EP1616997A1 - Dispositif hydraulique de contrôle - Google Patents

Dispositif hydraulique de contrôle Download PDF

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Publication number
EP1616997A1
EP1616997A1 EP05015152A EP05015152A EP1616997A1 EP 1616997 A1 EP1616997 A1 EP 1616997A1 EP 05015152 A EP05015152 A EP 05015152A EP 05015152 A EP05015152 A EP 05015152A EP 1616997 A1 EP1616997 A1 EP 1616997A1
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EP
European Patent Office
Prior art keywords
valve
pressure
control
arrangement according
control arrangement
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
EP05015152A
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German (de)
English (en)
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EP1616997B1 (fr
Inventor
Jörg Willy Grünert
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of EP1616997A1 publication Critical patent/EP1616997A1/fr
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • 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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out 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
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—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
    • F15B2211/50—Pressure control
    • F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/715—Output members, e.g. hydraulic motors or cylinders or control therefor having braking means

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a consumer according to the preamble of patent claim 1.
  • Such hydraulic control arrangements are preferably used in mobile implements, for example, wheeled excavators for controlling the different working movements enabling consumers, such as hydraulic cylinders or hydraulic motors.
  • LS Location Sensing
  • the adjustable metering orifices of a LS control are assigned individual pressure balances, which maintain a pressure difference independent of the load pressure via the respective metering orifices.
  • these individual pressure compensators are arranged upstream of the metering orifice and throttle between the pump line and the Zumessblenden the fluid flow so strong that the pressure before the metering orifices regardless of the pump pressure is only a certain pressure difference above the individual load pressure ,
  • the individual pressure balances are arranged downstream of the metering orifices and throttle the between the metering orifices and the load Fluid flow so strong that the pressure after all Zumessblenden same, preferably equal to the highest load pressure or slightly above this.
  • the pressure drop across the metering orifices of the system changes in the same way in a LUDV control, so that the preset current distribution between the metering orifices is maintained.
  • variable displacement pump does not necessarily have to be used.
  • the basic principle of such a control arrangement is described in DE 24 40 714 C3. Applications of this system are also described under the data sheets RD 64 122 or RD 64 354 available on the Internet at www.boschrexroth.de.
  • the control of the consumer such as a rotary drive, via a continuously adjustable 6-way valve, via which the two working ports of the consumer with the run as a fixed displacement pump or a tank connected.
  • the valve In the basic position of the directional control valve, the connections to the working connections are shut off.
  • the valve is designed in an open-center design, with the pump in the basic position (neutral position) conveying pressure medium without pressure into a circulation channel connected to the tank.
  • a pressure compensator is arranged according to DE 24 40 714 C3, which is acted upon in the opening direction of the pressure downstream of the directional control valve and in the closing direction of the force of a pressure compensator spring and the highest load pressure of the consumer of the mobile implement.
  • This pressure compensator works together with the directional control valve as a current regulator the pressure medium volume flow in the circulation channel load pressure independent can be kept constant.
  • connection to the pressure medium-loaded connection of the consumer When opening the directional control valve to the pressure medium supply of the consumer, the connection to the pressure medium-loaded connection of the consumer is gradually opened, while the connection to the circulation channel is throttled in opposite directions. In parallel, a flow cross-section is opened up via the directional control valve, via which the pressure medium flows from the consumer to the tank.
  • the pressure compensator ensures that the same pressure conditions prevail in the circulation channel as in the flow to the consumer.
  • the present invention seeks to provide a constructed according to the 6-way principle hydraulic control arrangement in which a small change in the technical complexity of the pressure / flow conditions in the process is possible.
  • the hydraulic control arrangement is executed in the sequence with at least one outlet throttle valve whose opening cross section can be controlled independently of the control of a continuously adjustable directional control valve, via which the consumer with pressure medium can be supplied and the connection to a circulation channel on or is zuu Kunststoffbar.
  • a separate drain groove is formed, which can be controlled independently of the inlet cross-section depending on the operating conditions in a suitable manner.
  • a pressure for biasing the load can be set via the outlet throttle valve in the outlet.
  • the volume flow can be preset via the inlet and then the speed of the consumer can be set by setting the outlet throttle valve.
  • each working port is assigned a drain line with a drain throttle valve, so that the flow in both directions can be controlled in the manner described above.
  • continuously adjustable directional control valve as a 6-way valve, so that the control arrangement is very compact.
  • the outlet throttle valve continuously adjustable, wherein the adjustment of the throttle cross section preferably takes place by means of a pilot control valve.
  • a pilot control valve instead of such electrohydraulic control also a hydraulic or electro-mechanical pilot control of the outlet throttle valve can be selected.
  • the control of the directional control valve via directional valve pilot valves, which are preferably supplied by the same control pressure as the pilot valves of the outlet throttle valve.
  • a primary pressure relief valve may be provided between the directional control valve and the pump.
  • the pressure relief valve can be controlled for example via the aforementioned control pressure and the control chamber via a further, electrically controllable pressure relief valve to be connected to the tank.
  • each a pressure / suction valve is provided which acts as a secondary pressure relief valve.
  • the hydraulic motor of the slewing gear can be provided with a brake which serves as a holding brake or as a dynamic brake with variable ventilation pressure.
  • a brake is mechanically biased, for example by a spring in the direction of braking engagement and is hydraulically disengaged by means of a brake release pressure. This may correspond to the aforementioned control supply pressure or adjusted by means of a pressure reducing valve to to control the braking intervention in a dynamic brake.
  • the pressure applied in the flow and in the sequence pressures are detected by a respective pressure transducer and driven in response to these signals, the directional control valve and the outlet throttle valve.
  • the consumer is a hydraulic motor
  • its speed can be detected by means of a speed sensor and in response to this signal, the speed of the hydraulic motor can be controlled.
  • this is integrated in a valve disc.
  • the pressure medium supply is preferably carried out by means of a constant pump.
  • Figure 1 shows the circuit diagram of a control block 1 for controlling a slewing gear of a wheeled excavator.
  • the slewing gear is actuated by a hydraulic motor 2, the drive shaft via a holding brake 4 can be fixed.
  • the pressure medium is conveyed by means of a pump 12 which is connected to a pressure port P of the control block 6 and the pressure medium flowing back from the consumer is led via a tank connection T to a tank.
  • the control block 1 further has a pilot port PV, a brake port 1 and a drain port L, which is also connected to the tank.
  • the self-adjusting load pressure or a corresponding pressure can be tapped via a control terminal X.
  • the control block 1 includes a continuously adjustable directional control valve 14, via which the pressure medium supply to the hydraulic motor 2 is controlled. Between the directional control valve 14 and the pump 12, a primary pressure limiting valve 16 is arranged, via which the pump pressure is limited.
  • the primary pressure limiting valve 16 can optionally be assigned a further pressure limiting valve 18, via which a control chamber of the primary pressure limiting valve 16 can be connected to the outlet connection L.
  • the brake 4 is biased by springs in the direction of braking intervention.
  • the release of the brake is hydraulically via a brake vent line 20 which is connected to the brake port 1. This can via a brake release valve 22 with the drain port L (brake engaged) or with the voltage applied to the pilot port PV Control pressure are applied to release the brake.
  • the brake pressure in the brake vent line 20 via a 3-way pressure reducing valve 24 can be adjusted. Both the brake release valve 22 and the pressure reducing valve 24 are electrically operated.
  • the speed of the hydraulic motor 2 is detected by a speed sensor 26 and the pressures in the two working lines 8, 10 are detected by pressure sensors 28 and 30, respectively.
  • a circulation channel 32 connected to the tank connection T and connected to a circulation connection C of the directional control valve 14.
  • a circulation pressure compensator 34 is provided, whose function will be explained below.
  • the control of the directional control valve 14 via two-way valve pilot valves 36, 38, which are designed as pressure reducing valves, wherein the input terminal is connected to the pilot port PV.
  • the directional control valve 14 has two working ports A, B, which are connected via two channels 40, 42 to the terminals A, B of the control block 6.
  • the right channel in FIG. 1 is the feed channel 40
  • the left channel connected to the B port is the drain channel 42.
  • a drain line 44 and 46 From each of the channels 40, 42 branches off a drain line 44 and 46, in each of which a pilot-operated outlet valve 48 and 50 is arranged, which is biased in a closed position and can be controlled via a pilot pressure in a throttle position in which a throttle cross-section opened is, via which the drain line 44, 46 is connected to a line section 52 and 54, respectively, the downstream of the circulation pressure compensator 34 opens into the circulation channel 32.
  • the pilot control of the outlet throttle valves 48, 50 takes place in each case via pilot valves 56, 58, which are likewise designed as pressure-reducing valves whose input connection is connected to the pilot control connection PV.
  • the pressure port P of the control block 6 is connected via an inlet channel 60 to an input port P of the directional control valve 14.
  • This also has an additional input port P ', which also bears the pressure in the inlet channel 60 and which is connected in the illustrated spring-biased home position (0) of the directional control valve 14 to the circulation port C, to which the circulation channel 32 is connected.
  • the above-circulation pressure compensator 34 is arranged.
  • the pressure compensator 34 is acted upon in the closing direction by the force of a spring and the pressure in a control channel 62, which is connected to an output of a shuttle valve 64 whose inputs are connected on the one hand to the control terminal X of the control block 1 and on the other hand to a control port Y of the directional control valve 14 is in the basic position (0) with a Tank connection T is connected. This leads via a short tank line 66 in the leading to the circulation channel 32 connecting line 54 a. In the opening direction, the pressure compensator 34 is acted upon by the pressure in the pressure medium flow path between the directional control valve 14 and the pressure compensator 34.
  • the directional control valve 14 is designed so that the connection to the circulation channel 32 in the basic position (0) is completely opened - that is, the connection to the pump P is open and leaves the pressure medium volume flow of P 'via C, the circulation channel 32 and the pressure compensator 34th flow out.
  • the input port P is connected to the output port A and the control port Y. With increasing displacement in the positions (a) the connection to the circulation channel 32 is controlled. Accordingly, when shifting to one of the positions indicated by (b), the input port P is connected to the working port B and to the control port Y.
  • the Umlaüfkanal 32 is controlled accordingly with increasing operation of the directional control valve 14. That is, in the solution according to the invention via the directional control valve 14, the control of the pressure medium volume flows in the circulation channel 32 and in the respective effective flow channel 40 (42).
  • the two channels 40, 42 and the connecting lines 52, 54 each connected via a pressure / Nachsaugventil 68, 70 with each other. These act as secondary pressure limiting valves and make it possible to suck in pressure medium from the tank to avoid cavitations when the load is pulled.
  • the directional valve pilot valve 38 is connected to the pilot port PV via a pilot channel 72, with one line section 72a leading to the input port P of the directional valve pilot valve 38, while another line section 72b leads to the input port P of the other directional valve pilot valve 36 (not shown in FIG. 2).
  • a port T of the directional valve pilot valve 38 is connected to a drain passage 74 leading to the drain port L, respectively.
  • An output port A of the directional control valve pilot valves 38 (36) is connected to the control spaces of the directional control valve 14 via a directional control valve line 76 and 78, respectively.
  • the 3-way pressure reducing valves 36, 38 are electrically controlled via the central control of the mobile device.
  • the control of the two outlet throttle valves 48, 50 is carried out accordingly via also as 3-way pressure reducing valves pilot valves 58 (56) whose input port P to the pilot passage 72, tank port T to the drain passage 74 and output port A to the control chamber of the respective outlet throttle valve 50th or 48 are connected.
  • the triggering value of the pressure relief valve 16 can be set on the one hand via an adjustable spring and on the other hand via a hydraulic pilot control for torque control.
  • This hydraulic pilot control is formed by the electrically operated pressure relief valve 18, which in a to a control terminal X of the pressure relief valve 16 connected to channel 82 is arranged, this channel 82 opens into the drainage channel 74, so that when opening the pressure relief valve 18 can be lowered in the control chamber of the primary pressure relief valve 16 applied control pressure.
  • a control connection Y of the primary pressure limiting valve 16 is likewise connected to the discharge channel 74 via a leakage line 84 indicated by dashed lines.
  • the brake 4 is released by means of the brake release valve 22.
  • This is designed as a switching valve which, in its spring-biased basic position shown in FIG. 2, has a brake channel 86 connected to a working port A with a connection T connected to the brake release valve 22. in the flow channel 74 opening portion 88 connects.
  • a pressure port P is connected to the working port A and the tank port T shut off.
  • the pressure port P opens via a vent line 90 in the portion 72 a of the pilot channel 72, so that then rests in the brake passage 86, the pilot pressure.
  • the brake channel 86 is connected to a pressure port P of the pressure reducing valve 24, the tank port T is connected to the drain passage 74 and the output port A via a brake bleeding passage 92 to the brake port 1.
  • the pressure reducing valve 24 is electrically actuated in order to reduce the pre-control pressure applied to the pilot control connection PV to a suitable brake release pressure and thus correspondingly to control a dynamically acting brake.
  • the pressure reducing valve 24 can also be omitted, so that the ventilation pressure always substantially corresponds to the pilot pressure.
  • the directional control valve 14 is initially displaced in the direction of its positions marked (a) in order to actuate the hydraulic motor 2. Initially, via fine control grooves of the directional control valve 14, the connection from the pressure port P to the working port A is controlled up steadily, while the pressure medium flow streaming out via the circulating passage 32 is throttled correspondingly via fine control grooves. With further displacement of the valve spool of the directional control valve 14, the pressure medium volume flow is increasingly reversed from the circulation channel 32 to the flow channel 40.
  • the pressure compensator 34 in each case adjusts itself into a control position such that approximately the same pressure is applied to the connections A, C of the directional control valve 14.
  • the pressure medium is then passed via the flow channel 40, the working port A of the control block 6 and the working line 10 to the input port of the hydraulic motor 2.
  • the flow restrictor valve 50 connected to the flow channel 40 remains in its spring-biased locking position and the outlet throttle valve 48 is brought into its fully open position by suitable control of the pilot valve 56, so that the hydraulic fluid flowing back from the hydraulic motor 2 without throttling via the working line. 8 , the port B of the control block 6, the drain line 44, the opened drain throttle valve 48, the connecting line 52 can flow to the tank port T out.
  • the speed of the hydraulic motor 2 is then determined by the adjustment of the directional control valve 14 and the maximum pressure supplied by the pump 12 (set via 16, 18).
  • the directional control valve 14 When moving back the directional control valve 14 in its basic position (0) of the circulation channel 32 is opened again steadily and accordingly controlled the connection to the flow channel 40.
  • a braking of the slewing gear can then be done by pressing the brake release valve 22, via which the ventilation pressure of the brake can be reduced.
  • the brake release valve 22 is switched from its illustrated basic position, so that the pressure port P is connected to the working port A.
  • the proportionally adjustable pilot valve pressure reducing valve 24
  • the ventilation pressure according to the control of the pressure reducing valve 24 to (0) controlled so that the brake brakes the slewing after a predetermined braking force.
  • the directional control valve 14 is moved in the manner described above in one of its (a) marked positions and thus the pressure medium supply to the hydraulic motor 2 via the flow channel 40 opened.
  • the outlet throttle valve 48 is controlled via the pilot valve 56 so that adjusts a biasing pressure in the working line 8, that is, at the output of the hydraulic motor 2, which is varied, for example, depending on the design or equipment of the excavator / crane.
  • This biasing pressure can be detected via the pressure sensors 28 (30) and regulated by the controller, so that a sequence control takes place.
  • the pressure medium volume flow is given by suitable control of the directional control valve 14 via the directional valve pilot valves 38 (36) and controlled by the respective drain in the outlet flow control valve 48 (50), the speed of the hydraulic motor 2. This speed can be detected by the speed sensor 26 and used for control.
  • FIG 3 shows a concrete embodiment of the control arrangement according to Figures 1 and 2 as a mobile control block 6, which has an approximately disc-shaped, very flat (perpendicular to the plane) valve housing 94, in which the entire above-described control arrangement is integrated.
  • a valve spool of the directional control valve is displaceable along the dot-dash line drawn valve axis 96, wherein the valve bore 94 passes through the valve housing 94 in the transverse direction (axis 96) and laterally closed by means of the control chambers limiting the lid 98, 100. The valve spool can thus be easily removed from the valve housing 94.
  • the other hydraulic components are used from the outside in the side surface (perpendicular to the plane) and thus very easily accessible.
  • the pilot valve 58, the directional valve pilot valve 38, the directional valve pilot valve 36, the pilot valve 56, the directional control valve 14, the outlet throttle valve 48, the pressure / suction valve 68, the circulation pressure compensator can be seen from the top left 34, the primary pressure limiting valve 16, the pressure / Nachsaugventil 70, the drain throttle valve 50, the pressure reducing valve 24th and the brake release valve 22 is shown.
  • the position of the terminals is also indicated - it can be seen that the control block according to the invention is designed to be extremely compact.
  • a hydraulic control arrangement for controlling a hydraulic consumer, in particular a consumer of a mobile working device.
  • the pressure medium supply via a directional control valve arrangement, via which a circulation channel is opened in a basic position, via which a pump of the control arrangement is connected to the tank.
  • the sequence control is carried out via separately controllable outlet throttle valves, which are preferably designed to be proportionally adjustable.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Valve Device For Special Equipments (AREA)
EP05015152A 2004-07-13 2005-07-12 Dispositif hydraulique de contrôle Not-in-force EP1616997B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004033891A DE102004033891A1 (de) 2004-07-13 2004-07-13 Hydraulische Steueranordnung

Publications (2)

Publication Number Publication Date
EP1616997A1 true EP1616997A1 (fr) 2006-01-18
EP1616997B1 EP1616997B1 (fr) 2010-09-15

Family

ID=35044597

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05015152A Not-in-force EP1616997B1 (fr) 2004-07-13 2005-07-12 Dispositif hydraulique de contrôle

Country Status (4)

Country Link
EP (1) EP1616997B1 (fr)
AT (1) ATE481534T1 (fr)
DE (2) DE102004033891A1 (fr)
DK (1) DK1616997T3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007062651A2 (fr) * 2005-11-30 2007-06-07 Sauer-Danfoss Aps Machine-outil, notamment mini-excavateur
CN100496789C (zh) * 2006-07-07 2009-06-10 江阴机械制造有限公司 自动速度跟随与压力曲线设定的小半径弯管顶推系统
DE102009015384B3 (de) * 2009-03-27 2010-09-16 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
CN106640817A (zh) * 2017-01-04 2017-05-10 浙江高宇液压机电有限公司 适用于双泵合分流液压系统的压力补偿型节能控制阀

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010055716B4 (de) 2010-12-22 2021-12-09 Robert Bosch Gmbh Hydraulischer Antrieb
DE102022212754A1 (de) 2022-11-29 2024-05-29 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zur Ansteuerung einer hydraulischen Haltebremse eines Drehwerks und Belüftungssystem für eine hydraulische Haltebremse eines Drehwerks

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2440714A1 (de) * 1974-08-24 1976-03-11 Rexroth Gmbh G L Vorrichtung zum lastunabhaengigen regeln eines hydraulikstromes
DE19904616A1 (de) 1999-02-05 2000-08-10 Mannesmann Rexroth Ag Steueranordnung für wenigstens zwei hydraulische Verbraucher und Druckdifferenzventil dafür
US6244158B1 (en) * 1998-01-06 2001-06-12 Fps, Inc. Open center hydraulic system with reduced interaction between branches

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2440714A1 (de) * 1974-08-24 1976-03-11 Rexroth Gmbh G L Vorrichtung zum lastunabhaengigen regeln eines hydraulikstromes
DE2440714C3 (de) 1974-08-24 1980-01-24 G.L. Rexroth Gmbh, 8770 Lohr Vorrichtung zum lastunabhängigen Regeln eines Hydraulikstromes
US6244158B1 (en) * 1998-01-06 2001-06-12 Fps, Inc. Open center hydraulic system with reduced interaction between branches
DE19904616A1 (de) 1999-02-05 2000-08-10 Mannesmann Rexroth Ag Steueranordnung für wenigstens zwei hydraulische Verbraucher und Druckdifferenzventil dafür

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007062651A2 (fr) * 2005-11-30 2007-06-07 Sauer-Danfoss Aps Machine-outil, notamment mini-excavateur
WO2007062651A3 (fr) * 2005-11-30 2007-10-18 Sauer Danfoss Aps Machine-outil, notamment mini-excavateur
CN100496789C (zh) * 2006-07-07 2009-06-10 江阴机械制造有限公司 自动速度跟随与压力曲线设定的小半径弯管顶推系统
DE102009015384B3 (de) * 2009-03-27 2010-09-16 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
WO2010108570A1 (fr) 2009-03-27 2010-09-30 Hydac Filtertechnik Gmbh Dispositif de soupape hydraulique
CN106640817A (zh) * 2017-01-04 2017-05-10 浙江高宇液压机电有限公司 适用于双泵合分流液压系统的压力补偿型节能控制阀

Also Published As

Publication number Publication date
DE502005010254D1 (de) 2010-10-28
DE102004033891A1 (de) 2006-02-16
ATE481534T1 (de) 2010-10-15
EP1616997B1 (fr) 2010-09-15
DK1616997T3 (da) 2010-11-08

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