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EP0760908B1 - Systeme de commande pour au moins deux consommateurs hydrauliques - Google Patents

Systeme de commande pour au moins deux consommateurs hydrauliques Download PDF

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Publication number
EP0760908B1
EP0760908B1 EP95919366A EP95919366A EP0760908B1 EP 0760908 B1 EP0760908 B1 EP 0760908B1 EP 95919366 A EP95919366 A EP 95919366A EP 95919366 A EP95919366 A EP 95919366A EP 0760908 B1 EP0760908 B1 EP 0760908B1
Authority
EP
European Patent Office
Prior art keywords
pressure
load
valve
control arrangement
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.)
Expired - Lifetime
Application number
EP95919366A
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German (de)
English (en)
Other versions
EP0760908A1 (fr
Inventor
Martin Schmitt
Thomas Weickert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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Publication of EP0760908A1 publication Critical patent/EP0760908A1/fr
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Anticipated expiration legal-status Critical
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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—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
    • 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
    • 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
    • F15B2211/25—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
    • F15B2211/30525—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
    • F15B2211/315—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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—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
    • F15B2211/60—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
    • F15B2211/6055—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
    • F15B2211/635—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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention is based on a control arrangement for at least two hydraulic consumers, the characteristics from the generic term of the claim.
  • Such a control arrangement is known from EP 0 566 449 A1. It includes a variable displacement pump that can be controlled so that it produces a pressure at its outlet which is around a certain one Differential amount above the highest load pressure of all hydraulic Consumer lies.
  • load-sensing control there is a load-sensing controller that works in the sense of a Reduction of the stroke volume of the variable pump from the pump pressure and in the sense of increasing the stroke volume of the pump from highest load pressure and can be acted upon by a compression spring. The difference between the pump pressure and the highest load pressure corresponds to the force of this compression spring.
  • the pressure compensator downstream of each adjustable metering orifice keeps the pressure drop across the orifice so that the amount of pressure medium flowing to a hydraulic consumer solely from the opening cross section of the metering orifice and not from Load pressure of the consumer or depends on the pump pressure.
  • the pressure compensators ensure that in one case, in which the hydraulic pump is adjusted to the maximum stroke volume has been and the pressure medium flow is not sufficient to the specified Maintain pressure drop across the orifice plates, the pressure balances of all actuated hydraulic consumers in Closing direction can be adjusted so that all pressure medium flows to individual consumers reduced by the same percentage become. Because of this load-independent flow distribution (LUDV) all operated consumers move with one speed reduced by the same value as a percentage.
  • LUDV load-independent flow distribution
  • a load sensing controlled variable displacement pump is usually also with a pressure control, through which the maximum possible pump pressure is specified and equipped with a power control, which determines the maximum output that can be output by the pump.
  • Pressure regulation and capacity regulation are the load sensing regulation overlaid.
  • the aim of the invention is to provide a control arrangement with the features to further develop from the preamble of claim 1, that for a first hydraulic consumer another rapid movement is possible when a second hydraulic Consumer hit a stop and hit that stop to be held.
  • this aim is achieved by a control arrangement, the features from the preamble of claim 1 has and in accordance with the characterizing part of the claim 1 the load-sensing controller with a common control only the first and second hydraulic consumers from a limit pressure below the maximum pressure of one only from the load pressure of the first hydraulic consumer dependent pressure can be applied.
  • the invention is initially based on the idea that not the maximum pressure is necessary to stop the second consumer to keep or with the second consumer the necessary Generate clamping force.
  • a limit pressure is therefore used specified below which the pressure in the load signaling line can not lie if the second hydraulic consumer is operated.
  • This limit pressure is sufficient for the Pump creates a pump pressure that works properly of the second hydraulic consumer. Lies the load pressure of the first hydraulic consumer above that Limit pressure and will not be a third hydraulic consumer a higher load pressure is actuated, so is the pressure in the load signaling line from the load pressure of the first hydraulic consumer dependent.
  • This load pressure is usually below the set by the pressure control maximum pressure, so that only with a much larger pressure medium flow than at maximum pressure the power control appeals.
  • the load sensing controller at a single control of the second hydraulic consumer also above the limit pressure from the load pressure of the second consumer is acted upon.
  • control arrangement is therefore designed in accordance with claim 3 in such a way that that the load-sensing controller also from the limit pressure of higher of the two load pressures of the first and third hydraulic Consumer can be acted upon.
  • control arrangement Constantly set the limit pressure.
  • a limit pressure only in certain situations.
  • the valve can e.g. arbitrarily adjustable by hand, each after which device with the second hydraulic consumer is operated. If this actuates e.g. a spoon on an excavator, so no limit pressure may be provided.
  • a pair of pliers is mounted on the boom of an excavator is operated by the second hydraulic consumer, so the Limit pressure to be effective.
  • valve according to claim 5 Independently or depending on that is to be operated by the second hydraulic consumer device it favorable if the valve according to claim 5 depending on different controls of the hydraulic consumers is adjustable.
  • the limit When the first is activated together hydraulic consumer and the second hydraulic consumer the limit is effective. With a common control of the first hydraulic consumer and a third hydraulic consumer or with a common control of the second hydraulic consumer and a third hydraulic pressure may not provide the limit pressure be.
  • the limit pressure is at one Pressure valve adjustable.
  • a particularly simple construction is possible if as Pressure valve a pressure relief valve is used with which the pressure in a rear pressure chamber of a load signaling valve is limited to the limit pressure.
  • This load signaling valve is between the load signal line and one with the load pressure of the first hydraulic loadable section of a Switched consumer line and has a control piston on the one with a rear printing surface on the rear Pressure space adjoins and of the one prevailing in this pressure space Pressure in the closing direction and on a front pressure surface with the load pressure of the first hydraulic consumer in the opening direction is acted upon.
  • the rear pressure chamber connected to the load signaling line via a choke.
  • the pump pressure is in each case one certain amount above the load pressure of the first hydraulic Consumer when the pressure relief valve is effective and if the load pressure is above that through the pressure relief valve set limit pressure.
  • the latter is usually the Case.
  • the pump pressure is also above the limit pressure, but below the maximum pressure if the load pressure of the first hydraulic consumer is less than the limit pressure is and if, as stated in claim 17 is, the load signaling valves combined with the pressure compensators in this way are that the load signal line via the control piston of the pressure compensator, the hydraulic consumer with the highest load pressure assigned, can be acted upon with this highest load pressure is, if a construction according to EP 0 566 449 A1 is used.
  • a particularly advantageous development of an inventive Control arrangement is characterized according to claim 12, that the pump pressure through a between the flow path to the second hydraulic consumer and the load signaling line switched pressure reducing valve can be limited.
  • This pressure reducing valve ensures that with simultaneous control of the first and second hydraulic consumers in the load signaling line has at least the limit pressure. It leaves it on the other hand to that the load reporting line with one above the Load pressure of the first hydraulic consumer or a third hydraulic consumer can be.
  • the pump pressure is around that on the load-sensing controller set difference over the pressure in the Load reporting line.
  • a first concrete version with a pressure reducing valve can this according to claim 13 in series with the load signaling valve second hydraulic consumer. Is a such a series connection is structurally difficult to accomplish, so it is cheaper, according to claim 14, the load signaling valve and arrange the pressure reducing valve parallel to each other and to The pressure reducing valve takes effect the connection between one with the load pressure of the second hydraulic consumer actable section of a consumer line and the To block the load reporting line. This can e.g. through a 2/2-way valve happen. However, it can also be cheap to lock according to claim 15, a movable valve body of the load signaling valve to block.
  • the metering orifices can be used independently directly by hand or remotely controlled e.g. electric or be adjusted electro-hydraulically.
  • the orifice 13 is assigned to a first hydraulic consumer 15, which as double-acting differential cylinder is formed.
  • the second metering orifice 14 is a second hydraulic consumer 16 assigned, which is also a double-acting differential cylinder is.
  • Each orifice 13 or 14 is the speed part of a Proportional directional valve, to which also a directional part 17 or 18 heard that the metering orifice is connected downstream.
  • a 2-way pressure compensator 19 or 20 is connected, the one control piston movable in a bore 21 22 has. This is in the opening direction of the pressure compensator its front end face 23 acted upon by the pressure the metering orifice 13 or 14 in a section 24 one of the Metering orifice to channel 25 or 36 leading to the directional part prevails. With its rear end face 26, which is the same size the control piston borders as the front end face 23 is 22 to a rear pressure chamber 27, which is independent of the current position of the control piston 22 continuously with a load signaling line 28 is connected.
  • the load signaling line 28 connects all holes 21 with each other, in which they, as in the versions according to Figures 1 and 2, in an annular groove 29 or, as in the embodiment according to FIG. 5, in which the control piston the pressure compensator in an additional housing in the directional control valve inserted sleeve, opens into several holes 30.
  • the connection between the annular groove 29 or the bores 30 and the rear pressure chamber 27 is over the control piston 22 is produced, there being a nozzle 31 in the connection, whose cross section is approximately 0.5 mm2.
  • the control piston 22 of a pressure compensator 19 or 20 can have two end positions take, in the one end position, which in the Figures 1 and 2 is shown and the by a weakly biased, compression spring 32 located in the pressure chamber 27 is predetermined is a connection between section 24 and one between the pressure compensator 19 or 20 and the directional part 17 or 18 located section 33 of the channel 25 and 36 interrupted is.
  • the connection between the channel sections 24 and 33 completely open and section 24 of channel 25 or 36 is through holes 34, 35 in the control piston with the load signaling line 28 connected.
  • the load reporting line 28 leads to a control unit 40, which the variable displacement pump 10 is constructed.
  • This control unit 40 is on known and shown in more detail in Figure 4. It comprises three 3/2-way directional control valves 41, 42 and 43.
  • the Pump 10 ultimately from an actuating cylinder 44 with a Actuating piston 45, which is provided on one side with a piston rod 46 is.
  • a measuring piston 47 is accommodated in the piston rod against the force of a compression spring 48 on a one-armed lever 49 acts.
  • the effective lever length for the force of the compression spring is constant while the effective lever length for the force of the Measuring piston 47 depends on the swivel angle of the pump 10. The volumetric flask is acted upon by the pump pressure.
  • the pump pressure also prevails in a pressure chamber of the piston rod Actuating cylinder 44, in which a compression spring 50 is accommodated, which the adjusting piston 45 in the direction of an increase in Swing angle applied to the pump 10.
  • the valve 43 is used to regulate the output of the variable pump 10. It has a connection which is connected to the tank 11 via a line 51. Another connection is on the pressure line 12.
  • the third Connection that can be connected to the first or the second connection is connected to a first connection of the valve 42, with which the pump pressure is limited to a maximum value.
  • a second connection of the valve 42 is located on the piston rod side Pressure chamber of the actuating cylinder 44 on the pressure line 12.
  • the third connection of the valve 42 is with its first or second connection connectable and permanently with one connection the so-called load sensing valve 41 connected.
  • a slide of the valve, not shown 43 is pressed by the compression spring 48 against the lever 49 and in the sense of increasing the swivel angle of the pump 10 charged.
  • a slide, not shown, of the valve 42 is by a compression spring 52 in the sense of increasing the Swivel angle and the pump pressure in the sense of a reduction of the pivoting angle of the pump 10.
  • a no closer shown slide of the load sensing valve 41 finally will increase the swivel angle of the pump 10 from a compression spring 53 and from in the load reporting line 28 prevailing pressure and in the sense of a reduction in the swivel angle acted upon by the pump pressure.
  • On the slide of valve 41 there is a balance of forces when between the pump pressure and there is a difference in the pressure in the load reporting line 28, which corresponds to the force of the spring 53. Usually that lies Difference at about 20 bar.
  • Balance on the valve spool 42 prevails when the pump pressure generates a force that the Force of the spring 52 corresponds. Usually lies with one Balance the pump pressure in the range of 350 bar.
  • the load reporting line 28 is connected to the tank line 51 via a Nozzle 54 connected.
  • a pressure relief valve on the load signaling line 55 connected which is set to a pressure of about by the amount by which the pump pressure and in the load signaling line 28 prevailing pressure with a balance on the slide of the load-sensing valve 41 differ below that on the valve 42 maximum pressure set.
  • the pressure drop across them is therefore always the same and corresponds to the difference between the pump pressure and the Load pressure of the consumer 15. Since the load pressure of the consumer 15 pending in the entire load reporting line, it also prevails in the rear pressure chambers 27 of the two pressure compensators 19 and 20th
  • the second hydraulic one may now Consumer 16 are operated, initially assumed be that the load pressure of the second hydraulic consumer 16th is lower than the load pressure of the first consumer 15. Of the The load pressure of the second hydraulic consumer can therefore do not fully open the pressure compensator 20. Its control piston takes rather now a control position in which the pressure on its front face 23 acts, you can see once from the Force from the compression spring 32, just as large as the pressure in Pressure chamber 27, that is the load pressure of the first consumer 15 corresponds, and in which there is no connection between the space in front the end face 23 and the load signaling line 28. Consequently is the pressure drop across the orifice 14 as large as over the orifice 13. The pressure in section 24 of channel 36 drops via the pressure compensator 20 to the load pressure of the second hydraulic Consumer 16 from.
  • the highest load pressure is in each case in the load reporting line 28 of an actuated hydraulic consumer.
  • the Pump 10 generates a pump pressure that is approximately 20 bar above this highest load pressure. If now e.g. by the consumer 16 a clamping device is actuated with which an object packed and then by operating another hydraulic Pump should be transported, so the pump pressure reach the maximum value set on valve 42, so that even with a small flow rate, the power control would respond to the pump and only a small speed of the consumer 15 would be possible.
  • the maximum pressure is there from e.g. 350 bar far above the pressure leading to a fixed Clamping the object to be transported is necessary and e.g. is in the range of 150 bar.
  • the pump pressure in such a case does not go to the maximum pressure is now at the control arrangements shown according to the invention provided that when the first consumer 15 and of the second consumer 16, which performs a clamping function the load reporting line at a limit pressure below the maximum pressure 28 of one only from the load pressure of the first hydraulic Consumer 15 dependent pressure can be applied.
  • the pressure compensator 19 via a 2/2-way valve 60 to a pressure relief valve 61 can be connected, e.g. to a value of 150 bar is set.
  • the directional control valve 60 blocks in its rest position the connection between the pressure chamber 27 and the Pressure relief valve 61. In the other switching position, in the it e.g.
  • the directional control valve 60 can be brought by applying a control pressure can, it establishes a connection between the pressure chamber 27 the pressure compensator 19 and the inlet of the pressure relief valve 61 forth.
  • the directional control valve 60 is then in its second switching position brought when the first consumer 15 and the second consumer 16 can be operated simultaneously.
  • the load pressure of the first hydraulic consumer can Pressure compensator 23 fully open and the control piston 22 in to maintain its upper end position in the view according to FIG. 1.
  • the pressure compensator 20 is also complete open, because in its rear pressure chamber 27 the pressure in the Load reporting line 28 prevails and since there is no load 16 Pressure medium flows, the front end face 23 of the control piston the pressure compensator 20 is acted upon by the pump pressure. Except over the metering orifice 13 now flows over a small amount of pressure medium the nozzle 35 of the pressure compensator 20, the load reporting line 28 and the Nozzle 35 of the pressure compensator 19 to the first consumer 15. Between the two nozzles 35, that is to say in the load reporting line 28 a pressure that is 20 bar above the load pressure of the first hydraulic consumer 15 lies. Via the nozzle 31 of the pressure compensator 19, this pressure falls on the pressure relief valve 61 set and prevailing in the pressure chamber 27 of the pressure compensator 19 Pressure off.
  • the load pressure of the first hydraulic consumer 15 is lower than the pressure set at the pressure relief valve 61, thus, as tests have shown, builds up in the Load reporting line 28 also one above that on the pressure relief valve 61 set, but far below the maximum pressure lying pressure on.
  • valve combination consisting of a directional valve and there is a fixed pressure relief valve
  • an electromagnet Pressure relief valve used to in the pressure chamber 27 of the Pressure compensator 19 to set a limit pressure.
  • This solution is alternatively shown in Figure 1.
  • the pressure relief valve which is now provided with the reference number 62, designed so that when the electromagnet is switched off value above the occurring operating pressures and by driving the electromagnet to a lower one Value of e.g. 150 bar is adjusted. So it has a so-called falling characteristic.
  • the power of the electromagnet supports the pressure force that the pressure relief valve 62 opposes tries to open the force of a compression spring.
  • the falling characteristic is favorable if the switch-on time of the electromagnet is shorter than the switch-off time.
  • the magnet is arranged so that it is against the pressure force in Closing direction of valve 62 acts.
  • the closing direction of the valve 65 acts on a not shown Valve body is a weak compression spring 66.
  • the valve body in the closing direction also by an electromagnet 63 acted upon.
  • Electromagnet 63 is a pressure of e.g. 150 bar in the Load signaling line necessary to close valve 65.
  • An additional electromagnet 67 is on the rear pressure chamber 27 of the pressure compensator 20 and can be fitted with a tappet 68 block the control piston 22 of the pressure compensator 20 such that it although the connection between sections 24 and 33 of Channel 36, but not the connection of this channel to the load reporting line 28 can open.
  • the control spool is blocked Pressure compensator 20 with magnet 67 switched on.
  • the control arrangement according to FIG. 3 differs essentially in three points from the control arrangement according to Figure 2.
  • Zum the highest load pressure will not exceed that of the consumer pressure compensator assigned to the highest load, but via a Check valve 70, which opens to the load reporting line 28, in this reported.
  • each check valve 70 is the individual one Consumers with the exception of the second consumer 16 directly to the line section 33 between the respective pressure compensators and the directional part 17 connected.
  • the second difference for the execution according to Figure 2 is that a pressure reducing valve 71 now in line with the second hydraulic Consumer 16 assigned check valve 70 is arranged.
  • an electromagnet 63 acts together with the Pressure at the outlet of the pressure reducing valve 71 a movable Valve body of the valve against a strong in the closing direction Compression spring 66 acting in the opening direction so strong that the pressure reducing valve 71 at the occurring Operating pressure is open when the solenoid 63 is turned off is.
  • the control arrangement according to FIG. 3 therefore functions when the control is switched off Electromagnet 63 in the already specified above normal way.
  • the pressure reducing valve 71 is after the switching on of the electromagnet 63 to an output pressure from e.g. 150 bar is set, this pressure of 150 bar reported in the load reporting line 28, provided the highest load pressure of all other operated consumers is below 150 bar.
  • the pump pressure is then 170 bar, that on the piston of the cylinder 16 acts and generates a certain clamping force. Lies the highest load pressure of the other operated hydraulic consumers higher than 150 bar, the load reporting line 28 with this highest load pressure and the pump pressure is 20 bar above this highest load pressure.
  • Electromagnets 63 act in the opening direction of valve 71 let and the limit pressure of e.g. 150 bar by a corresponding one Adjust the preload of the compression spring 66. After turning on of the electromagnet 63 is then the valve 71 in all Operating pressures open.
  • the proportional directional control valve segment according to FIG. 5 has one Housing 80 has a valve bore 81 in which a control piston 82 is axially displaceable.
  • This control piston has a metering orifice part in the middle 13, 14 and on both sides of the metering orifice part one half each of a directional part 17.
  • a pressure compensator 19 is used, which is in a sleeve 84 contains a control piston 22 with the bores 30 already mentioned. Is located between the pressure compensator and the orifice 13 the channel section 24, between the pressure compensator 19 and the Halves of the directional part 17 each part of the channel section 33, with a load holding valve 85 in each part. A connection between the channel sections 24 and 33 can be produced over several radial bores 86 of the sleeve 84.
  • the Bores 30 go outside of an annular space between the sleeve 84 and the wall of the bore 83, in which the dashed indicated load reporting channel 28 opens twice.
  • This load reporting channel 28 is over an outer groove 87 of the control piston 22 and over one radial and one axial bore and one in this axial bore arranged nozzle 31 with the rear pressure chamber 27 permanently connected. With a completely open pressure compensator there is also through the control piston 22 through a connection between the Line section 24 and the bores 30.
  • the control piston another axial bore 34, another radial bore and another ring groove.
  • the radial bore can be as Nozzle 35 can be understood.
  • the pressure chamber 27 is in the sleeve 84 with a screw attachment closing, a pressure relief valve 62 screwed in with which limits the pressure in the pressure chamber 27 to a certain pressure can be.
  • a pressure relief valve 62 screwed in with which limits the pressure in the pressure chamber 27 to a certain pressure can be.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un système de commande pour au moins deux consommateurs (15, 16) hydrauliques, qui comprend une pompe à cylindrée variable (10) dont l'ajustement peut être modulé par un régulateur de détection de charge (41) auquel il est possible d'appliquer la pression de charge la plus élevée, par l'intermédiaire d'une conduite de signalisation de charge (28), et auquel sont superposées une régulation de pression maximale et une régulation de puissance. Ce système de commande comprend également deux diaphragmes de dosage (13, 14) mobiles, dont un premier est monté entre la pompe à cylindrée variable (10) et un premier consommateur (15) hydraulique. Le second diaphragme est monté entre la pompe à cylindrée variable (10) et un second consommateur (16) hydraulique. Le système de commande comprend en outre deux balances de pression (19, 20), dont la première est montée en aval du premier diaphragme de dosage (13) et la seconde, en aval du second diaphragme de dosage (14), et aux pistons de régulation (22) desquels on peut appliquer de la pression sur une face avant (23), d'après le diaphragme de dosage (13, 14) correspondant, dans le sens d'ouverture et sur la face arrière (26), dans la conduite de signalisation de charge (28), dans le sens de fermeture. Afin que la pression de pompage ne soit pas maximale, étant donné que lorsque les deux consommateurs (15, 16) hydrauliques fonctionnent simultanément, l'un d'entre eux est déplacé contre une butée ou exerce une fonction de serrage, il est prévu que lors d'un tel fonctionnement conjoint uniquement du premier (15) et du second (16) consommateurs hydrauliques, à partir d'une pression limite inférieure à la pression maximale, le régulateur de détection de charge (41) ne puisse être sollicité que par une pression dépendant de la pression de charge du premier consommateur (15) hydraulique.

Claims (18)

  1. Un dispositif de pilotage pour au moins deux récepteurs (15, 16) hydrauliques doté d'une pompe (10) à cylindrée variable, dont le réglage peut être modifié par un régulateur (40) à saisie de charge, lequel peut être soumis à la pression en charge maximum au travers d'une conduite (28) de saisie de charge et lequel est subordonné à des asservissements de la pression maximum et de la puissance, doté de deux diaphragmes (13, 14) de mesure réglables, desquels un premier est branché entre la pompe (10) à cylindrée variable et un premier récepteur (15) hydraulique et le deuxième entre la pompe (10) à cylindrée variable et un deuxième récepteur (16) hydraulique, et doté de deux balances (19, 20) de pression, desquelles une première est branchée derrière le premier diaphragme (13) de mesure et la deuxième derrière le deuxième diaphragme (14) de mesure et dont les tiroirs (22) de régulation peuvent être soumis sur une face (23) avant à la pression régnant derrière le diaphragme (13, 14) de mesure correspondant, dans le sens d'une ouverture, et sur une face (26) arrière à la pression de la conduite (28) de saisie de charge, dans le sens d'une fermeture, caractérisé en ce que, lors d'une commande commune exclusivement des premier et deuxième récepteurs (15, 16) hydrauliques, à partir d'un seuil de pression inférieur à la pression maximum, le régulateur (40) à saisie de charge peut être soumis à une pression qui ne dépend que de la pression en charge d'un seul récepteur (15) hydraulique, le premier.
  2. Un dispositif de pilotage conforme à la revendication n° 1, caractérisé en ce que, lors d'une commande simple uniquement du deuxième récepteur (16) hydraulique, c'est également au-dessus du seuil de pression que le régulateur (40) à saisie de charge peut être soumis à la pression en charge du deuxième récepteur (16).
  3. Un dispositif de pilotage conforme à la revendication n° 1 ou n° 2, caractérisé en ce que, lors d'une commande commune des premier, deuxième et d'un troisième récepteurs hydrauliques, ce dernier pouvant être gavé en moyen de pression par la pompe (10) à cylindrée variable au travers d'une troisième diaphragme de mesure et d'une troisième balance de pression branchée derrière ce diaphragme de mesure, le régulateur (40) à saisie de charge peut être soumis à la plus élevée des pressions en charge des premier et troisième récepteurs hydrauliques, toujours à partir du seuil de pression.
  4. Un dispositif de pilotage conforme à une revendication précédente, caractérisé en ce que, en fonction de la position d'une valve réglable (60, 62, 65, 71), le régulateur (40) à saisie de charge peut être soumis à des pressions différentes.
  5. Un dispositif de pilotage conforme à la revendication n° 4, caractérisé en ce que la valve (60, 62, 65, 71) est réglable en fonction de différents pilotages des récepteurs (15, 16) hydrauliques.
  6. Un dispositif de pilotage conforme à une revendication précédente, caractérisé en ce que le seuil de pression peut être calibré au niveau d'une valve de pression (61, 62, 65, 71).
  7. Un dispositif de pilotage conforme à la revendicatiqn n° 4 ou n° 5 ainsi qu'à la revendication n° 6, caractérisé en ce que la valve de pression (61, 62, 65, 71) peut être commutée entre les modes actif et inactif.
  8. Un dispositif de pilotage conforme à la revendication n° 7, caractérisé en ce que la valve de pression (61) est de calibre fixe et peut être basculée entre les modes actif et inactif en faisant commuter un distributeur (60).
  9. Un dispositif de pilotage conforme à la revendication n° 7, caractérisé en ce que la valve de pression (62, 65, 71) peut être modifiée à l'aide d'un solénoïde (63).
  10. Un dispositif de pilotage conforme à la revendication n° 9, caractérisé en ce que la pression calibrée au niveau de la valve de pression (62, 65, 71) est plus basse pour un solénoïde (63) traversé par un courant que pour un solénoïde sans courant.
  11. Un dispositif de pilotage conforme à une des revendications nos 6 à 10, caractérisé en ce que la conduite (28) de saisie de charge peut être connectée au travers d'une valve (19) de signalisation de charge à une section (24, 33) d'une tuyauterie (25) de récepteur, laquelle peut être soumise à la pression en charge du premier récepteur (15) hydraulique, que la valve (19) de signalisation de charge présente un tiroir (22) de commande, lequel peut être soumis sur une surface (26) de pression tournée vers l'arrière, dans le sens d'une fermeture, à la pression régnant dans une chambre (27) de pression arrière, reliée à la conduite (28) de saisie de charge au travers d'un gicleur (31), et lequel peut être soumis sur une surface (23) de pression tournée vers l'avant, dans le sens d'une ouverture, à la pression en charge du premier récepteur (15) hydraulique, et que la pression dans la chambre (27) de pression arrière peut être limitée au seuil de pression à l'aide d'un limiteur (61, 62) de pression.
  12. Un dispositif de pilotage conforme à une des revendications nos 6 à 10, caractérisé en ce que le seuil de pression peut être calibré à l'aide d'un limiteur (65, 71), de pression, lequel est branché entre l'itinéraire (12, 36) du flux vers le deuxième récepteur (16) hydraulique et la conduite (28) de saisie de charge.
  13. Un dispositif de pilotage conforme à la revendication no 12, caractérisé en ce que la conduite (28) de saisie de charge peut être connectée au travers d'une valve (70) de signalisation de charge à une section (33) d'une tuyauterie (36) de récepteur, laquelle est soumise à la pression en charge du deuxième récepteur (16) hydraulique, qu'un élément mobile de la valve (70) de signalisation de charge peut être soumis dans le sens d'une fermeture à la pression de la conduite (28) de saisie de charge et dans le sens d'une ouverture à la pression en charge du deuxième récepteur (16) hydraulique, et que le limiteur (71) de pression est disposé en série par rapport à la valve (70) de signalisation de charge.
  14. Un dispositif de pilotage conforme à la revendication n° 12, caractérisé en ce que, au travers d'une valve (20) de signalisation de charge et en contournant le limiteur (65) de pression, la conduite (28) de saisie de charge peut être connectée à une section (24, 33) d'une tuyauterie (36) de récepteur, laquelle peut être soumise à la pression en charge du deuxième récepteur (16) hydraulique, et que cette connexion peut être fermée, afin d'activer la fonction du limiteur (65) de pression.
  15. Un dispositif de pilotage conforme à la revendication°. 14, caractérisé en ce que, dans la valve (20) de signalisation de charge, un élément (22) de valve mobile peut être bloqué afin d'activer la fonction du limiteur (65) de pression.
  16. Un dispositif de pilotage conforme à la revendication n° 14 ou n° 15, caractérisé en ce que le limiteur (65) de pression est branché sur une tuyauterie (12) de pression entre la pompe (10) à cylindrée variable et les diaphragmes (13, 14) de mesure.
  17. Un dispositif de pilotage conforme à une revendication précédente, caractérisé en ce que les valves de signalisation de charge sont associées aux balances (19, 20) de pression de telle façon, que la conduite (28) de saisie de charge peut être soumise à la pression en charge maximum au travers du tiroir (22) de commande de la balance (19, 20) de pression, laquelle est dédiée à celui des récepteurs (15, 16) hydrauliques dont la pression en charge est la plus élevée.
  18. Un dispositif de pilotage conforme à la revendication n° 17, caractérisé en ce que la conduite (28) de saisie de charge est connectée à la chambre (27) de pression, laquelle se trouve au niveau de la face (26) arrière du tiroir (22) de commande, au travers du tiroir (22) de commande d'une balance (19, 20) de pression ainsi que d'un gicleur (31), lequel est prévu à l'intérieur de ou au niveau du tiroir (22) de commande.
EP95919366A 1994-05-21 1995-04-29 Systeme de commande pour au moins deux consommateurs hydrauliques Expired - Lifetime EP0760908B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4417962A DE4417962A1 (de) 1994-05-21 1994-05-21 Steueranordnung für wenigstens zwei hydraulische Verbraucher
DE4417962 1994-05-21
PCT/EP1995/001642 WO1995032364A1 (fr) 1994-05-21 1995-04-29 Systeme de commande pour au moins deux consommateurs hydrauliques

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EP0760908A1 EP0760908A1 (fr) 1997-03-12
EP0760908B1 true EP0760908B1 (fr) 1999-01-20

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US (1) US5752384A (fr)
EP (1) EP0760908B1 (fr)
JP (1) JPH10500472A (fr)
KR (1) KR970703494A (fr)
DE (2) DE4417962A1 (fr)
WO (1) WO1995032364A1 (fr)

Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19703997A1 (de) * 1997-02-04 1998-08-06 Mannesmann Rexroth Ag Hydraulischer Steuerkreis für einen vorrangigen und für einen nachrangigen hydraulischen Verbraucher
DE19828963A1 (de) 1998-06-29 1999-12-30 Mannesmann Rexroth Ag Hydraulische Schaltung
DE19831595B4 (de) * 1998-07-14 2007-02-01 Bosch Rexroth Aktiengesellschaft Hydraulische Schaltung
DE19855187A1 (de) 1998-11-30 2000-05-31 Mannesmann Rexroth Ag Verfahren und Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers
EP1088995A4 (fr) * 1999-04-26 2006-04-05 Hitachi Construction Machinery Dispositif a circuit hydraulique
DE19944835A1 (de) * 1999-09-18 2001-03-22 Rauch Landmaschfab Gmbh Vorrichtung zum Verteilen von Streugut
DE10047175A1 (de) * 2000-09-22 2002-04-11 Mannesmann Rexroth Ag Verfahren und Steueranordnung zur Ansteuerung von hydraulischen Verbrauchern
DE10058032A1 (de) * 2000-11-23 2002-05-29 Mannesmann Rexroth Ag Hydraulische Steueranordnung
US6675904B2 (en) * 2001-12-20 2004-01-13 Volvo Construction Equipment Holding Sweden Ab Apparatus for controlling an amount of fluid for heavy construction equipment
DE50309629D1 (de) 2002-03-04 2008-05-29 Bosch Rexroth Ag Ventilanordnung
DE10325296A1 (de) * 2003-06-04 2004-12-23 Bosch Rexroth Ag Hydraulische Steueranordnung
DE10325294A1 (de) 2003-06-04 2004-12-23 Bosch Rexroth Ag Hydraulische Steueranordnung
US7380491B2 (en) * 2004-01-07 2008-06-03 Bosch Rexroth Ag Flow valve and flow distributor comprising several flow valves
DE502005003090D1 (de) 2004-02-05 2008-04-17 Bosch Rexroth Ag Messblendenanordnung für ein hydraulisches stromteil- und stromsummiergerät
DE102005033222B4 (de) * 2005-07-15 2012-05-16 Bosch Rexroth Aktiengesellschaft LUDV-Ventilanordnung
DE102005055309A1 (de) 2005-11-21 2007-05-24 Bosch Rexroth Ag Hydraulische Steuervorrichtung
US7260931B2 (en) * 2005-11-28 2007-08-28 Caterpillar Inc. Multi-actuator pressure-based flow control system
DE102007028864A1 (de) * 2007-03-27 2008-10-02 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102010009705A1 (de) * 2010-03-01 2011-09-01 Robert Bosch Gmbh Hydraulische Steueranordnung
JP5750154B2 (ja) * 2010-03-17 2015-07-15 パーカー・ハニフィン・コーポレーション 圧力制限器を備える油圧弁
DE102010027964A1 (de) * 2010-04-20 2011-10-20 Deere & Company Hydraulische Anordnung
US8459195B2 (en) 2011-04-28 2013-06-11 Michael H. IRVING Self load sensing circuit board controller diaphragm pump
JP5948260B2 (ja) * 2013-01-24 2016-07-06 Ｋｙｂ株式会社 流体圧制御装置
CA2899867A1 (fr) 2013-01-31 2014-08-07 Parker-Hannifin Corporation Suralimentation a ecoulement prioritaire et pression limitee
CN104968947A (zh) * 2013-02-05 2015-10-07 沃尔沃建造设备有限公司 工程机械用压力控制阀
EP2980416B1 (fr) * 2014-07-31 2019-06-05 Bucher Hydraulics S.p.A. Section hydraulique pour des applications de détection de charge et de multiples distributeurs hydrauliques
JP6656913B2 (ja) * 2015-12-24 2020-03-04 株式会社クボタ 作業機の油圧システム
DE102021103091A1 (de) 2021-02-10 2022-08-11 Zf Cv Systems Europe Bv Elektropneumatischer Getriebesteller
CN117590876B (zh) * 2024-01-18 2024-05-24 深圳市前海能源科技发展有限公司 并联阀门组的运行优化方法、系统、电子设备及存储介质

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3044144A1 (de) * 1980-11-24 1982-09-09 Linde Ag, 6200 Wiesbaden Hydrostatisches antriebssystem mit einer einstellbaren pumpe und mehreren verbrauchern
DE3540061A1 (de) * 1985-02-28 1987-05-14 Rexroth Mannesmann Gmbh Mehrwegeventil mit druckwaage
DE3603630A1 (de) * 1986-02-06 1987-08-13 Rexroth Mannesmann Gmbh Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher
JP2582266B2 (ja) * 1987-09-29 1997-02-19 新キヤタピラー三菱株式会社 流体圧制御システム
DE3805061A1 (de) * 1988-02-18 1989-08-31 Linde Ag Hydraulische schaltanordnung
DE3812753C2 (de) * 1988-04-16 1994-05-26 Rexroth Mannesmann Gmbh Ventilanordnung für eine verstellbare Pumpe
DE3919175A1 (de) * 1989-06-12 1990-12-13 Hydromatik Gmbh Regeleinrichtung fuer eine verstellbare pumpe
DE4135013C2 (de) * 1991-10-23 2000-07-27 Linde Ag Hydraulisches Antriebssystem
DE4137963C2 (de) * 1991-10-30 1995-03-23 Rexroth Mannesmann Gmbh Ventilanordnung zur lastunabhängigen Steuerung mehrerer hydraulischer Verbraucher
JP3124094B2 (ja) * 1991-12-25 2001-01-15 カヤバ工業株式会社 複数アクチュエータの制御装置
FR2689575B1 (fr) * 1992-04-06 1994-07-08 Rexroth Sigma Distributeur hydraulique a compensation de pression et une selection de pression maximale pour piloter une pompe et commande hydraulique multiple incluant de tels distributeurs.
DE4235707B4 (de) * 1992-10-22 2007-10-18 Linde Material Handling Gmbh Hydrostatisches Antriebssystem
DE9318522U1 (de) * 1993-12-03 1995-03-30 O & K Orenstein & Koppel Ag, 13581 Berlin Steuerung zur Aufteilung des Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher

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Publication number Publication date
US5752384A (en) 1998-05-19
EP0760908A1 (fr) 1997-03-12
DE59504916D1 (de) 1999-03-04
JPH10500472A (ja) 1998-01-13
DE4417962A1 (de) 1995-11-23
KR970703494A (ko) 1997-07-03
WO1995032364A1 (fr) 1995-11-30

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