction check valve 66 is arranged, which is also connected to line 62. Furthermore, a line 69 is connected to the line 44 between the check valve 68 and the working cylinder 48, which leads to a hydraulically controlled pressure relief valve 70, the outlet line 71 of which is connected to the line 62.
  • the control pressure chamber of the pressure relief valve 70 is connected via line 72 to the line 54 upstream of the check valve 58 and in the same way the control pressure chamber of the pressure relief valve 60 is connected via line 73 to the line 44 upstream of the check valve 68.
  • valves 58, 64, 60, 70, 68, 66 are combined in a control unit 74 which is attached directly to the working cylinder 48.
  • An analogous valve arrangement is provided in the control unit 75, which is attached to the working cylinder 49.
  • a line 76 is connected to the line 53, which leads to a check valve 77.
  • a line 78 which leads to a check valve 79, is also connected to line 43.
  • the two check valves 77 and 79 are connected to the partial control pressure line 80, to which the pressure spaces behind the slide bodies 41 and 51 are also connected.
  • a relief check valve 94 opening towards the line 35 is arranged in the slide body 41.
  • a relief check valve 95 opening towards the line 36 is arranged in the slide body 51:
  • the control pressure line 80 leads to an overall control pressure line 81 to which a control pressure branch line 83 is connected.
  • a branch line 82 is connected to the delivery line 12.
  • the two branch lines 82 and 83 lead to an overall control unit 85, from which a return line 84 emerges, which is connected to the return line 39.
  • the overall control unit 85 is attached to the working cylinder 86, which serves to actuate the bucket of the excavator.
  • the overall structure of the circuit of the overall control unit 85 is analogous to the sum of the partial control unit 27 and the control unit 74.
  • Two single-edge control slides 86 and 87 are provided, of which the single-edge control slide 86 via a pressure transmitter control pressure line 88 is acted upon by an arbitrarily actuable control pressure transmitter 90, which is arranged in the vicinity of the control pressure transmitters 92 and 93, which act on the pressure transmitter control pressure lines 33 and 34. Accordingly, the single-edge control slide 87 is controlled by a pressure transmitter control pressure line 89, which in turn also leads to an arbitrarily actuatable control pressure transmitter 91 leads, which is arranged in the vicinity of the control pressure transmitter 90, 92, 93.
  • the two single-edge control spools 86 and 87, each acting as a measuring throttle point, are followed by a parallel connection throttle point 96 b or 97, behind which a branch line leading to the control pressure partial line 83, each with a check valve 100 or 101, branches off at a connection point 98 or 99;
  • the return line 39 leads to a main return line 102, which leads directly into the housing 24 of the pumps and to which a prestressed storage tank 103 is connected.
  • Branch lines 104, 105, 106 branch off from the delivery line 15 starting from the pump 4, of which the delivery branch line 104 to a working cylinder 107 for the buckling of the dipper stick and the delivery branch line 105 to a hydraulic motor 108 for driving and the delivery branch line 106 to a hydraulic motor 109 for swinging the excavator.
  • the overall control units 110 and 111 are constructed in the same way as the overall control unit 85.
  • the control pressure sensor 120 is acted upon and the single-edge control spool 113 is acted on by a control pressure transmitter 121 and the single-edge control spool 114 is acted on by a control pressure transmitter 122 and the single-edge control spool 115 is acted on by a control pressure transmitter 123.
  • the return partial lines 124 and 125 starting from the overall control units 110 and 111 all lead to a return branch line 126 which is connected to the main return line 102. Likewise, the return line 127.
  • the lines 106 and 127 are connected to a four-port / three-position directional valve 128 which is hydraulically controlled by the two control pressure transmitters 129 and 130 and optionally either one port 131 of the hydraulic motor 109 with the delivery line 106 and the other port 132 of the hydraulic motor 109 connects to the return line 127 or, conversely, connects the delivery line 106 to the connection 132 and the return line 127 to the connection 131.
  • an additional control unit 133 is provided, which is attached directly to the hydraulic motor 109 and in which two check valves 134 and 135 and two pressure relief valves 136 and 137 and connections 138 and 139 are provided for a control pressure line 140, between the control pressure line 140 and the connections 139 and 138 check valves 141 and 142 are arranged.
  • the total control pressure line 81 assigned to the pump 3 continues in the control pressure line 150, which leads to a branch line 152, in which a throttle point 153 is arranged and which leads to a pressure chamber of the hydraulically controlled servo control valve 10.
  • the opposite pressure chamber is connected via branch line 154 to line 14, which is in the delivery with the delivery pressure line 12 of the pump 3 is acted upon.
  • a current regulator 155 is also connected to line 150, the output of which leads into the interior of housing 24 of pumps 3 and 4.
  • a pressure relief valve 157 is connected to line 152 between throttle point 153 and the control pressure chamber of servo control valve 10.
  • a line 158 extends from the line 13 and leads to a connection 159 of the servo control valve 10, so that pressure medium conveyed through this line 158 and the connection 159 by the pump 3 via the delivery line 12, the lines 13, 158 and the connection 159 can be guided into the pressure chamber 8 by the servo control valve 10.
  • a connecting line 160 in which a circulation throttle point 161 is arranged (this line 160 with the throttle point 161 can be omitted if the servo control valve 10 is designed with a sufficiently large negative overlap, so that when in.
  • Neutral position standing servo control valve 10 constantly leads a partial flow via lines 12, 13, 158 and connection 159 to the pressureless container 156 or preferably into the interior of the housing 24 of pumps 3 and 4.
  • This solution has the advantage that the current regulator 155 does not additionally must be set to the current flowing through the circulation throttle 161).
  • control pressure sub-lines 162, 163 and 164 proceed, which are connected to a total control pressure line 165, which continues in line 166, to which line 167 is connected to throttle point 168 and to which the current regulator 169 is connected.
  • the one from the throttle position 168 outgoing line 170 leads to a pressure chamber of the hydraulically controlled servo control valve 23, the opposite pressure chamber of which is connected to the line 22 via the connection 171.
  • a pressure relief valve 172 is connected to line 170.
  • connection 173 of the servo control valve 23 is connected to the line 321 via the line 174.
  • a connecting line 175 which contains a circulation throttle 176 (the same applies here as said with regard to the line 160 and throttle point 161).
  • An interconnection control line 177 is connected to the overall control pressure line 81 and an interconnection control line 178 is connected to the overall control pressure line 165, these two control lines leading to the interconnection unit 179.
  • a four-port / two-position valve 182 is arranged, which is hydraulically controlled and has two control pressure chambers on each side, each control pressure chamber on the one hand being assigned an equally large control pressure chamber on the other side, but it is not necessary for the two to open control pressure chambers lying on one side have the same diameter.
  • a branch line 180 leads to the interconnection unit 179, and likewise a branch line 181 leads from the delivery line 15 to the interconnection unit 179.
  • the two lines 180 and I81 are connected to the four-position / two-way valve 182 such that in the drawn position of the same.
  • the lines 180 and 181 are connected to one another and in the other position of the same these lines are blocked.
  • the control pressure lines 177 and 178 are connected to the two other connections of the four-position / two-way valve 182 in such a way that in the drawing Position of the valve spool, the lines 177 and 178 are interconnected.
  • two pressure relief valves 184 and 184 are also arranged, of which the pressure relief valve 184 serves to protect the delivery line 12 and is connected to this via line 180, while the pressure relief valve 185 serves to protect the delivery line 15 and via line 181 this is connected.
  • the line 180 acted upon by the delivery pressure of the pump 3 and the line 177 leading from the control pressure assigned to the pump 3 are connected on opposite sides to pressure chambers of the same size, and the line 181 acted upon by the delivery pressure of the pump 4 and that of the pump 4 is also connected assigned control pressure line 178 connected to opposite sides of equal pressure chambers of the four / two-way valve 182 connected in such a way that both lines 177 and 178 acted upon by the control pressure are connected to the side on which the compression spring 186 is arranged.
  • the constant pump 25 draws in via line 187 from the housing 24 of the pumps 3 and 4 and feeds into a line 188 which leads to an adjustable throttle point 189, the setting member 190 of which is operatively connected to the setting member of the internal combustion engine 1.
  • a pressure limiting valve 193 is connected to the line 188 via a line 191 / in which a filter 192 is arranged, the outlet of which is connected to a line 194 which in turn is connected to the line 195 which is behind the throttle point 189 forms the continuation of line 188, and the leads to further consumers no longer shown in the drawing.
  • a controlled pressure relief valve 196 is also connected to line 194, the control pressure of which is determined via line 197 by the pressure upstream of throttle point 189.
  • the line 198 emanating from the pressure relief valve 196 leads to a throttle point 199 and the line 200 emanating from it leads to the tank 156 via a pressure relief valve 201 Pressure before the pressure relief valve 196 keeps constant. The important thing is that the pressure drop at the throttle point 189 controls the pressure relief valve 196, which in turn controls the flow to the throttle point 199.
  • a limit pressure control line 203 branches off from the line 198 between the pressure limiting valve 196 and the throttle point 199 and a second limit pressure line 204 branches off from the line 200.
  • the line 203 branches into two lines 205 and 206, which each open into a control pressure chamber of the servo control valve 10 and 23, respectively, on the same side on which this is acted upon by the delivery pressure of the associated pump 3 or 4.
  • Two lines 207 and 208 branch off from line 204, each of which leads to the other side of the hydraulically controlled servo control valve 10 and 23, respectively, which is acted upon by a spring.
  • the mode of operation is as follows: when the internal combustion engine 1 is running and the pumps 3, 4, 25, 26 are driving and all control pressure transmitters 93.,. 92, 91, 90, 120, 121, 122, 123, 130, 129 are not actuated, the Pumps in the zero stroke position and do not deliver. No consumer is charged. Now the Control pressure transmitter 92 is actuated, the single-edge control slide 31 is actuated and opens so that it establishes a connection between the delivery line 12 and the line 44 to the working cylinder 48, the parallel connection throttle point 40 opening. At the same time, the check valve 79 opens, so that the line 80 and thus the line 81 is also pressurized.
  • the pressure in line 35 and thus the pressure in line 43 and thus also the pressure in line 78 and in line 80 and in line 81 is lower than the pressure in the delivery branch line 28 and the delivery line 12.
  • the pressure in the delivery line 12 acts via lines 13, 14 and 154 on one side of the servo control valve 10 and the pressure in the control pressure line 81 acts via lines 150, 151, 152 on the other side of this servo control valve, on which the spring also acts.
  • the spring is designed such that the servo control valve 10 responds to a specific pressure difference between the pressures in the lines 154 and 152, for example to a pressure difference of 20 bar.
  • the servo control valve 10 of the pump 3 is set by means of the servo control valve 10 via the pump actuating piston 6 in such a way that it promotes a flow of flow which produces this predetermined pressure drop at the single-edge control slide valve 31 acting as a measuring throttle point. That is, if the setting of the single-edge control spool 31 is changed by changing the setting of the control pressure transmitter 92, the pump 3 is also set to a different flow rate and specifically to such a flow rate that the predetermined pressure drop arises at this single-edge control spool 31, which acts as a measuring throttle point.
  • the parallel connection choke points 40, 50, 96 or 97 and 116 or 117 have the following effect:
  • this control line system also acts on the rear sides of the slide bodies 41 and 241, but different pressures prevail in the line 35 and 240 in front of this slide body, a different throttling effect is generated at the throttle points 40 and 96, ie in the case of the consumer 48, 49, which generates the lower pressure, this parallel connection throttle point 40 generates such a large pressure drop that before this parallel connection throttle point 40 in line 35 and thus in line 28 and thus in line 12 and thus in line 82, such a high pressure is generated , as required by the consumer 86, with the parallel connection throttle 96 due to the pressure in line 240 under the effect of the control pressure in line 83, a correspondingly lower throttling effect is generated, since the consumer pressure acting on the slide body 241 is large enough to fully open the parallel connection throttle point 96, so that no pressure drop occurs at this.
  • This arrangement of the parallel connection throttle points, which are acted upon together by the same control pressure on the rear side, has the essential advantage that if two consumers could take up a larger current than the pump 3 delivers, the current supplied by the pump 3 on the two consumers - in the present case on the one hand the consumers 48, 49 on the other hand the consumer 86 - is divided proportionally to the opening width of the throttle columns.
  • the check valves 58 and 68 act as pipe break protection. This means that if there is a leak in line 12 or line 28 or line 82 or another line connected to this and the pressure escapes, the consumer is connected by actuating the associated control pressure transmitter and thus opening the associated single-edge valve , cannot sink back under load. For example, when lifting under load and thus the working cylinders 48 and 49 are under pressure and the line 12 breaks, the check valve 58 closes. The liquid present in the working cylinders 48 and 49 is thus enclosed and clamped in, so that no unwanted movement occurs can, since the pressure relief valves 60 and 70 are also closed, since there is no pressure in the lines 53 and 43 and thus the pressure relief valves 60 and 70 are not open.
  • the pistons in the working cylinders 48 and 49 want to lead this current, they draw in liquid with the result that the pressure in the line 44 and thus in the line 43 drops.
  • the pressure in the control pressure chamber of the pressure relief valve 60 is also reduced via the line 73, so that it closes to the extent that the pressure is reduced, that is to say that a throttling effect is generated in the pressure relief valve 60, which reduces the pressure in the pressure chambers 56 and 57 flowing current throttles, so that the speed of movement of the pistons in the working cylinders 48 and 49 is braked by this throttling effect.
  • the pressure relief valves 60 and 70 are also controlled by the pressure in the lines 59 and thus 54 and 69 and thus 44.
  • the pressure relief valves 60 and 70 thus also act as a safeguard against impermissibly high pressure in the working cylinders 48 and 49. That is, if too high a pressure occurs as a result of overloading or intermittent loading, opens either the pressure relief valve 60 or the pressure relief valve 70, depending on the direction of the load due to the excessively high pressure, so that these pressure relief valves 60 and 70 also act as overload relief pressure relief valves, even when none of the control pressure transmitters 92 and 93 is actuated.
  • the associated suction check valve 64 or 66 opens so that the respective opened suction check valve 64 or 66 and line 62 and partial return line 39 line 102 can be reloaded from container 103.
  • valves on the other side of the control unit 74 or the corresponding valves in the control unit 85 or 100 or 111 act in an analogous manner.
  • the interconnection unit 179 takes effect.
  • the spring acting on it is designed such that a certain pressure drop occurs at the single-edge control slide 31 acting as a measuring throttle point, for example a pressure drop of 20 bar.
  • the spring 186 of the four-port / two-position valve 182 is designed such that this valve opens at a lower pressure gradient, such as a pressure drop of 15 bar, between the Fordertechnisch '12 and the control pressure line 81st
  • the four-port / two-position valve 182 is designed such that when the slide body begins to move, the control lines 177 and 178 are first connected to one another, with the result that the pump 4 is pivoted out so far that the same pressure is present in the delivery line 15 as in FIG the delivery line 12, which, if no consumer is connected to the pump 4, this pressure is generated upstream of the throttle point 176.
  • the lines 180 and 181 are then connected to one another by the valve 182, so that the delivery flow of the pump 4 through the four-port / two-position valve 182 is additionally is conveyed into the delivery line 12 of the pump 3, the pump 4 now swiveling so far that it generates exactly the 'delivery flow which is required, together with the delivery flow of the pump 3, at the single-edge control slide valve 31 which acts as a measuring throttle point, the required pressure drop - to generate 1 5 bar in the given case.
  • this pressure relief valve is also installed in the interconnection unit 179, namely the pressure relief valve 184 is connected via the line 180 to the delivery line 12 and, in a corresponding manner, the pressure relief valve 185 is connected to the delivery line 15 via line 181 to protect the pump 4. Opening one of these pressure relief valves has the disadvantage that this pressure medium is used to discharge at the highest possible pressure, which means that a lot of energy is destroyed in this pressure relief valve. This is inevitable for the reduction of short pressure surges.
  • the pump 3 is assigned the pressure relief valve 157, which is set to such a low pressure that it opens when there is a pressure in the control line 81 which, in accordance with the predetermined pressure drop, at the pressure caused by the single-edge slide valve 31 or 32 or 86 or 87 given measuring throttle point is below the response pressure of the pressure relief valve 184, so that the pressure relief valve 157 opens before opening the pressure relief valve 184 and thereby limits the maximum possible pressure in the line 152, with the result that with a slight increase in the pressure in the line 154
  • Servo control valve 10 increases the pressure in the pressure chamber 8 of the pump actuating cylinder 7 and thereby adjusts the pump 3 to a smaller stroke and thus a smaller flow, whereby it can be expected that after this control process caused by the increase in the control pressure increases, the pressure in the delivery line 12 as a result of the reduced conveying flow is reduced and thus the An Jardinen.des pressure relief
  • the pump 4 is assigned a corresponding pressure relief valve 172, which responds to the pressure in the control pressure line 166 and opens before the pressure relief valve 185 opens.
  • the pressure relief valve 196 is set to the pressure drop at the throttle point should prevail at the intended operating speed. If this pressure drop is present, the pressure relief valve 196 is closed. If the pressure drop is smaller than intended, the pressure relief valve 196 opens and leads a current to the downstream throttle point 199, at which a pressure drop now also arises and this pressure drop is applied via lines 203 and 204 as a pressure difference to the two sides of both servo control valves 10 and 13 . It is thereby achieved that when both pumps 3 and 4 deliver to at least one consumer and the limit load control 230 intervenes, both pumps 3 and 4 are proportional.
  • both pumps 3 and 4 are thus adjusted in the direction of a smaller stroke volume per revolution, but only to the extent that the pressure drop at the throttle point 199 and the pressure drop at the single-edge slide valve acting as a measuring throttle of the consumer which is switched on keep the balance. If one of the pumps 3 or 4 tends to run ahead, it immediately receives a counter signal, which indicates the two pressure drops. aligns again. In this way, the Pressure drop at the single-edge control spool acting as a measuring throttle of the two consumers is kept the same, with the result that the absolute quantity changes at these single-edge control spools acting as measuring throttle, but not the ratio of the quantities to one another and thus the ratio of the movement speeds to one another.
  • the pressure relief valve 202 serves to protect the constant pump 25.
  • the bypass pressure relief valve 193 additionally protects the constant pump 25 in the event that the throttle point 189 is too far or completely closed. In this case, the oil flows via line 188, line 191, pressure relief valve 193 into line 194.
  • the pump 26 is used, which delivers to the steering device of the excavator, which is no longer shown in the drawing.
  • the return from the steering device still has sufficient pressure to charge the memory 103.
  • the line 239 coming from the steering device is connected to the line 102.
  • the pump 25 sucks from the housing 24, in which the two pumps 3 and 4 are arranged, in order to ensure that an exchange of pressure medium takes place in the housing 24.
  • the pressure medium flowing back from the steering through line 239 flows, as far as it is excess, via pressure-limiting valve 201 into pressure-free container 156.
  • the volume of the reservoir 103 is dimensioned such that leakage losses and volume differences on the two sides of the pistons can be compensated for even when several consumers are actuated in the same direction.
  • FIG. 11 shows a modified embodiment of a partial control unit.
  • the partial control unit 270 corresponds to the partial control unit 27 with the only difference that instead of the two single-edge control spools 31 and 32, which form the two measuring throttle points in the partial control unit 27, a single four-port / three-position valve 231 is provided, which is by means of the two control pressure transmitters 92 and 93 via the control pressure lines 33 or 34 can be controlled and in the neutral position shown in the drawing closes the branch conveyor line 28 and connects the lines 35 and 36 to one another and in a controlled position the branch conveyor line.
  • 28 connects to line 35 and at the same time connects line 36 to return line 39 and in the other modulated position connects branch delivery line 28 to line 36 and at the same time connects line 35 to return line 39.
  • the additional control unit 133 has a slightly different structure and a different mode of operation than the control units 85 or 110 or 111.
  • the four-port / three-position valve 128 is not only controlled by the two control pressure transmitters 129 and 130, but it is also controlled on the side that is controlled opposite side is acted upon by the delivery pressure in the line 131 or 132 leading to the consumer, so that when valve 128 is actuated via one of control pressure transmitters 129 or 130, a state of equilibrium is established at valve slide of valve 128. If the pressure at the consumer drops, the valve is opened further so that a larger current flows to the consumer and the pressure at the consumer is increased due to the consumer detection.
  • FIG. 12 shows a modified embodiment of an interconnection unit.
  • the interconnection unit 279 essentially corresponds to the interconnection unit 179, the four-port / two-position valve 282 essentially corresponding to the valve 182.
  • a branch line 180 originating from the delivery line 12 and opposite thereto an interconnection control line 177 originating from the control line 81, and a branch line 181 originating from the delivery line 15 is also connected and to the opposite one Control pressure chamber, an interconnection control line 178 starting from the control pressure line 166 is connected.
  • valve 183 on the side opposite the compression spring 286 has a third control pressure chamber 234 which is connected via a line 233 to the limit load control element 230 in such a way that when the limit load control element 230 acts on the servo control valves 10 and 23 Signal, by which the actuator 5 of the pump 3 and the actuator 16 of the pump 4 are adjusted in the direction of a smaller stroke volume, prevents the interconnection valve 282 from opening.
  • a pressure is thus exerted on the additional pressure space 234 by the limit load control element 230 via the control line 233, which pressure loads the valve member of the interconnection valve 282 in the direction of the closed position.
  • the interconnection unit 279 should only connect the two delivery lines 12 and 15 of the two pumps 5 and 4 to one another if one of the two pumps is set to the maximum possible flow rate and the pressure drop at the single-edge control slide 32 acting as a measuring throttle point drops below the intended value. However, this pressure drop at the single-edge slide valve 31 acting as a measuring throttle point also becomes then less when the limit load controller 230 intervenes, with the result that the stroke volume of the pump 4 or 5 is set to a smaller value than the pressure drop at the measuring throttle point.

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)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Fluid Gearings (AREA)
  • Operation Control Of Excavators (AREA)
  • Control Of Transmission Device (AREA)
EP81109744A 1980-11-24 1981-11-17 Système de transmission hydrostatique comprenant une pompe variable et plusieurs utilisateurs Expired EP0053323B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3044144 1980-11-24
DE19803044144 DE3044144A1 (de) 1980-11-24 1980-11-24 Hydrostatisches antriebssystem mit einer einstellbaren pumpe und mehreren verbrauchern

Publications (2)

Publication Number Publication Date
EP0053323A1 true EP0053323A1 (fr) 1982-06-09
EP0053323B1 EP0053323B1 (fr) 1986-04-16

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ID=6117399

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EP81109744A Expired EP0053323B1 (fr) 1980-11-24 1981-11-17 Système de transmission hydrostatique comprenant une pompe variable et plusieurs utilisateurs

Country Status (9)

Country Link
US (1) US4425759A (fr)
EP (1) EP0053323B1 (fr)
JP (1) JPS57116965A (fr)
CS (1) CS238619B2 (fr)
DE (1) DE3044144A1 (fr)
ES (1) ES8300394A1 (fr)
FI (1) FI70075C (fr)
PL (1) PL139197B1 (fr)
YU (1) YU267581A (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2548290A1 (fr) * 1983-06-14 1985-01-04 Linde Ag Installation hydraulique comportant une pompe et au moins deux equipements utilisateurs d'energie hydraulique alimentes par cette pompe
DE3504744A1 (de) * 1984-02-13 1985-08-14 Koehring Co., Brookfield, Wis. Druckausgeglichenes hydraulikventil
DE3634728A1 (de) * 1986-10-11 1988-04-21 Rexroth Mannesmann Gmbh Ventilanordnung zum lastunabhaengigen steuern mehrerer gleichzeitig betaetigter hydraulischer verbraucher
DE3716200A1 (de) * 1987-05-14 1988-11-24 Linde Ag Steuer- und regeleinrichtung fuer ein hydrostatisches antriebsaggregat und verfahren zum betreiben eines solchen
WO1995032364A1 (fr) * 1994-05-21 1995-11-30 Mannesmann Rexroth Gmbh Systeme de commande pour au moins deux consommateurs hydrauliques
RU2122660C1 (ru) * 1996-12-25 1998-11-27 Государственный научно-исследовательский тракторный институт "НАТИ" Гидрораспределитель
WO2000006915A1 (fr) 1998-07-24 2000-02-10 Mannesmann Rexroth Ag Circuit hydraulique
WO2005093263A1 (fr) * 2004-03-09 2005-10-06 Bucher Hydraulics Gmbh Systeme de commande hydraulique

Families Citing this family (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3422165A1 (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
JPS61175301A (ja) * 1985-01-29 1986-08-07 Uchida Yuatsu Kiki Kogyo Kk ロ−ドセンシング形マルチプルコントロ−ル弁のタンデム回路装置
DE3605312A1 (de) * 1985-02-22 1986-08-28 Linde Ag, 6200 Wiesbaden Schieberventil
US4719753A (en) * 1985-02-22 1988-01-19 Linde Aktiengesellschaft Slide valve for load sensing control in a hydraulic system
DE3535771A1 (de) * 1985-10-07 1987-04-09 Linde Ag Hydrostatischer antrieb mit mehreren verbrauchern
US4724673A (en) * 1986-06-30 1988-02-16 Vickers, Incorporated Power transmission
DE3640236A1 (de) * 1986-11-25 1988-06-01 Rexroth Mannesmann Gmbh Anordnung zum erzeugen hoher hydraulischer druecke
AU603907B2 (en) * 1987-06-30 1990-11-29 Hitachi Construction Machinery Co. Ltd. Hydraulic drive system
DE3883690T2 (de) * 1987-10-05 1994-03-17 Hitachi Construction Machinery Hydraulisches Antriebssystem.
DE3733679A1 (de) * 1987-10-05 1989-04-13 Rexroth Mannesmann Gmbh Steuerschaltung fuer einen mit einer verstellpumpe betriebenen hydraulischen kraftheber
DE3733677A1 (de) * 1987-10-05 1989-04-13 Rexroth Mannesmann Gmbh Lastunabhaengige steuereinrichtung fuer hydraulische verbraucher
KR920006546B1 (ko) * 1988-03-23 1992-08-08 히다찌 겐끼 가부시기가이샤 유압구동장치
US5186000A (en) * 1988-05-10 1993-02-16 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for construction machines
EP0366815B1 (fr) * 1988-05-10 1993-11-24 Hitachi Construction Machinery Co., Ltd. Unite d'entrainement hydraulique pour engin de construction
EP0341650B1 (fr) * 1988-05-12 1993-11-18 Hitachi Construction Machinery Co., Ltd. Système d'entraînement hydraulique pour véhicule de construction à chenilles
FI83256C (fi) * 1988-07-27 1991-06-10 Tampella Oy Ab Anordning foer anvaendning av hydrauliska manoeveranordningar i en bergborrsbom.
EP0411151B1 (fr) * 1989-02-20 1994-07-06 Hitachi Construction Machinery Co., Ltd. Circuit hydraulique pour machines
US4986071A (en) * 1989-06-05 1991-01-22 Komatsu Dresser Company Fast response load sense control system
JPH0792090B2 (ja) * 1989-06-19 1995-10-09 株式会社小松製作所 油圧回路
US5271227A (en) * 1990-05-15 1993-12-21 Kabushiki Kaisha Komatsu Seisakusho Hydraulic apparatus with pressure compensating valves
DE69109250T2 (de) * 1990-07-05 1995-09-21 Hitachi Construction Machinery Co., Ltd., Tokio/Tokyo Hydraulische antriebssystem und ventilanordnung.
JPH04136507A (ja) * 1990-09-28 1992-05-11 Komatsu Ltd 油圧回路
JP3115887B2 (ja) * 1990-09-28 2000-12-11 株式会社小松製作所 クローズドセンタ・ロードセンシングシステムにおけるポンプの吐出容積の可変回路
EP0516864B2 (fr) * 1990-11-26 2001-12-12 Hitachi Construction Machinery Co., Ltd. Systeme d'entrainement hydraulique et soupapes d'inversion de sens
JPH04210101A (ja) * 1990-11-30 1992-07-31 Komatsu Ltd 油圧回路
JP3006777B2 (ja) * 1991-03-15 2000-02-07 株式会社小松製作所 ロ−ドセンシング油圧回路
US5305604A (en) * 1991-05-10 1994-04-26 Techco Corporation Control valve for bootstrap hydraulic systems
US5226290A (en) * 1991-05-10 1993-07-13 Techco Corporation Bootstrap hydraulic systems
US5249420A (en) * 1991-05-10 1993-10-05 Techco Corporation Control valve for bootstrap hydraulic systems
WO1993011364A1 (fr) * 1991-11-25 1993-06-10 Kabushiki Kaisha Komatsu Seisakusho Circuit hydraulique pour l'actionnement de plusieurs activateurs et soupapes de compensation de pression et detecteurs de pression de charge maximum associes
AU3617193A (en) * 1992-02-25 1993-09-13 Techco Corporation Control valves having parasitic leakage orifices
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
JPH06123123A (ja) * 1992-05-22 1994-05-06 Hitachi Constr Mach Co Ltd 油圧駆動装置
KR0149708B1 (ko) * 1994-07-25 1998-10-15 석진철 선회 토르크 제어장치
US5499503A (en) * 1994-09-22 1996-03-19 Iowa Mold Tooling Company, Inc. Hydraulic swing circuit
CA2279435A1 (fr) * 1999-07-30 2001-01-30 Michael Alexander Duff Actionneur lineaire
US6382595B1 (en) * 2000-07-26 2002-05-07 Schlumberger Technology Corporation Differential hydrostatic transmission system
CN101144490B (zh) * 2003-08-20 2010-06-23 株式会社小松制作所 油压驱动控制装置
JP2005098455A (ja) * 2003-09-26 2005-04-14 Mitsubishi Heavy Ind Ltd 産業機械の油圧制御装置
CN103244501B (zh) * 2013-05-14 2016-07-13 三一汽车起重机械有限公司 一种液压控制阀组、液压系统和工程机械
US9222493B2 (en) 2013-10-14 2015-12-29 Brian Riskas Statically stable walking machine and power system therefor
DE102018202148B3 (de) * 2018-02-12 2019-03-07 Hawe Hydraulik Se Hydraulikventilverband mit Zwangsschaltung und Mobilhydrauliksystem

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2159766A1 (de) * 1971-12-02 1973-06-07 Rexroth Gmbh G L Druckregelung mit verstellpumpe
DE2320679A1 (de) * 1972-05-05 1973-11-22 Parker Hannifin Corp Umsteuerschieber
DE2260457A1 (de) * 1972-12-11 1974-06-12 Wabco Westinghouse Gmbh Stromteilereinrichtung fuer ein hydrauliksystem mit mehreren unterschiedlich belastbaren verbrauchern

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1728270U (de) 1956-05-16 1956-08-16 Albert Griesemer Universal-spannlasche.
DE1755065U (de) 1957-06-15 1957-10-31 Jakob Mueller Wandregal.
US2892312A (en) * 1958-01-27 1959-06-30 Deere & Co Demand compensated hydraulic system
DE1801137U (de) 1959-10-07 1959-11-26 Waldemar Busch & Co Kommanditg Schwimmspielzeug.
GB1126873A (en) * 1964-09-22 1968-09-11 Sperry Rand Corp Improvements in hydraulic supply and control systems
LU52175A1 (fr) * 1965-10-21 1966-12-19
DE1952034U (de) 1966-05-10 1966-12-22 Constructa Werke G M B H Haushaltmaschine mit einem in der gehaeusewandung befestigten schlauchanschlussstueck.
DE1755065A1 (de) * 1968-03-26 1971-10-14 Linde Ag Steuereinrichtung fuer den hydrostatischen Antrieb eines Fahrzeuges mit einer hydraulisch angetriebenen Betriebseinrichtung
DE1728270A1 (de) * 1968-09-19 1972-03-09 Bosch Gmbh Robert Hydraulische Regelanlage
DE1801137A1 (de) * 1968-10-04 1970-04-16 Bosch Gmbh Robert Hydraulikanlage mit einer verstellbaren Pumpe
DE1952034A1 (de) * 1969-10-15 1971-04-22 Linde Ag Steuereinrichtung fuer eine hydraulische Anlage und Ventil hierzu
DE2038414B2 (de) * 1970-08-01 1977-03-17 Salzgitter Maschinen Ag, 3320 Salzgitter Regelvorrichtung fuer einen hydrostatischen fahrantrieb und einem hydrostatischen arbeitsgeraeteantrieb eines laderfahrzeuges mit gleisketten
DE2146585C3 (de) * 1971-09-17 1980-08-28 G.L. Rexroth Gmbh, 8770 Lohr Hydrostatischer Antrieb für Haspelanlagen
BE792618A (fr) 1971-12-13 1973-06-12 Caterpillar Tractor Co Ensemble de valves de commande hydrauliques.
BE794408A (fr) * 1972-01-24 1973-05-16 Clark Equipment Co Transmission hydrostatique pour vehicules a quatre roues motrices
DE2413295B2 (de) * 1974-03-20 1978-02-02 Robert Bosch Gmbh, 7000 Stuttgart Regeleinrichtung fuer eine verstellbare pumpe
DE2440251A1 (de) * 1974-08-22 1976-03-04 Linde Ag Schaltung fuer zwei kreislaeufe zur vereinigung der foerderstroeme beider pumpen
DE2700803C2 (de) * 1977-01-11 1982-10-28 Sauer Getriebe KG, 2350 Neumünster Regelungssystem für eine Antriebseinrichtung
CA1104033A (fr) 1977-02-24 1981-06-30 Commercial Shearing, Inc. Dispositif de commande a compensation de pression et de debit, a couple constant et element de detection de viscosite
DD133698A1 (de) * 1977-11-28 1979-01-17 Stefan Hein Grenzlastregelung fuer hydrostatische antriebe
DE2754430A1 (de) * 1977-12-07 1979-06-13 Bosch Gmbh Robert Steuereinrichtung fuer mindestens zwei verstellbare pumpen
DE2810611C3 (de) * 1978-03-11 1982-03-04 Eberhard 5427 Bad Ems Heine Fertigteil zur Unterstützung von Fensterbänken
DE2823559A1 (de) * 1978-05-30 1979-12-06 Linde Ag Steuer- und regeleinrichtung fuer ein hydrostatisches getriebe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2159766A1 (de) * 1971-12-02 1973-06-07 Rexroth Gmbh G L Druckregelung mit verstellpumpe
DE2320679A1 (de) * 1972-05-05 1973-11-22 Parker Hannifin Corp Umsteuerschieber
FR2183825A1 (fr) * 1972-05-05 1973-12-21 Parker Hannifin Corp
DE2260457A1 (de) * 1972-12-11 1974-06-12 Wabco Westinghouse Gmbh Stromteilereinrichtung fuer ein hydrauliksystem mit mehreren unterschiedlich belastbaren verbrauchern

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
Hydraulics & Pneumatics, Band 29, No. 10, Oktober 1976 Industrial Publishing Corp. Cleveland (US) A. MYERS: "Can the Efficiency o Open Circuit Hydraulic Systems be Increased?" seiten 148 bis 152 * seite 152, figur 7 * *
Olhydraulik und Pneumatik, Report 1976, Oktober 1976 Krausskopf Verlag Mainz (DE) Lasthalteventile * seite 57 * *

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2548290A1 (fr) * 1983-06-14 1985-01-04 Linde Ag Installation hydraulique comportant une pompe et au moins deux equipements utilisateurs d'energie hydraulique alimentes par cette pompe
DE3504744A1 (de) * 1984-02-13 1985-08-14 Koehring Co., Brookfield, Wis. Druckausgeglichenes hydraulikventil
DE3504744C2 (fr) * 1984-02-13 1993-03-18 Husco International Inc., Waukesha, Wis., Us
DE3634728A1 (de) * 1986-10-11 1988-04-21 Rexroth Mannesmann Gmbh Ventilanordnung zum lastunabhaengigen steuern mehrerer gleichzeitig betaetigter hydraulischer verbraucher
DE3716200A1 (de) * 1987-05-14 1988-11-24 Linde Ag Steuer- und regeleinrichtung fuer ein hydrostatisches antriebsaggregat und verfahren zum betreiben eines solchen
WO1995032364A1 (fr) * 1994-05-21 1995-11-30 Mannesmann Rexroth Gmbh Systeme de commande pour au moins deux consommateurs hydrauliques
US5752384A (en) * 1994-05-21 1998-05-19 Mannesmann Rexroth Ag Control arrangement for at least two hydraulic consumers
RU2122660C1 (ru) * 1996-12-25 1998-11-27 Государственный научно-исследовательский тракторный институт "НАТИ" Гидрораспределитель
WO2000006915A1 (fr) 1998-07-24 2000-02-10 Mannesmann Rexroth Ag Circuit hydraulique
US6499296B1 (en) 1998-07-24 2002-12-31 Mannesmann Rexroth Ag Hydraulic circuit
WO2005093263A1 (fr) * 2004-03-09 2005-10-06 Bucher Hydraulics Gmbh Systeme de commande hydraulique

Also Published As

Publication number Publication date
CS238619B2 (en) 1985-12-16
YU267581A (en) 1984-02-29
FI70075C (fi) 1986-09-12
DE3044144A1 (de) 1982-09-09
JPS57116965A (en) 1982-07-21
PL233434A1 (fr) 1982-08-02
US4425759A (en) 1984-01-17
FI813748L (fi) 1982-05-25
ES507204A0 (es) 1982-11-01
FI70075B (fi) 1986-01-31
EP0053323B1 (fr) 1986-04-16
PL139197B1 (en) 1986-12-31
JPH0249405B2 (fr) 1990-10-30
ES8300394A1 (es) 1982-11-01

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