EP1616997B1 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
EP1616997B1
EP1616997B1 EP05015152A EP05015152A EP1616997B1 EP 1616997 B1 EP1616997 B1 EP 1616997B1 EP 05015152 A EP05015152 A EP 05015152A EP 05015152 A EP05015152 A EP 05015152A EP 1616997 B1 EP1616997 B1 EP 1616997B1
Authority
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.)
Not-in-force
Application number
EP05015152A
Other languages
German (de)
French (fr)
Other versions
EP1616997A1 (en
Inventor
Jörg Willy Grünert
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
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Bosch Rexroth AG
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Publication of EP1616997A1 publication Critical patent/EP1616997A1/en
Application granted granted Critical
Publication of EP1616997B1 publication Critical patent/EP1616997B1/en
Not-in-force legal-status Critical Current
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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.
  • 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.
  • Such systems are for example in the DE 199 04 616 A1 described.
  • variable displacement pump does not necessarily have to be used.
  • the basic principle of such a control arrangement is in the DE 24 40 714 C3 described. 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 running 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.
  • this circulation channel is in accordance with the DE 24 40 714 C3 arranged a pressure compensator, 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 working device.
  • 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.
  • FIG. 1 shows the circuit diagram of a control block 1 for controlling a rotating mechanism 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 in FIG. 1 right channel is the flow channel 40, while the left, connected to the port B channel is the drain channel 42. With appropriate switching of the directional valve then the flow channel to the drainage channel and the drainage channel to the flow channel.
  • a pilot-operated outlet valve 48 and 50 which is biased in a closed position and can be controlled via a pilot pressure in a throttle position in which opened a throttle cross-section is via which the drain line 44, 46 is connected to a connecting line 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 port 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 control valve pilot valve 38 is connected to the pilot port PV via a pilot passage 72, with one passage section 72a leading to the input port P of the directional control valve 38, while another passage section 72b leads to the input port P of the other directional control valve 36 (in FIG FIG. 2 not shown).
  • 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 release of the brake 4 takes place by means of the brake release valve 22.
  • This is designed as a switching valve, which in its spring-loaded, in FIG. 2 illustrated basic position connected to a working port A brake channel 86 with a connected to a tank port T of the brake release valve 22, opening in the flow passage 74 section 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 circulation channel 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 blocking 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 by the pressure sensor 28 (30) and controlled by the controller, so that a flow 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 the FIGS. 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 ??? 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 drain throttle valve 48, the pressure / respiratory valve 68, the circulation pressure compensator 34, the primary pressure relief 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.

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  • 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)

Abstract

The device is connected by a constantly adjustable control valve arrangement with a pump and an expiration with a tank. The controller has in a basic position a rotating channel, which is connected with the tank and a rotating pressure limiter is provided. The position of the controller is on an accessible and controllable and a flow pipe for the argument supply of the consumer. The selector movement has an arranged expiration operational sequence (48, 50). The cross-section of the opening is independently adjustable of the control of the control valve (14). The load (2) has two connections, such as in each case an end throttle valve (48, 50) is provided. The device is a constantly adjustable 6-direction control valve (14).

Description

Die Erfindung betrifft eine hydraulische Steueranordnung zur Ansteuerung eines Verbrauchers gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic control arrangement for controlling a consumer according to the preamble of patent claim 1.

Derartige, beispielsweise aus der US 6 244 158 B1 bekannte hydraulische Steueranordnungen werden vorzugsweise bei mobilen Arbeitsgeräten, beispielsweise Mobilbaggern zur Ansteuerung von die unterschiedlichen Arbeitsbewegungen ermöglichenden Verbrauchern, wie beispielsweise Hydrozylindern oder Hydromotoren verwendet.Such, for example from the US Pat. No. 6,244,158 B1 known hydraulic control arrangements are preferably used in mobile work equipment, such as wheeled excavators for controlling the different working movements enabling consumers, such as hydraulic cylinders or hydraulic motors.

Dabei kommen unterschiedliche Steuerungskonzepte wie beispielsweise das LS-System mit dem Sonderfall einer LUDV-Steuerung oder das 6-Wege-Prinzip zum Einsatz. Bei den LS (Load Sensing)-Systemen wird der höchste Lastdruck der angesteuerten Verbraucher des mobilen Arbeitsgerätes an eine Verstellpumpe gemeldet und diese so geregelt, dass in einer Pumpenleitung ein um eine bestimmte Druckdifferenz Δp über dem Lastdruck liegender Pumpendruck vorliegt. Den verstellbaren Zumessblenden einer LS-Steuerung sind Individualdruckwaagen zugeordnet, die über den jeweiligen Zumessblenden eine vom Lastdruck unabhängige Druckdifferenz aufrecht erhalten. Bei den herkömmlicherweise mit LS-Steuerung bezeichneten Steueranordnungen sind diese Individualdruckwaagen stromaufwärts der Zumessblende angeordnet und drosseln zwischen der Pumpenleitung und den Zumessblenden den Fluidstrom so stark an, dass der Druck vor den Zumessblenden unabhängig vom Pumpendruck nur noch um eine bestimmte Druckdifferenz über dem individuellen Lastdruck liegt.Different control concepts are used, such as the LS system with the special case of a LUDV control or the 6-way principle. In the case of the LS (Load Sensing) systems, the highest load pressure of the driven consumers of the mobile implement is reported to a variable displacement pump and regulated so that in a pump line there is a pump pressure lying by a certain pressure difference .DELTA.p above the load pressure. 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. In the conventionally designated LS control arrangements, 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 ,

Beim Sonderfall einer LUDV-Steuerung sind die Individualdruckwaagen stromabwärts der Zumessblenden angeordnet und drosseln zwischen den Zumessblenden und der Last den Fluidstrom so stark an, dass der Druck nach allen Zumessblenden gleich, vorzugsweise gleich dem höchsten Lastdruck ist oder leicht über diesem liegt. Im Fall einer Unterversorgung ändert sich bei einer LUDV-Steuerung der Druckabfall über den Zumessblenden des Systems in gleicher Weise, so dass die voreingestellte Stromaufteilung zwischen den Zumessblenden erhalten bleibt. Derartige Systeme sind beispielsweise in der DE 199 04 616 A1 beschrieben.In the special case of a LUDV control, 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. In the case of an undersupply, 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. Such systems are for example in the DE 199 04 616 A1 described.

Beim sogenannten 6-Wege-Prinzip muss nicht notwendigerweise eine Verstellpumpe eingesetzt werden. Das Grundprinzip einer derartigen Steueranordnung ist in der DE 24 40 714 C3 beschrieben. Anwendungen dieses Systems werden auch unter den im Internet unter www.boschrexroth.de verfügbaren Datenblättern RD 64 122 oder RD 64 354 beschrieben.In the so-called 6-way principle, a variable displacement pump does not necessarily have to be used. The basic principle of such a control arrangement is in the DE 24 40 714 C3 described. 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.

Beim 6-Wege-Prinzip erfolgt die Ansteuerung des Verbrauchers, beispielsweise eines Drehwerkantriebs, über ein stetig verstellbares 6-Wege-Ventil, über das die beiden Arbeitsanschlüsse des Verbrauchers mit der als Konstantpumpe ausgeführten Pumpe oder einem Tank verbindbar sind. In der Grundposition des Wegeventils sind die Verbindungen zu den Arbeitsanschlüssen abgesperrt. Das Ventil ist in Open-Center-Bauweise ausgeführt, wobei die Pumpe in der Grundposition (Neutralstellung) Druckmittel drucklos in einen mit dem Tank verbundenen Umlaufkanal fördert. In diesem Umlaufkanal ist gemäß der DE 24 40 714 C3 eine Druckwaage angeordnet, die in Öffnungsrichtung von dem Druck stromabwärts des Wegeventils und in Schließrichtung von der Kraft einer Druckwaagenfeder und dem höchsten Lastdruck der Verbraucher des mobilen Arbeitsgerätes beaufschlagt ist. Diese Druckwaage wirkt gemeinsam mit dem Wegeventil als Stromregler, über den der Druckmittelvolumenstrom im Umlaufkanal lastdruckunabhängig konstant gehalten werden kann.In the 6-way principle, 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 running as a fixed displacement pump or a tank connected. 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. In this circulation channel is in accordance with the DE 24 40 714 C3 arranged a pressure compensator, 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 working device. 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.

Beim Aufsteuern des Wegeventils zur Druckmittelversorgung des Verbrauchers wird die Verbindung zum druckmittelbeaufschlagten Anschluss des Verbrauchers allmählich aufgesteuert, während die Verbindung zum Umlaufkanal gegenläufig angedrosselt wird. Parallel dazu wird entsprechend über das Wegeventil ein Ablaufquerschnitt aufgesteuert, über den das Druckmittel vom Verbraucher zum Tank hin abströmt. Durch die Druckwaage ist gewährleistet, dass im Umlaufkanal die gleichen Druckverhältnisse wie im Vorlauf zum Verbraucher vorliegen.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.

Bei einer derartigen Konstruktion sind somit Vorlauf und Ablauf von dem einzigen Kolben des Wegeventils gesteuert, so dass die Querschnitte entsprechend aufeinander abgestimmt werden müssen und somit eine individuelle Beeinflussung des Druckmittelvolumenstroms im Vorlauf oder im Ablauf nicht möglich ist.In such a construction, thus the flow and the flow are controlled by the single piston of the directional control valve, so that the cross sections must be adjusted to each other and thus an individual influence of the pressure medium flow in the flow or in the process is not possible.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine nach dem 6-Wege-Prinzip aufgebaute hydraulische Steueranordnung zu schaffen, bei der mit geringem vorrichtungstechnischen Aufwand eine Veränderung der Druck- /Strömungsverhältnisse im Ablauf ermöglicht ist.In contrast, 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.

Diese Aufgabe wird durch eine hydraulische Steueranordnung mit den Merkmalen des Patentanspruchs 1 gelöst.This object is achieved by a hydraulic control arrangement having the features of patent claim 1.

Erfindungsgemäß wird die hydraulische Steueranordnung im Ablauf mit zumindest einem Ablaufdrosselventil ausgeführt, dessen Öffnungsquerschnitt unabhängig von der Ansteuerung eines stetig verstellbaren Wegeventils ansteuerbar ist, über das der Verbraucher mit Druckmittel versorgbar ist und die Verbindung zu einem Umlaufkanal auf- bzw. zusteuerbar ist.According to the invention, 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 zuusteuerbar.

Durch das erfindungsgemäße Ablaufdrosselventil wird somit eine separate Ablaufnut gebildet, die je nach vorliegenden Betriebsbedingungen in geeigneter Weise unabhängig von dem Zulaufquerschnitt ansteuerbar ist. So lässt sich beispielsweise über das Ablaufdrosselventil im Ablauf ein Druck zum Vorspannen des Verbrauchers einstellen. Des Weiteren kann beispielsweise der Volumenstrom über den Zulauf vorgegeben und dann durch Einstellung des Ablaufdrosselventils die Geschwindigkeit des Verbrauchers eingestellt werden.By the discharge throttle valve according to the invention thus 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. For example, a pressure for biasing the load can be set via the outlet throttle valve in the outlet. Furthermore, for example, 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.

Diese proportionale Steuerung des Ablaufquerschnittes ermöglicht es, die Steueranordnung mit minimalem Aufwand an unterschiedliche Betriebsbedingungen und konstruktive Vorgaben anzupassen.This proportional control of the flow cross-section makes it possible to adapt the control arrangement with minimal effort to different operating conditions and design specifications.

Bei Verbrauchern mit zwei Arbeitsanschlüssen, beispielsweise Differentialzylindern oder Hydromotoren wird es bevorzugt, wenn jedem Arbeitsanschluss eine Ablaufleitung mit einem Ablaufdrosselventil zugeordnet ist, so dass der Ablauf in beiden Richtungen in der vorbeschriebenen Weise steuerbar ist.For consumers with two working ports, such as differential cylinders or hydraulic motors, it is preferred if 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.

Es wird bevorzugt, das stetig verstellbare Wegeventil als 6-Wege-Ventil auszuführen, so dass die Steueranordnung sehr kompakt baut.It is preferred to carry out the continuously adjustable directional control valve as a 6-way valve, so that the control arrangement is very compact.

Erfindungsgemäß wird es bevorzugt, das Ablaufdrosselventil stetig verstellbar auszuführen, wobei die Einstellung des Drosselquerschnittes vorzugsweise mittels eines Vorsteuerventils erfolgt. An Stelle einer derartigen elektrohydraulischen Ansteuerung kann selbstverständlich auch eine hydraulische oder elektromechanische Vorsteuerung des Ablaufdrosselventils gewählt werden.According to the invention, it is preferable to make the outlet throttle valve continuously adjustable, wherein the adjustment of the throttle cross section preferably takes place by means of a pilot control valve. Of course, instead of such electrohydraulic control also a hydraulic or electro-mechanical pilot control of the outlet throttle valve can be selected.

Bei einem besonders einfach aufgebauten Ausführungsbeispiel erfolgt die Ansteuerung des Wegeventils über Wegeventilvorsteuerventile, die vorzugsweise vom gleichen Steuerdruck wie die Vorsteuerventile des Ablaufdrosselventils versorgt werden.In a particularly simply constructed embodiment, 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.

Zur Begrenzung des von der Pumpe gelieferten Maximaldrucks, kann zwischen dem Wegeventil und der Pumpe ein Primärdruckbegrenzungsventil vorgesehen sein.To limit the maximum pressure delivered by the pump, a primary pressure relief valve may be provided between the directional control valve and the pump.

In dem Fall, in dem eine Momentensteuerung durchgeführt werden soll, kann das Druckbegrenzungsventil beispielsweise über den vorgenannten Steuerdruck angesteuert werden und der Steuerraum über ein weiteres, elektrisch ansteuerbares Druckbegrenzungsventil mit dem Tank verbunden sein.In the case in which a torque control is to be performed, 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.

Zur Vermeidung von Kavitationen wird zwischen dem Druckmittelvorlauf und dem Druckmittelablauf jeweils ein Druck-/Nachsaugventil vorgesehen, das als Sekundärdruckbegrenzungsventil wirkt.In order to avoid cavitations between the pressure medium flow and the pressure fluid outlet each a pressure / suction valve is provided which acts as a secondary pressure relief valve.

Soll mit der erfindungsgemäßen Steueranordnung beispielsweise ein Drehwerk eines Mobilbaggers betätigt werden, so kann der Hydromotor des Drehwerks mit einer Bremse versehen sein, die als Haltebremse dient oder als dynamische Bremse mit variablem Lüftungsdruck ausgeführt sein kann. Eine derartige Bremse ist mechanisch, beispielsweise durch eine Feder in Richtung Bremseingriff vorgespannt und wird hydraulisch mittels eines Bremslüftungsdruckes außer Eingriff gebracht. Dieser kann dem vorgenannten Steuerversorgungsdruck entsprechen oder mittels eines Druckreduzierventils angepasst werden, um den Bremseingriff bei einer dynamischen Bremse zu steuern.If, for example, a slewing gear of a mobile excavator is to be actuated with the control arrangement according to the invention, then 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. Such 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.

Bei einem bevorzugten Ausführungsbeispiel werden die im Vorlauf und im Ablauf anliegenden Drücke mittels jeweils eines Druckaufnehmers erfasst und in Abhängigkeit von diesen Signalen das Wegeventil und das Ablaufdrosselventil angesteuert. In dem Fall, in dem der Verbraucher ein Hydromotor ist, kann dessen Drehzahl mittels eines Drehzahlsensors erfasst werden und in Abhängigkeit von diesem Signal die Geschwindigkeit des Hydromotors gesteuert werden.In a preferred embodiment, 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. In the case in which 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.

Bei einer konkreten Ausführungsform der erfindungsgemäßen Steueranordnung ist diese in eine Ventilscheibe integriert.In a specific embodiment of the control arrangement according to the invention, this is integrated in a valve disc.

Die Druckmittelversorgung erfolgt vorzugsweise mittels einer Konstantpumpe.The pressure medium supply is preferably carried out by means of a constant pump.

Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand weiterer Unteransprüche.Other advantageous developments of the invention are the subject of further subclaims.

Im Folgenden wird ein bevorzugtes Ausführungsbeispiel der Erfindung an Hand schematischer Zeichnungen näher erläutert. Es zeigen:

  • Figur 1 ein Schaltbild einer hydraulischen Steueranordnung zur Ansteuerung eines Drehwerks;
  • Figur 2 eine Detaildarstellung des Schaltbilds aus Figur 1 und
  • Figur 3 eine Draufsicht auf ein konkretes Ausführungsbeispiel eines Steuerblocks.
In the following, a preferred embodiment of the invention will be explained in more detail with reference to schematic drawings. Show it:
  • FIG. 1 a circuit diagram of a hydraulic control arrangement for controlling a slewing gear;
  • FIG. 2 a detailed representation of the circuit diagram FIG. 1 and
  • FIG. 3 a plan view of a concrete embodiment of a control block.

Figur 1 zeigt den Schaltplan eines Steuerblocks 1 zur Ansteuerung eines Drehwerks eines Mobilbaggers. Das Drehwerk wird durch einen Hydromotor 2 betätigt, dessen Antriebswelle über eine Haltebremse 4 festlegbar ist. FIG. 1 shows the circuit diagram of a control block 1 for controlling a rotating mechanism 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.

Die Druckmittelversorgung des Hydromotors 2 erfolgt über einen Steuerblock 6, dessen Arbeitsanschlüsse A, B über zwei Arbeitsleitungen 8 bzw. 10 mit den Anschlüssen des Hydromotors 2 verbunden sind. Das Druckmittel wird mittels einer Pumpe 12 gefördert, die an einen Druckanschluss P des Steuerblocks 6 angeschlossen ist und das vom Verbraucher zurück strömende Druckmittel wird über einen Tankanschluss T zu einem Tank geführt. Der Steuerblock 1 hat des Weiteren noch einen Vorsteueranschluss PV, einen Bremsanschluss 1 und einen Ablaufanschluss L, der ebenfalls mit dem Tank verbunden ist. Der sich einstellende Lastdruck oder ein entsprechender Druck kann über einen Steueranschluss X abgegriffen werden.The pressure medium supply of the hydraulic motor 2 via a control block 6, the working ports A, B are connected via two working lines 8 and 10 with the terminals of the hydraulic motor 2. 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.

Gemäß Figur 1 enthält der Steuerblock 1 ein stetig verstellbares Wegeventil 14, über das die Druckmittelzufuhr zum Hydromotor 2 gesteuert wird. Zwischen Wegeventil 14 und der Pumpe 12 ist ein Primärdruckbegrenzungsventil 16 angeordnet, über das der Pumpendruck begrenzt ist. Zur Momentensteuerung kann dem Primärdruckbegrenzungsventil 16 optional ein weiteres Druckbegrenzungsventil 18 zugeordnet sein, über das ein Steuerraum des Primärdruckbegrenzungsventils 16 mit dem Ablaufanschluss L verbindbar ist.According to FIG. 1 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. For torque control, 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.

Die Bremse 4 ist über Federn in Richtung Bremseingriff vorgespannt. Das Lüften der Bremse erfolgt hydraulisch über eine Bremslüftungsleitung 20, die an den Bremsanschluss 1 angeschlossen ist. Dieser kann über ein Bremslüftungsventil 22 mit dem Ablaufanschluss L (Bremse in Eingriff) oder mit dem am Vorsteueranschluss PV anliegenden Steuerdruck beaufschlagt werden, um die Bremse zu lüften.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.

In dem Fall, in dem keine Haltebremse sondern eine dynamische Bremse eingesetzt wird, kann der Bremsdruck in der Bremslüftungsleitung 20 über ein 3-Wege-Druckreduzierventil 24 eingestellt werden. Sowohl das Bremslüftungsventil 22 als auch das Druckreduzierventil 24 sind elektrisch betätigt.In the case in which no holding brake but a dynamic brake is used, 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.

Die Drehzahl des Hydromotors 2 wird über einen Drehzahlsensor 26 und die Drücke in den beiden Arbeitsleitungen 8, 10 werden über Druckaufnehmer 28 bzw. 30 erfasst.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.

Die nach dem 6-Wege-Prinzip ausgeführte Steueranordnung hat - wie im Folgenden noch näher dargelegt wird-einen mit dem Tankanschluss T verbundenen Umlaufkanal 32, der mit einem Umlaufanschluss C des Wegeventils 14 verbunden ist. In dem Umlaufkanal 32 ist eine Umlaufdruckwaage 34 vorgesehen, deren Funktion weiter unten erläutert wird.The control arrangement designed according to the 6-way principle has-as will be explained in more detail below-a circulation channel 32 connected to the tank connection T and connected to a circulation connection C of the directional control valve 14. In the circulation channel 32, a circulation pressure compensator 34 is provided, whose function will be explained below.

Die Ansteuerung des Wegeventils 14 erfolgt über zwei Wegeventilvorsteuerventile 36, 38, die als Druckreduzierventile ausgeführt sind, wobei deren Eingangsanschluss jeweils mit dem Vorsteueranschluss PV verbunden ist.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.

Das Wegeventil 14 hat zwei Arbeitsanschlüsse A, B, die über zwei Kanäle 40, 42 mit den Anschlüssen A, B des Steuerblocks 6 verbunden sind. Zur Vereinfachung der Erläuterung sei angenommen, dass der in Figur 1 rechte Kanal der Vorlaufkanal 40 ist, während der linke, mit dem Anschluss B verbundene Kanal der Ablaufkanal 42 ist. Bei entsprechender Umschaltung des Wegeventils wird dann der Vorlaufkanal zum Ablaufkanal und der Ablaufkanal zum Vorlaufkanal.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. To simplify the explanation, it is assumed that the in FIG. 1 right channel is the flow channel 40, while the left, connected to the port B channel is the drain channel 42. With appropriate switching of the directional valve then the flow channel to the drainage channel and the drainage channel to the flow channel.

Von jedem der Kanäle 40, 42 zweigt eine Ablaufleitung 44 bzw. 46 ab, in der jeweils ein vorgesteuertes Ablaufdrosselventil 48 bzw. 50 angeordnet ist, das in eine Schließposition vorgespannt ist und über einen Vorsteuerdruck in eine Drosselposition aufsteuerbar ist, in der ein Drosselquerschnitt aufgesteuert wird, über den die Ablaufleitung 44, 46 mit einer Verbindungsleitung 52 bzw. 54 verbunden ist, die jeweils stromabwärts der Umlaufdruckwaage 34 in den Umlaufkanal 32 einmündet. Die Vorsteuerung der Ablaufdrosselventile 48, 50 erfolgt jeweils über Vorsteuerventile 56, 58, die ebenfalls als Druckreduzierventile ausgeführt sind, deren Eingangsanschluss mit dem Vorsteueranschluss PV verbunden ist.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 opened a throttle cross-section is via which the drain line 44, 46 is connected to a connecting line 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.

Weitere Details werden im Folgenden an Hand der vergrößerten Teildarstellung der Steueranordnung 1 erläutert, wobei in Figur 2 lediglich der rechte Teil (Ansicht nach Figur 1) des Steuerblocks 6 dargestellt ist.Further details are explained below with reference to the enlarged partial representation of the control arrangement 1, wherein in FIG. 2 only the right part (view after FIG. 1 ) of the control block 6 is shown.

Demgemäß ist der Druckanschluss P des Steuerblocks 6 über einen Zulaufkanal 60 mit einem Eingangsanschluss P des Wegeventils 14 verbunden. Dieses hat des Weiteren noch einen Eingangsanschluss P', an dem ebenfalls der Druck im Zulaufkanal 60 anliegt und der in der dargestellten federvorgespannten Grundposition (0) des Wegeventils 14 mit dem Umlaufanschluss C verbunden ist, an die der Umlaufkanal 32 angeschlossen ist. In diesem Umlaufkanal 32 ist die vorbeschriebene Umlaufdruckwaage 34 angeordnet. Die Druckwaage 34 ist in Schließrichtung von der Kraft einer Feder und dem Druck in einem Steuerkanal 62 beaufschlagt, der an einen Ausgang eines Wechselventils 64 angeschlossen ist, dessen Eingänge einerseits mit dem Steueranschluss X des Steuerblocks 1 und andererseits mit einem Steueranschluss Y des Wegeventils 14 verbunden ist, der in der Grundposition (0) mit einem Tankanschluss T verbunden ist. Dieser mündet über eine kurze Tankleitung 66 in die zum Umlaufkanal 32 führende Verbindungsleitung 54 ein. In Öffnungsrichtung ist die Druckwaage 34 von dem Druck im Druckmittelströmungspfad zwischen dem Wegeventil 14 und der Druckwaage 34 beaufschlagt. Das Wegeventil 14 ist so ausgebildet, dass die Verbindung zum Umlaufkanal 32 in der Grundposition (0) vollständig aufgesteuert ist - das heißt, die Verbindung zur Pumpe P ist geöffnet und lässt den Druckmittelvolumenstrom von P' über C, den Umlaufkanal 32 und die Druckwaage 34 abströmen.Accordingly, 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. In this circulation channel 32, 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 port 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.

In den mit (a) dargestellten Steuerpositionen des Wegeventils 14 ist der Eingangsanschluss P mit dem Ausgangsanschluss A und dem Steueranschluss Y verbunden. Mit zunehmender Verschiebung in die Positionen (a) wird die Verbindung zum Umlaufkanal 32 zugesteuert. Entsprechend wird bei einer Verschiebung in eine der mit (b) gekennzeichneten Positionen der Eingangsanschluss P mit dem Arbeitsanschluss B und mit dem Steueranschluss Y verbunden. Der Umlaüfkanal 32 wird entsprechend mit zunehmender Betätigung des Wegeventils 14 zugesteuert. Das heißt, bei der erfindungsgemäßen Lösung erfolgt über das Wegeventil 14 die Steuerung der Druckmittelvolumenströme im Umlaufkanal 32 und im jeweils wirksamen Vorlaufkanal 40 (42).In the control positions of the directional control valve 14 shown by (a), 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).

Bei dem dargestellten Ausführungsbeispiel sind die beiden Kanäle 40, 42 und die Verbindungsleitungen 52, 54 jeweils über ein Druck-/Nachsaugventil 68, 70 miteinander verbunden. Diese wirken als Sekundärdruckbegrenzungsventile und ermöglichen es, zur Vermeidung von Kavitationen bei ziehender Last Druckmittel aus dem Tank nachzusaugen.In the illustrated embodiment, 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.

Die vorbeschriebene Betätigung des Schiebers des Wegeventils 14 erfolgt mittels der beiden Wegeventilvorsteuerventile 36, 38, von denen in Figur 2 der Einfachheit halber lediglich eines dargestellt ist. Das Wegeventilvorsteuerventil 38 ist über einen Vorsteuerkanal 72 mit dem Vorsteueranschluss PV verbunden, wobei ein Leitungsabschnitt 72a zum Eingangsanschluss P des Wegeventilvorsteuerventils 38 führt, während ein anderer Leitungsabschnitt 72b zum Eingangsanschluss P des anderen Wegeventilvorsteuerventils 36 führt (in Figur 2 nicht dargestellt). Ein Anschluss T des Wegeventilvorsteuerventils 38 ist jeweils mit einem Ablaufkanal 74 verbunden, der zum Ablaufanschluss L führt. Ein Ausgangsanschluss A der Wegeventilvorsteuerventile 38 (36) ist jeweils über eine Wegeventilsteuerleitung 76 bzw. 78 mit den Steuerräumen des Wegeventils 14 verbunden. Die 3-Wege-Druckreduzierventile 36, 38 werden über die zentrale Steuerung des Mobilgeräts elektrisch angesteuert.The above-described operation of the slide of the directional control valve 14 by means of the two-way valve pilot valves 36, 38, of which in FIG. 2 simplicity only one is shown. The directional control valve pilot valve 38 is connected to the pilot port PV via a pilot passage 72, with one passage section 72a leading to the input port P of the directional control valve 38, while another passage section 72b leads to the input port P of the other directional control valve 36 (in FIG FIG. 2 not shown). 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.

Die Ansteuerung der beiden Ablaufdrosselventile 48, 50 erfolgt entsprechend über als ebenfalls als 3-Wege-Druckreduzierventile ausgeführte Vorsteuerventile 58 (56), deren Eingangsanschluss P an den Vorsteuerkanal 72, Tankanschluss T an den Ablaufkanal 74 und Ausgangsanschluss A an den Steuerraum des jeweiligen Ablaufdrosselventils 50 bzw. 48 angeschlossen sind.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.

Die Begrenzung des von der Konstantpumpe 12 gelieferten Drucks erfolgt über das Primärdruckbegrenzungsventil 16, das bei Überschreiten des Maximaldrucks eine Verbindung zu einem Entlastungskanal 80 aufsteuert, der in den Umlaufkanal 32 einmündet.The limitation of the pressure supplied by the fixed displacement pump 12 via the primary pressure limiting valve 16, which opens a connection to a discharge channel 80 when the maximum pressure is exceeded, which opens into the circulation channel 32.

Der Auslösewert des Druckbegrenzungsventils 16 lässt sich zum Einen über eine einstellbare Feder einstellen und zum Anderen über eine hydraulische Vorsteuerung zur Momentensteuerung anpassen. Diese hydraulische Vorsteuerung ist durch das elektrisch betätigte Druckbegrenzungsventil 18 gebildet, das in einem an einen Steueranschluss X des Druckbegrenzungsventils 16 angeschlossenen Kanal 82 angeordnet ist, dieser Kanal 82 mündet in den Ablaufkanal 74 ein, so dass sich bei Öffnen des Druckbegrenzungsventils 18 der im Steuerraum des Primärdruckbegrenzungsventils 16 anliegende Steuerdruck absenken lässt. Ein Steueranschluss Y des Primärdruckbegrenzungsventils 16 ist über eine gestrichelt angedeutete Leckageleitung 84 ebenfalls mit dem Ablaufkanal 74 verbunden.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.

Wie bereits erläutert, erfolgt das Lüften der Bremse 4 mittels des Bremslüftungsventils 22. Dieses ist als Schaltventil ausgeführt, das in seiner federvorgespannten, in Figur 2 dargestellten Grundposition einen an einen Arbeitsanschluss A angeschlossenen Bremskanal 86 mit einem an einen Tankanschluss T des Bremslüftungsventils 22 angeschlossenen, im Ablaufkanal 74 mündenden Abschnitt 88 verbindet. Durch elektrisches Umschalten des Bremslüftungsventils 22 wird ein Druckanschluss P mit dem Arbeitsanschluss A verbunden und der Tankanschluss T abgesperrt. Der Druckanschluss P mündet über eine Lüftungsleitung 90 in den Abschnitt 72a des Vorsteuerkanals 72 ein, so dass dann im Bremskanal 86 der Vorsteuerdruck anliegt. Der Bremskanal 86 ist an einen Druckanschluss P des Druckreduzierventils 24 angeschlossen, dessen Tankanschluss T mit dem Ablaufkanal 74 und dessen Ausgangsanschluss A über einen Bremslüftungskanal 92 mit dem Bremsanschluss 1 verbunden ist. Das Druckreduzierventil 24 ist elektrisch betätigbar, um den am Vorsteueranschluss PV anliegenden Vorsteuerdruck auf einen geeigneten Bremslüftungsdruck zu reduzieren und somit eine dynamisch wirkende Bremse entsprechend anzusteuern. Wie bereits erwähnt, kann das Druckreduzierventil 24 auch entfallen, so dass der Lüftungsdruck stets im Wesentlichen dem Vorsteuerdruck entspricht.As already explained, the release of the brake 4 takes place by means of the brake release valve 22. This is designed as a switching valve, which in its spring-loaded, in FIG. 2 illustrated basic position connected to a working port A brake channel 86 with a connected to a tank port T of the brake release valve 22, opening in the flow passage 74 section 88 connects. By electrically switching the brake release valve 22, 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. As already mentioned, the pressure reducing valve 24 can also be omitted, so that the ventilation pressure always substantially corresponds to the pilot pressure.

Zum besseren Verständnis sei die Funktion der Steueranordnung an Hand einiger Betriebszustände erläutert.For a better understanding, the function of the control arrangement is explained on the basis of a few operating states.

Offener KreisOpen circle

Es sei angenommen, dass zur Ansteuerung des Hydromotors 2 das Wegeventil 14 zunächst in Richtung seiner mit (a) gekennzeichneten Positionen verschoben wird. Dabei wird zunächst über Feinsteuernuten des Wegeventils 14 die Verbindung vom Druckanschluss P zum Arbeitsanschluss A stetig aufgesteuert, während der über den Umlaufkanal 32 abströmende Druckmittelvolumenstrom entsprechend über Feinsteuernuten angedrosselt wird. Mit weiterem Verschieben des Ventilschiebers des Wegeventils 14 wird der Druckmittelvolumenstrom zunehmend vom Umlaufkanal 32 zum Vorlaufkanal 40 umgesteuert. Die Druckwaage 34 stellt sich dabei jeweils in eine Regelposition ein, dass an den Anschlüssen A, C des Wegeventils 14 etwa der gleiche Druck anliegt.It is assumed that 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 circulation channel 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.

Das Druckmittel wird dann über den Vorlaufkanal 40, den Arbeitsanschluss A des Steuerblocks 6 und die Arbeitsleitung 10 zum Eingangsanschluss des Hydromotors 2 geführt.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.

Dabei verbleibt das an den Vorlaufkanal 40 angeschlossene Ablaufdrosselventil 50 in seiner federvorgespannten Sperrposition und das im Ablaufkanal 42 liegende Ablaufdrosselventil 48 wird durch geeignete Ansteuerung des Vorsteuerventils 56 in seine vollständig geöffnete Stellung gebracht, so dass das vom Hydromotor 2 zurückströmende Druckmittel ohne Androsselung über die Arbeitsleitung 8, den Anschluss B des Steuerblocks 6, die Ablaufleitung 44, das geöffnete Ablaufdrosselventil 48, die Verbindungsleitung 52 zum Tankanschluss T hin abströmen kann.In this case, the flow restrictor valve 50 connected to the flow channel 40 remains in its spring-biased blocking 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.

Die Geschwindigkeit des Hydromotors 2 ist dann durch die Einstellung des Wegeventils 14 und des maximal von der Pumpe 12 gelieferten Druckes (eingestellt über 16, 18) bestimmt. Beim Zurückfahren des Wegeventils 14 in seine Grundposition (0) wird der Umlaufkanal 32 wieder stetig aufgesteuert und entsprechend die Verbindung zum Vorlaufkanal 40 zugesteuert.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). 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.

Ein Abbremsen des Drehwerks kann dann durch Betätigen des Bremslüftungsventils 22 erfolgen, über das der Lüftungsdruck der Bremse abgebaut werden kann. Dazu wird das Bremslüftungsventil 22 aus seiner dargestellten Grundposition umgeschaltet, so dass der Druckanschluss P mit dem Arbeitsanschluss A verbunden ist. Bei einer dynamischen Bremse wird entsprechend das proportional verstellbare Vorsteuerventil (Druckreduzierventil 24) angesteuert und der Lüftungsdruck entsprechend der Ansteuerung des Druckreduzierventils 24 nach (0) geregelt, so dass die Bremse nach einem vorbestimmten Bremskraftverlauf das Drehwerk abbremst.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. For this purpose, 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. In a dynamic brake, the proportionally adjustable pilot valve (pressure reducing valve 24) is controlled accordingly and 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.

AblaufregelungDischarge control

Das Wegeventil 14 wird in der vorbeschriebenen Weise in eine seiner mit (a) gekennzeichneten Positionen verfahren und somit die Druckmittelzufuhr zum Hydromotor 2 über den Vorlaufkanal 40 aufgesteuert. Das Ablaufdrosselventil 48 wird über das Vorsteuerventil 56 so angesteuert, dass sich in der Arbeitsleitung 8, das heißt am Ausgang des Hydromotors 2 ein Vorspanndruck einstellt, wobei dieser beispielsweise je nach Ausführung oder Ausrüstung des Baggers/Krans variiert wird. Dieser Vorspanndruck kann über die Druckaufnehmer 28 (30) erfasst und von der Steuerung eingeregelt werden, so dass eine Ablaufsteuerung erfolgt.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 by the pressure sensor 28 (30) and controlled by the controller, so that a flow control takes place.

Geschwindigkeitssteuerungspeed control

In diesem Betriebsmodus erfolgt eine stärkere Vorspannung des Ablaufs als beim vorbeschriebenen Betriebszustand. Das heißt, der Druckmittelvolumenstrom wird bei geeigneter Ansteuerung des Wegeventils 14 über die Wegeventilvorsteuerventile 38 (36) vorgegeben und über das jeweilige im Ablauf liegende Ablaufdrosselventil 48 (50) die Geschwindigkeit des Hydromotors 2 gesteuert. Diese Geschwindigkeit kann über den Drehzahlsensor 26 erfasst und zur Regelung verwendet werden.In this mode of operation there is a stronger bias of the process than in the above-described operating condition. That is, 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.

Figur 3 zeigt eine konkrete Ausführung der Steueranordnung gemäß den Figuren 1 und 2 als Mobilsteuerblock 6, der ein etwa scheibenförmiges, sehr flaches (senkrecht zur Zeichenebene) Ventilgehäuse 94 aufweist, in das die gesamte vorbeschriebene Steueranordnung integriert ist. Ein Ventilschieber des Wegeventils ist dabei entlang der strichpunktiert eingezeichneten Ventilachse 96 verschiebbar, wobei die Ventilbohrung das Ventilgehäuse 94 in Querrichtung (Achse 96) durchsetzt und seitlich mittels der die Steuerräume begrenzenden Deckel 98, 100 verschlossen ist. Der Ventilschieber lässt sich somit auf einfache Weise aus dem Ventilgehäuse 94 entnehmen. FIG. 3 shows a concrete embodiment of the control arrangement according to the FIGS. 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.

Die sonstigen hydraulischen Bauelemente sind von außen her in die Seitenfläche (senkrecht zur Zeichenebene) eingesetzt und somit sehr gut zugänglich. In der Darstellung gemäß Figur 3 sind von links oben zu sehen das ???, das Vorsteuerventil 58, das Wegeventilvorsteuerventil 38, das Wegeventilvorsteuerventil 36, das Vorsteuerventil 56, das Wegeventil 14, das Ablaufdrosselventil 48, das Druck-/Nachsaugventil 68, die Umlaufdruckwaage 34, das Primärdruckbegrenzungsventil 16, das Druck-/Nachsaugventil 70, das Ablaufdrosselventil 50, das Druckreduzierventil 24 und das Bremslüftungsventil 22 dargestellt. Die Lage der Anschlüsse ist ebenfalls angedeutet - man sieht, dass der erfindungsgemäße Steuerblock äußerst kompakt ausgeführt ist.The other hydraulic components are used from the outside in the side surface (perpendicular to the plane) and thus very easily accessible. In the illustration according to FIG. 3 from left top are the ???, 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 drain throttle valve 48, the pressure / respiratory valve 68, the circulation pressure compensator 34, the primary pressure relief 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.

Offenbart ist eine hydraulische Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers, insbesondere eines Verbrauchers eines mobilen Arbeitsgerätes. Die Druckmittelzufuhr erfolgt über eine Wegeventilanordnung, über die in einer Grundposition ein Umlaufkanal aufgesteuert ist, über den eine Pumpe der Steueranordnung mit dem Tank verbunden ist. Die Ablaufsteuerung erfolgt über separat ansteuerbare Ablaufdrosselventile, die vorzugsweise proportional verstellbar ausgeführt sind.Disclosed is 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.

Bezugszeichenliste:LIST OF REFERENCE NUMBERS

11
Steuerblockcontrol block
22
Hydromotorhydraulic motor
44
Bremsebrake
66
Steuerblockcontrol block
88th
Arbeitsleitungworking line
1010
Arbeitsleitungworking line
1212
Pumpepump
1414
Wegeventilway valve
1616
PrimärdruckbegrenzungsventilPrimary pressure relief valve
1818
DruckbegrenzungsventilPressure relief valve
2020
BremslüftungsleitungBrake release line
2222
BremslüftungsventilBrake release valve
2424
DruckreduzierventilPressure reducing valve
2626
DrehzahlsensorSpeed sensor
2828
DruckaufnehmerPressure transducer
3030
DruckaufnehmerPressure transducer
3232
Umlaufkanalcirculation channel
3434
UmlaufdruckwaagePressure compensator
3636
WegeventilvorsteuerventilWay valve pilot valve
3838
WegeventilvorsteuerventilWay valve pilot valve
4040
Kanalchannel
4242
Kanalchannel
4444
Ablaufleitungdrain line
4646
Ablaufleitungdrain line
4848
AblaufdrosselventilOutlet throttle valve
5050
AblaufdrosselventilOutlet throttle valve
5252
Verbindungsleitungconnecting line
5454
Verbindungsleitungconnecting line
5656
Vorsteuerventilpilot valve
5858
Vorsteuerventilpilot valve
6060
Zulaufkanalinlet channel
6262
Steuerkanalcontrol channel
6464
Wechselventilshuttle valve
6666
Tankleitungtank line
6868
Druck-/NachsaugventilPressure / anti-cavitation valve
7070
Druck-/NachsaugventilPressure / anti-cavitation valve
7272
Vorsteuerkanalpilot passage
7474
Ablaufkanaldrain channel
7676
WegeventilsteuerleitungWay valve control line
7878
WegeventilsteuerleitungWay valve control line
8080
Entlastungskanalrelief channel
8282
Kanalchannel
8484
Leckageleitungleakage line
8686
Bremskanalbrake channel
8888
Abschnittsection
9090
Lüftungsleitungvent line
9292
BremsdruckkanalBrake pressure channel
9494
Ventilgehäusevalve housing
9696
Achseaxis
9898
Deckelcover
100100
Deckelcover

Claims (15)

  1. A hydraulic control arrangement for actuating a hydraulic consumer (2), especially of a mobile machine, wherein that consumer (2) is connectable via an inlet to a pump (12) and via an outlet to a tank by means of a continuously variable directional valve arrangement (14, 48, 50), and a continuously variable directional valve (14) of the directional valve arrangement in a home position (0) opens a bypass channel (32) via which the pump is connected to the tank and in which a bypass pressure compensator (34) is disposed, and wherein, in the control positions (a, b) of the directional valve, the bypass channel (32) can be closed and a channel connectable to a port of the consumer can be opened as an inlet line (40 or 42) to supply the consumer with pressure medium, wherein a channel connectable to a second port of the consumer forms an outlet (42 or 40, respectively) from the consumer, characterised in that the directional valve arrangement (14, 48, 50) has, in an outlet line (44, 46) branching off the channel of the outlet (42 or 40, respectively), an outlet throttle valve (48, 50) whose opening cross-section is adjustable independently of the actuation of the directional valve (14) and whose outlet is connected via a connecting line (52, 54) to the bypass channel (32) leading to the tank (T).
  2. A control arrangement according to patent claim 1, wherein the two ports of the consumer (2) are each assigned an outlet throttle valve (48, 50).
  3. A control arrangement according to patent claim 1 or 2, wherein the directional valve is a continuously variable 6-way valve (14).
  4. A control arrangement according to any one of the preceding patent claims, wherein the outlet throttle valve (48, 50) is of a continuously variable configuration.
  5. A control arrangement according to patent claim 4 having a pilot valve (56, 58) for actuating the outlet throttle valve (48, 50).
  6. A control arrangement according to patent claim 4 having two directional valve pilot valves (36, 38) for actuating the directional valve (14), wherein the same control supply pressure is applied to those directional valve pilot valves (36, 38) as is applied to the pilot valve (56, 58).
  7. A control arrangement according to any one of the preceding patent claims having a primary pressure limiting valve (16) between pump (12) and directional valve (14).
  8. A control arrangement according to patent claim 7, wherein the primary pressure limiting valve (16) has a control port (X) which is connectable to the tank (T) via a pressure limiting valve (18).
  9. A control arrangement according to any one of the preceding patent claims, having a pressure/anticavitation valve (68, 70) disposed in each case between one of the channels (40, 42) and the connecting line (52, 54).
  10. A control arrangement according to any one of the preceding patent claims, wherein the consumer is assigned a hydraulically operated brake (4) having a brake releasing valve (22) via which a brake releasing pressure can be applied to a pressure chamber of the brake (4), which pressure chamber is effective in the direction of release.
  11. A control arrangement according to patent claim 9 having a pressure reducing valve (24) for reducing the brake releasing pressure.
  12. A control arrangement according to any one of the preceding patent claims having pressure sensors (28, 30) for detecting the pressure in the channels (42, 40).
  13. A control arrangement according to any one of the preceding patent claims, wherein the consumer is a hydraulic motor (2), having a revolution speed sensor for detecting the revolution speed of the hydraulic motor.
  14. A control arrangement according to any one of the preceding patent claims having a valve disc (94) which accommodates the above-described valves.
  15. A control arrangement according to any one of the preceding patent claims, wherein the pump (12) is a fixed displacement pump.
EP05015152A 2004-07-13 2005-07-12 Hydraulic control device Not-in-force EP1616997B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004033891A DE102004033891A1 (en) 2004-07-13 2004-07-13 Hydraulic control arrangement

Publications (2)

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

Family

ID=35044597

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05015152A Not-in-force EP1616997B1 (en) 2004-07-13 2005-07-12 Hydraulic control device

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005056981B4 (en) * 2005-11-30 2007-09-27 Sauer-Danfoss Aps Work machine, especially mini excavators
CN100496789C (en) * 2006-07-07 2009-06-10 江阴机械制造有限公司 Automatic speed following and pressure curve setting pushing system for pipe with small bending radius
DE102009015384B3 (en) * 2009-03-27 2010-09-16 Hydac Filtertechnik Gmbh Hydraulic valve device
DE102010055716B4 (en) 2010-12-22 2021-12-09 Robert Bosch Gmbh Hydraulic drive
CN106640817B (en) * 2017-01-04 2018-11-13 浙江高宇液压机电有限公司 The pressure compensation type energy-saving control valve of shunting hydraulic system is closed suitable for double pump
DE102022212754A1 (en) 2022-11-29 2024-05-29 Robert Bosch Gesellschaft mit beschränkter Haftung Method for controlling a hydraulic holding brake of a slewing gear and ventilation system for a hydraulic holding brake of a slewing gear

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2440714C3 (en) * 1974-08-24 1980-01-24 G.L. Rexroth Gmbh, 8770 Lohr Device for load-independent regulation of a hydraulic flow
US6244158B1 (en) * 1998-01-06 2001-06-12 Fps, Inc. Open center hydraulic system with reduced interaction between branches
DE19904616A1 (en) 1999-02-05 2000-08-10 Mannesmann Rexroth Ag Control arrangement for at least two hydraulic consumers and pressure differential valve therefor

Also Published As

Publication number Publication date
DK1616997T3 (en) 2010-11-08
ATE481534T1 (en) 2010-10-15
EP1616997A1 (en) 2006-01-18
DE102004033891A1 (en) 2006-02-16
DE502005010254D1 (en) 2010-10-28

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