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EP1954949B1 - Dispositif hydraulique de commande - Google Patents

Dispositif hydraulique de commande Download PDF

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Publication number
EP1954949B1
EP1954949B1 EP06818465A EP06818465A EP1954949B1 EP 1954949 B1 EP1954949 B1 EP 1954949B1 EP 06818465 A EP06818465 A EP 06818465A EP 06818465 A EP06818465 A EP 06818465A EP 1954949 B1 EP1954949 B1 EP 1954949B1
Authority
EP
European Patent Office
Prior art keywords
pressure
load
valve
consumer
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06818465A
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German (de)
English (en)
Other versions
EP1954949A1 (fr
Inventor
Wolfgang Kauss
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of EP1954949A1 publication Critical patent/EP1954949A1/fr
Application granted granted Critical
Publication of EP1954949B1 publication Critical patent/EP1954949B1/fr
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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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • 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
    • 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
    • F15B11/168—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load with an isolator valve (duplicating valve), i.e. at least one load sense [LS] pressure is derived from a work port load sense pressure but is not a work port pressure itself
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—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
    • F15B2211/32—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
    • F15B2211/50—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
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/651—Methods of control of the load sensing pressure characterised by the way the load pressure is communicated to the load sensing circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the 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
    • F15B2211/70—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
    • F15B2211/7052—Single-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
    • F15B2211/7051—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
    • F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
    • 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 hydraulic control device in load-sensing embodiment according to the preamble of patent claim 1.
  • a so-called load-compensated or load-sensing control device for controlling a plurality of hydraulic consumers is for example from DE 197 15 020 A1 and from the DE 102 45 836 A1 known.
  • the load pressure of the individual consumers is detected.
  • the highest detected load pressure is fed via a load pressure signaling line to a control element of the pressure medium source.
  • the pressure provided by the pressure medium source is thereby adjusted by a certain control pressure difference ⁇ p above the highest load pressure.
  • the speed of the individual consumers is controlled by adjustable metering orifices.
  • Individual pressure balances regulate the pressure difference across the metering orifices in each case to a constant value, so that the speed of the individual consumers can be controlled independently of their load pressure.
  • Such pressure compensators are also called LS pressure compensators.
  • the consumers controlled in this way are called LS consumers.
  • the respective individual pressure compensator is usually acted upon in the opening direction by the load pressure of the consumer, ie by the pressure downstream of the metering orifice, as well as by a control spring and in the closing direction by the pressure upstream of the metering orifice. If the consumer associated branch of the load pressure signaling line is provided with a pressure relief valve, the pressure of the pressure medium supplied to the consumer can be limited individually for each LS consumer. The individual pressure compensator then provides at its output at most a pressure that the opening pressure of the pressure relief valve plus the pressure equivalent of their control spring corresponds.
  • a priority valve usually takes the place of the individual pressure compensator which, in addition to the quantity of pressure medium supplied to the prioritized consumer, controls the quantity of pressure medium supplied to the subordinate consumers. Also via such a priority valve can be done in the manner described a pressure limit.
  • the hydraulic control device is designed in load-sensing technology and serves to control a first hydraulic consumer and a second hydraulic consumer.
  • the first consumer may be an LS consumer with upstream or downstream Individual pressure balance act. Be but it is also the case that it is a so-called LUDV consumer is (l ast u ntouche D urch Weg v grant), as further elaborated in the following description includes.
  • a first control valve for controlling the first hydraulic consumer and a second control valve for controlling the second hydraulic consumer are present.
  • a first load signal is detectable based on a load pressure applied to the first hydraulic load
  • a second load signal is detectable based on a load pressure applied to the second hydraulic load.
  • the first control valve and the second control valve pressure medium from a pressure medium source can be fed in parallel.
  • a load reporting path can be acted on to control an actuator assigned to the pressure medium source with a highest currently detected load signal.
  • a limiting device allows the limitation of the second load signal to a predetermined signal limit value.
  • a switching means is provided which can be controlled by the second load signal such that, at the latest when the second load signal reaches the signal limit value, the signal carried on the load signaling path is limited by the limiting device.
  • the first consumer pressure medium under a higher pressure than a maximum allowable limit load pressure of the second consumer is supplied. Only when the load pressure of the second consumer reaches a predetermined pressure limit, the load signal is limited to the load signaling path. In this case, the supply pressure provided by the pressure medium source is reliably lowered in accordance with the pressure limit value and the control pressure difference ⁇ p of the pressure medium source.
  • This overload protection according to the invention can be implemented both in purely hydraulic and in electrohydraulic load-sensing controllers.
  • a switching valve which fluidly connects a load pressure signaling line to a pressure limiting valve in an actuated switching position.
  • the switching pressure of the second load consumer is supplied as control pressure.
  • the pressure limitation is effected by influencing the control mechanism of the pressure medium source and not, as in the conventional case, by a arranged in the consumer supply valve.
  • the valves used according to the invention for pressure limiting, the switching valve and the pressure relief valve are invariably connected to control lines of small cross-section and can therefore be carried out inexpensively in a smaller nominal size.
  • the pressure limiting valve is arranged on a supply line from a load pressure signaling connection of the second control valve to the load pressure signaling line.
  • a pressure limiting valve is already provided in many hydraulic control blocks and allows a simple modification of existing series.
  • a preferred embodiment of the present invention is that the switching valve is designed as a seat valve, and that it has the function of a check valve opening to the load pressure signaling line in an unactuated shift position. In this way, the switching valve ensures that the load pressure of the second consumer is only reported to the load pressure signaling line, if this is the load pressurehighest consumer.
  • the switching valve thus replaces that in conventional constructions for this purpose used check valve and allows a compact and efficient design of the control device.
  • a required for actuation of the switching valve switching pressure corresponds at most to the opening pressure of the pressure relief valve.
  • the switching pressure of the switching valve is about 5 to 10 bar below the opening pressure of the pressure relief valve, one achieves a particularly reliable insertion of the pressure relief.
  • the first control valve comprises a load-holding valve. This ensures that, regardless of a pressure limit in the load-sensing line and a subsequently reduced supply pressure, no sagging of the first load is to be feared.
  • a hydraulic control device 1 is used to control at least two hydraulic consumers 15 and 30.
  • a pressure medium supply line 13 is supplied by a hydraulic pump 10 from a storage tank 12 with pressure medium.
  • the hydraulic pump 10 is an adjustable pump, the delivery rate of which is controlled by a pump regulator 11.
  • the pump regulator 11 is controlled by the pressure signal applied in a load pressure detection line 24. It ensures that at the output of the pump 10, a pressure is established, which is at a certain control pressure .DELTA.p above the load pressure signal.
  • the adjustable metering orifice 18 and the directional control valve 20 are both formed on the valve piston of a control valve.
  • the pressure compensator 16 is acted upon in the opening direction with the pressure downstream of the adjustable metering orifice 18 and with the force of a control spring. In the closing direction is at the control member of the pressure compensator 16, the pressure upstream of the metering orifice 18.
  • the pressure detected downstream of the metering orifice 18 corresponds to the load pressure of the consumer 15. This load pressure is supplied as a pressure signal via a shuttle valve 26 to the load pressure signaling line 24.
  • the shuttle valve 26 also allows load pressure signals of other consumers to lead to the load pressure signaling line 24. In this case, the load pressure signaling line 24 is acted upon by the highest of the detected load pressure signals.
  • the control line 24 is relieved via a flow control valve 25 to the storage tank 12 out.
  • the hydraulic consumer 30 is driven essentially via an adjustable metering orifice 32. This can be carried out together with a directional control valve on the valve piston of another control valve. At one Load pressure signaling connection 33, a load pressure signal of the consumer 30 can be detected. Usually, the load pressure signaling connection 33 is located on the control valve, which also forms the adjustable metering orifice 32. The load pressure signaling connection 33 is connected to a control line 34. The pressure on the control line 34 is limited by a pressure limiting valve 35. The control line 34 leads to a switching valve 36. A control member of the switching valve 36 is acted upon in the direction of an unactuated valve position by a spring 38.
  • the switching valve 36 In the direction of an actuated valve position, the switching valve 36 is acted upon by the load pressure signal of the load 30, which is brought by the control line 34 via a further control line 37 to it.
  • the switching valve 36 controls a connection between the control line 34 and the load pressure signaling line 24.
  • the switching valve 36 In the unactuated switching position, the switching valve 36 has the function of a load pressure signaling line 24 to open the check valve.
  • the switching valve 36 releases a fluidic connection between the control line 34 and the load pressure signaling line 24.
  • the control of the hydraulic consumer 15 corresponds to the conventional control of a consumer in a load-sensing system and is therefore not specifically explained. In the following, in particular, the mechanism of limiting the load 30 acting on the load will be discussed.
  • the opening pressure of the pressure limiting valve 35 corresponds to a pressure which is around the control pressure difference ⁇ p of the pump regulator 11 below the maximum permissible load pressure of the consumer 30.
  • the spring 38 of the switching valve 36 is dimensioned such that it corresponds to a switching pressure which is about 5 to 10 bar below the opening pressure of the pressure limiting valve 35.
  • the switching valve 36 is closed. In this state, either the load pressure of the consumer 15 or the check valve function of the switching valve 36, the load pressure of the consumer 30 is reported in the load pressure signaling line 24, depending on which load pressure is the higher. This can be in the load pressure signaling line 24 by the consumer 15th or by further consumers reported load pressure signal are well above the maximum allowable load pressure of the consumer 30. Accordingly, the supply pressure provided by the hydraulic pump 10 may also exceed the maximum allowable load pressure of the consumer 30. As long as the load 30 is subjected to a load resulting in a load pressure below its maximum allowable load pressure, the load 30 will not be overloaded.
  • the switching valve 36 releases a connection between the load pressure signaling line 24 and the control line 34 and in particular the pressure limiting valve 35.
  • the load pressure signal present in the load pressure signaling line 24 is limited to the opening pressure of the pressure limiting valve 35. Since the switching pressure of the switching valve 36 is about 5 to 10 bar below the opening pressure of the pressure relief valve 35, and the opening pressure in turn by about the control pressure difference Ap of the pump controller 11 is below the maximum allowable load pressure of the consumer 30, in this way an overload of the consumer 30th effectively prevented.
  • the load pressure signal is limited to the central load pressure signaling line 24 and thus the supply pressure available to all consumers. However, this occurs only when an overload of the consumer 30 threatens. In normal operation, the consumer 15 or further consumers can be operated at a pressure which is above the load pressure limit of the consumer 30.
  • the FIG. 2 shows a circuit diagram of a hydraulic control device 2.
  • the hydraulic control device 2 is a modification of the hydraulic control device 1, which differs from this only in the arrangement of the switching valve and the pressure relief valve and in the type of the switching valve. Components of the hydraulic control device 2, which correspond to those of the hydraulic control device 1, are provided with the same reference numerals and will not be described specifically.
  • the switching valve 44 in the case of the hydraulic control device 2, is fluidically connected to the load pressure signaling line 24 via a separate connecting line 45.
  • the switching valve 44, the pressure relief valve 48 is arranged downstream.
  • a control line 40 leads to the load pressure signaling line 24 via a check valve 42 opening toward the load pressure signaling line 24.
  • the load pressure signal of the consumer 30 is supplied via the control line 47 to an actuator of the switching valve 44 and acts on it in the opening direction. In the closing direction, the actuator of the switching valve 44 is acted upon by the spring 46.
  • an actuated switching position of the switching valve 44 there is a fluid connection between the load pressure signaling line 24 and the pressure limiting valve 48.
  • an unactuated switching position of the switching valve 44 the fluidic connection between the load pressure signaling line 24 and the pressure relief valve 48 is interrupted.
  • the opening pressure of the pressure relief valve 48 is set in accordance with the maximum allowable load pressure of the load 30.
  • the determined by the spring 46 switching pressure of the switching valve 44 is about 5 to 10 bar less than the opening pressure of the pressure relief valve 48th
  • the load pressure detected at the load pressure signaling connection 33 is reported to the load pressure signaling line 24 via the check valve 42 if no higher load pressure exists on the part of the further load.
  • the load pressure detected at the terminal 33 is applied to the switching valve 44 via the control line 47.
  • this load pressure signal reaches the opening pressure of the switching valve 44, the switching valve 44 releases the connection between the load pressure signaling line 24 and the pressure limiting valve 48.
  • the load pressure signal guided on the load pressure signaling line 24 is limited to the opening pressure of the pressure limiting valve 48.
  • the function of the hydraulic control device 2 thus corresponds to the function of the hydraulic control device 1 with regard to the overload protection for the load 30.
  • the connection of the switching valve 44 to the load pressure signaling line 24 via a separate control line 45 allows a greater flexibility in the arrangement of the switching valve 44 and the pressure relief valve 48. In addition, a simply constructed switching valve can be used.
  • FIG. 3 is with the hydraulic control device 3, a further modification of in FIG. 1 shown hydraulic control device 1 shown. Again, the same components are provided with the same reference numerals and are not specifically explained.
  • the speed of the consumer 15 is controlled via a metering orifice 52. Downstream of the metering orifice 52, a pressure compensator 54 is arranged. In the fluid path from the pump 10 to the consumer 15 are further a load-holding valve 64 and the directional control valve 20.
  • the pressure compensator 54 has a control piston 57. By the control piston 57 performs a control line 58 into a back space 55 of the pressure compensator 54. In the control line 58 is a check valve 59 opening towards the rear space 55 is arranged.
  • the rear space 55 is in fluid communication with a load pressure signaling line 50.
  • a spring 56 is arranged in the rear space 55, which acts on the control piston 57.
  • Further consumers are supplied via similarly constructed pressure compensators 62 with pressure medium.
  • a steering unit 70 is supplied via the supply line 13.
  • the steering unit 70 controls via terminals 78 and 79 to / the steering cylinder of a vehicle.
  • the main component of the steering unit 70 is a rotor set 72, via which the terminals 78 and 79 supplied amount of pressure medium is controlled.
  • a load pressure signal is passed to the outside. This load pressure signal is limited within the steering unit 70 by a pressure relief valve 74.
  • the load pressure signal present at the load pressure signaling connection 76 is conducted via the control line 77 to the switching valve 36. Via the control line 37, an actuator of the switching valve 36 is acted upon by this load pressure signal.
  • the pressure compensator 54 regulates the pressure downstream of the metering orifice 52 to a value which is about the pressure equivalent of the force of the spring 56 above the load pressure signal, which is present in its rear space 55.
  • Spring 56 designed quite weak, so that the pressure between the metering orifice 52 and the pressure compensator 54 is only slightly above the pending in the pressure chamber 55 load pressure signal.
  • This load pressure signal corresponds to the highest load pressure of the connected consumers.
  • the back rooms of further pressure compensators 62, etc., as well as the pressure chamber 55 are acted upon by the load pressure signal carried in the load pressure signaling line 50.
  • the pressure upstream of the metering orifice 52 corresponds to the supply pressure provided by the hydraulic pump 10.
  • the steering unit 70 is supplied via the supply line 13 from the pump 10.
  • the present at the output 76 of the steering unit 70 load pressure signal is supplied via the switching valve 36, which has the function of a check valve in the unactuated position, the load pressure signaling line 50.
  • the load-holding valve 64 is arranged in the supply line of the consumer 15.
  • the overload protection mechanisms described with reference to the hydraulic control devices 1, 2 and 3 can also be implemented in the electronic control unit of an electro-hydraulic control device.
  • the load-signaling path in the sense of claim 1 is implemented as a load-pressure-signaling line, the limiting device as a pressure-limiting valve, and the switching means as a switching valve.

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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)

Claims (7)

  1. Dispositif de commande hydraulique dans une réalisation de détection de charge pour la commande d'un premier consommateur hydraulique (15) et d'un deuxième consommateur hydraulique (30), dans lequel :
    on prévoit une première soupape de commande (18, 20) pour la commande du premier consommateur hydraulique (15) et une deuxième soupape de commande (32) pour la commande du deuxième consommateur hydraulique (30),
    un premier signal de charge sur la base d'une pression de charge, avec laquelle le premier consommateur hydraulique (15) est sollicité, et un deuxième signal de charge sur la base d'une pression de charge avec laquelle le deuxième consommateur hydraulique (30) est sollicité, peuvent être détectés,
    on peut acheminer en parallèle à la première soupape de commande (18, 20) et à la deuxième soupape de commande (32) des fluides de pression
    provenant d'une source de fluide de pression (10),
    une voie de communication de charge (24) est prévue, laquelle peut être sollicitée pour la commande d'un actionneur (11) associé à la source de fluide de pression (10), avec un signal de charge maximal détecté actuellement, et
    dans lequel un dispositif de limitation (35 ; 48) est prévu, avec lequel le deuxième signal de charge peut être limité à une valeur limite de signal prédéfinie,
    caractérisé en ce que
    l'on prévoit un moyen de commutation (36 ; 44) qui peut être commandé par le deuxième signal de charge de telle sorte qu'au plus tard lorsque le deuxième signal de charge atteint la valeur limite de signal, le signal guidé sur la voie de commutation de charge (24) soit limité par le dispositif de limitation (35 ; 48).
  2. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que l'on prévoit une soupape de commutation (36 ; 44) qui, dans une position de commutation actionnée, relie fluidiquement une conduite de communication de pression de charge (24) à une soupape de limitation de pression (35 ; 48), et en ce que l'on achemine à la soupape de commutation (36 ; 44) la pression de charge du deuxième consommateur (30) en tant que pression de commande.
  3. Dispositif de commande hydraulique selon la revendication 2, caractérisé en ce que la soupape de limitation de pression (35 ; 74) est disposée au niveau d'une conduite d'amenée allant d'un raccordement de communication de pression de charge de la deuxième soupape de commande (32 ; 72) à la conduite de communication de pression de charge (24 ; 50).
  4. Dispositif de commande hydraulique selon la revendication 3, caractérisé en ce que la soupape de commutation (36) est réalisée sous forme de soupape à siège, et en ce qu'elle possède, dans une position de commutation non actionnée, la fonction d'une soupape de non retour s'ouvrant vers la conduite de communication de pression de charge (24 ; 50).
  5. Dispositif de commande hydraulique selon l'une quelconque des revendications 2 à 4, caractérisé en ce qu'une pression de commutation nécessaire pour l'actionnement de la soupape de commutation (36 ; 44) correspond au maximum à la pression d'ouverture de la soupape de limitation de la pression (35 ; 48 ; 74).
  6. Dispositif de commande hydraulique selon la revendication 5, caractérisé en ce que la pression de commutation de la soupape de commutation (36 ; 44) est de l'ordre d'environ 5 à 10 bars en dessous de la pression d'ouverture de la soupape de limitation de la pression (35 ; 48 ; 74).
  7. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la première soupape de commande (52, 20, 64) comprend une soupape de retenue de charge (64).
EP06818465A 2005-11-21 2006-11-10 Dispositif hydraulique de commande Not-in-force EP1954949B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005055309A DE102005055309A1 (de) 2005-11-21 2005-11-21 Hydraulische Steuervorrichtung
PCT/EP2006/010793 WO2007057126A1 (fr) 2005-11-21 2006-11-10 Dispositif hydraulique de commande

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EP1954949A1 EP1954949A1 (fr) 2008-08-13
EP1954949B1 true EP1954949B1 (fr) 2010-02-10

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DE102011118255A1 (de) * 2011-11-11 2013-05-16 Robert Bosch Gmbh Hydrostatischer Fahrantrieb und Fahrzeug mit einem derartigen Fahrantrieb
JP5948260B2 (ja) * 2013-01-24 2016-07-06 Ｋｙｂ株式会社 流体圧制御装置
US11143211B1 (en) * 2021-01-29 2021-10-12 Cnh Industrial America Llc System and method for controlling hydraulic fluid flow within a work vehicle

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DE4417962A1 (de) * 1994-05-21 1995-11-23 Rexroth Mannesmann Gmbh Steueranordnung für wenigstens zwei hydraulische Verbraucher
DE19703997A1 (de) * 1997-02-04 1998-08-06 Mannesmann Rexroth Ag Hydraulischer Steuerkreis für einen vorrangigen und für einen nachrangigen hydraulischen Verbraucher
DE19715020A1 (de) 1997-04-11 1998-10-15 Rexroth Mannesmann Gmbh Hydraulische Steueranordnung, insbesondere für ein Fahrzeug zum Transport von Absetzmulden
DE19930618A1 (de) * 1999-07-02 2001-01-04 Mannesmann Rexroth Ag Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
DE10058032A1 (de) * 2000-11-23 2002-05-29 Mannesmann Rexroth Ag Hydraulische Steueranordnung
DE10149791B4 (de) * 2001-10-09 2012-03-29 Linde Material Handling Gmbh Steuerventileinrichtung
DE10245836B4 (de) 2002-04-26 2013-03-14 Bosch Rexroth Aktiengesellschaft LS-Wegeventilanordnung

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EP1954949A1 (fr) 2008-08-13
US20090064673A1 (en) 2009-03-12
DE502006006129D1 (de) 2010-03-25
US8006490B2 (en) 2011-08-30
DE102005055309A1 (de) 2007-05-24
WO2007057126A1 (fr) 2007-05-24

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