EP1954949A1 - Dispositif hydraulique de commande - Google Patents

Dispositif hydraulique de commande

Info

Publication number
EP1954949A1
EP1954949A1 EP06818465A EP06818465A EP1954949A1 EP 1954949 A1 EP1954949 A1 EP 1954949A1 EP 06818465 A EP06818465 A EP 06818465A EP 06818465 A EP06818465 A EP 06818465A EP 1954949 A1 EP1954949 A1 EP 1954949A1
Authority
EP
European Patent Office
Prior art keywords
pressure
load
valve
hydraulic
signal
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
EP06818465A
Other languages
German (de)
English (en)
Other versions
EP1954949B1 (fr
Inventor
Wolfgang Kauss
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
Bosch Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1954949A1 publication Critical patent/EP1954949A1/fr
Application granted granted Critical
Publication of EP1954949B1 publication Critical patent/EP1954949B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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 known e.g. known from DE 197 15 020 A1 and DE 102 45 836 A1.
  • 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
  • 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 according to the invention is load-sensing
  • the first consumer may be an LS consumer with upstream or downstream teter individual pressure balance act. However, it should also be the case that it is a so-called LUDV consumer (load-independent flow distribution), as explained in more detail in the following description.
  • 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 message path is to
  • a limiting device allows the limitation of the second load signal to a predetermined signal limit value. It is the peculiarity of the present invention that 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. In this way, a simple and efficient limitation of the pressure load of the second consumer is achieved. This makes it possible to operate a less pressure-resistant consumer together with higher-load consumers in the same hydraulic control circuit. In particular, the first consumer pressure medium under a higher pressure than a maximum allowable limit load pressure of the second consumer is supplied.
  • the load signal is limited to the load signaling path.
  • 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 only activated as needed limitation of the load signal on the Lastmeldepfad thus allows Under normal operating conditions unrestricted operation of the hydraulic consumers and secures in the case of imminent overload of a consumer this reliable.
  • This overload protection according to the invention can be implemented both in purely hydraulic and in electrohydraulic load-sensing controllers. Further advantageous embodiments are specified in the subclaims.
  • 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 limiting pressure, the switching valve and the pressure limiting valve are invariably connected to control lines of small cross-section and can therefore be designed cost-effectively 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 is in an unactuated
  • 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, allowing compact and efficient
  • 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 no sagging of the first consumer is to be feared, regardless of a pressure limit in the load-sensing line and a subsequently reduced supply pressure.
  • FIG. 1 is a circuit diagram of a hydraulic control arrangement for a consumer, in whose supply line an individual pressure compensator is arranged, and for a further consumer, with its
  • Fig. 2 shows a modification of the circuit shown in Fig. 1 with an alternative arrangement of a switching valve and the pressure relief valve, wherein the pressure relief valve is not is directly connected to a load-sensing connection of the first consumer
  • Fig. 3 shows a modification of the circuit shown in Fig. 1, according to which a plurality of consumers in the sense of a LUDV control can be controlled and after the further consumer as a steering unit is provided with the load pressure signal, the switching valve is driven.
  • a hydraulic control device 1 serves to control at least two hydraulic consumers 15 and 30.
  • a pressure medium supply line 13 is supplied with pressure medium by a hydraulic pump 10 from a storage tank 12.
  • the hydraulic pump 10 is an adjustable pump, the flow rate is controlled by a pump regulator 1 1.
  • the pump regulator 1 1 is controlled by the pending in a load pressure signaling line 24 pressure signal. 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 essentially an adjustable
  • Metering orifice 32 activated. This can be carried out together with a directional control valve on the valve piston of another control valve.
  • a load pressure signal of the consumer 30 can be detected.
  • 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 .DELTA.p of the pump controller 1 1 below the maximum allowable 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 As long as the load pressure of the consumer 30 is below the switching pressure of the switching valve 36, 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.
  • 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. This will do this in the load pressure signaling line
  • 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 hydraulic control device 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 nature 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. in the Difference to the hydraulic control device 1 is in the hydraulic
  • Control device 2 the switching valve 44 fluidly connected via a separate connecting line 45 to the load pressure signaling line 24.
  • the switching valve 44, the pressure relief valve 48 is arranged downstream. From the load pressure detection connection 33 of the consumer 30 or a control valve, 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.
  • In 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. In 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.
  • Pressure limiting valve 48 set in accordance with the maximum allowable load pressure of the load 30.
  • the switching pressure of the switching valve 44 determined by the spring 46 is approximately 5 to 10 bar less than the opening pressure of the pressure limiting valve 48.
  • the load pressure detected at the load pressure reporting terminal 33 is transmitted via the check valve 42 into the load pressure signaling line 24 if no further load pressure exists on the other load reported.
  • 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. Thereupon, 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 consumer 30.
  • switching valve 44 Connecting 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 shows a further modification of the hydraulic control device 1 shown in FIG. 1 with the hydraulic control device 3.
  • 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
  • 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)

Abstract

L'invention concerne un dispositif hydraulique de commande réalisé à l'aide de la technologie de détection des charges et qui sert à commander un premier consommateur hydraulique et un deuxième consommateur hydraulique. De plus, une première soupape de commande qui contrôle le premier consommateur hydraulique et une deuxième soupape de commande qui contrôle le deuxième consommateur hydraulique sont prévues. Un premier signal de charge peut être détecté à partir de la pression de charge qui sollicite le premier consommateur hydraulique et un deuxième signal de charge peut être détecté à partir de la pression de charge qui sollicite le deuxième consommateur hydraulique. Un fluide sous pression qui provient d'une source de fluide sous pression peut être amené en parallèle à la première soupape de commande et à la deuxième soupape de commande. Le signal de charge le plus élevé détecté à un moment donné peut être envoyé dans un parcours de transmission de charge pour commander un organe de réglage associé à la source de fluide sous pression. Un dispositif de limitation permet de limiter le deuxième signal de charge à une valeur de seuil prédéterminée du signal. Un moyen de commutation peut être commandé par le deuxième signal de charge de telle sorte que le signal transporté sur le parcours de transmission de charge soit limité par le dispositif de limitation au plus tard lorsque le deuxième signal de charge atteint la valeur de seuil du signal.
EP06818465A 2005-11-21 2006-11-10 Dispositif hydraulique de commande Expired - Fee Related 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

Publications (2)

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

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EP06818465A Expired - Fee Related EP1954949B1 (fr) 2005-11-21 2006-11-10 Dispositif hydraulique de commande

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Country Link
US (1) US8006490B2 (fr)
EP (1) EP1954949B1 (fr)
DE (2) DE102005055309A1 (fr)
WO (1) WO2007057126A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
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

Non-Patent Citations (1)

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Title
See references of WO2007057126A1 *

Also Published As

Publication number Publication date
US8006490B2 (en) 2011-08-30
EP1954949B1 (fr) 2010-02-10
US20090064673A1 (en) 2009-03-12
DE102005055309A1 (de) 2007-05-24
DE502006006129D1 (de) 2010-03-25
WO2007057126A1 (fr) 2007-05-24

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