EP1691083B1 - Hydraulische Steueranordnung - Google Patents

Hydraulische Steueranordnung Download PDF

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Publication number
EP1691083B1
EP1691083B1 EP06100715A EP06100715A EP1691083B1 EP 1691083 B1 EP1691083 B1 EP 1691083B1 EP 06100715 A EP06100715 A EP 06100715A EP 06100715 A EP06100715 A EP 06100715A EP 1691083 B1 EP1691083 B1 EP 1691083B1
Authority
EP
European Patent Office
Prior art keywords
control
valve
pressure
connection
rotary slide
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
EP06100715A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1691083A3 (de
EP1691083A2 (de
Inventor
Armin Stellwagen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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Filing date
Publication date
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Publication of EP1691083A2 publication Critical patent/EP1691083A2/de
Publication of EP1691083A3 publication Critical patent/EP1691083A3/de
Application granted granted Critical
Publication of EP1691083B1 publication Critical patent/EP1691083B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/008—Valve failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/166—Controlling a pilot pressure in response to the load, i.e. supply to at least one user is regulated by adjusting either the system pilot pressure or one or more of the individual pilot command pressures
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/002—Electrical failure
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—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
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a 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
    • F15B2211/57—Control of a differential 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
    • F15B2211/605—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
    • F15B2211/635—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/67—Methods for controlling pilot 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8757—Control measures for coping with failures using redundant components or assemblies

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a consumer according to the preamble of patent claim 1.
  • Such a hydraulic control arrangement is off DE 44 35 339 known.
  • Such hydraulic control arrangements are used for example in loading cranes and other mobile equipment for controlling hydraulic consumers, such as hydraulic cylinders or hydraulic motors.
  • a hydraulic control arrangement in which connections of a hydraulic cylinder can be connected via a 4/3-way valve with a variable displacement pump or a tank.
  • the directional control valve is actuated by means of electrohydraulic pilot valves and is spring-centered in a middle position in which its pump connection, tank connection and the two working connections of the hydraulic cylinder are shut off from each other.
  • the hydraulic control arrangement fulfills an emergency stop function, since after the failure of the electrical and / or hydraulic supply, the directional control valve assumes its central position by the spring preload and thus an unwanted consumer movement is excluded.
  • a disadvantage of such hydraulic control arrangements is that after the failure of the electrical and / or hydraulic supply is no longer possible to actuate the directional control valve and thus the
  • the present invention seeks to provide a hydraulic control arrangement that allow emergency operation of the consumer.
  • the hydraulic control arrangement according to the invention for controlling a consumer, in particular a mobile working device has a directional control valve which can be connected by means of a pilot valve arrangement and can be connected to a pump or pressure medium sink (tank).
  • the pilot valve assembly is associated with at least one pressure reducing valve for adjusting a control pressure in a control oil flow path connected to a control space of the directional control valve upon switching the pilot valve assembly from a home position to operate the consumer.
  • the hydraulic control arrangement in the control oil flow path has a manually operable emergency actuation valve, via which the directional control valve in the basic position of the pilot valve arrangement is adjustable to a position to actuate the consumer.
  • the directional control valve can be operated even in case of failure of the electrical and / or hydraulic supply. This makes it possible for the consumer, for example a loading crane to move to a safe position, or to ensure emergency operation.
  • the pilot control valve arrangement has two pilot valves whose output are connected via a control channel and a pilot line to a control chamber of the directional control valve, wherein the emergency valve opens the connection between the pilot valves to the control chambers in a basic position and shuts off in its switching positions and one of the pilot lines with a Pressure medium source connects.
  • the emergency actuation valve In its switching positions, the emergency actuation valve preferably blocks the connection to the pressure reducing valve, so that a pressure medium loss during emergency operation of the control arrangement is prevented.
  • the emergency actuation valve is a 6/3-way valve, in particular as a rotary slide valve.
  • the valve by hand and in an emergency in a very short time adjustable without much effort.
  • control arrangement according to the invention is independent of the type of pump.
  • the pilot control valve arrangement may preferably have at least one pressure relief valve.
  • a pressure source is preferably a constant pump at bypass pressure balance use.
  • a manually operable auxiliary pump can be connected as a pressure source.
  • the auxiliary pump is it is possible to generate the hydraulic pressure required for the actuation of the consumers and thereby to enable an emergency operation.
  • the rotary valve has a plurality of terminals and switching positions, wherein annular grooves are formed on a guided in a valve housing rotary valve, in each of which a plurality of circumferential portions formed on longitudinal pockets open, which can be brought by twisting the rotary valve with different ports in coverage to Depending on the switching position on the annular grooves and longitudinal pockets to establish a pressure medium connection between the annular grooves and connections.
  • the angular spacing of the longitudinal pockets arranged on a circumferential section is at least 90 °.
  • the rotary valve has a valve housing with a pressure port, two control input ports, two control output ports and a control pressure port.
  • the pressure port is connected to the control pressure port and a control input port is connected to a control output port.
  • the control pressure port and the control input port are locked in a first switching position, and the pressure port is connected to the control output port and the control input port is connected to the control output port.
  • the control pressure port and the control input port are blocked and the pressure port is blocked with the Control output terminal and the control input terminal connected to the control output terminal.
  • One port opens at the end face and the other ports on the circumference into a valve bore receiving the rotary valve. This makes it possible to supply both control chambers of the directional control valve with pressure medium, to adjust this to its switching positions and to move the connected implements and the like in a safe position, or to ensure emergency operation.
  • the rotary valve valve preferably has two annular grooves defining two annular channels with the valve bore, wherein a first control input port opens into a first annular channel and a first control input port opens in the other second annular channel and the other peripherally opening ports open into the valve bore at an axial distance from the annular channels and in dependence can be connected to the annular channels of the actuating position of the rotary valve on the arranged along the circumference of the rotary valve longitudinal pockets.
  • the second control input connection opens as an axial connection in an adjacent to the second annular channel rear, bounded by an end face of the rotary valve end portion of the valve bore and the other terminals are preferably formed as radial connections.
  • a first control output connection opens in the region between the annular channels, the second control output connection and the control pressure connection offset by 90 ° open into a front end section adjacent to the first annular channel.
  • the two perpendicular to each other extending radial bores in the periphery of the front end portion of the rotary valve opens.
  • the radial bores are hydraulically connected to the second control output port in the home position and in a first control position.
  • two longitudinal pockets extend from the first annular groove into the front end section.
  • a first longitudinal pocket is hydraulically connected in the basic position with the control pressure port and the second longitudinal pocket in a second actuating position with the second control pressure output port.
  • a third longitudinal pocket extends, which in the first setting position is connected to the first control output connection.
  • a fourth and a fifth longitudinal pocket extend from the second annular groove to the first annular groove. The fourth longitudinal pocket is connected in the basic position and the fifth longitudinal pocket in the second switching position to the first control output terminal.
  • the first longitudinal pocket and the second longitudinal pocket by 180 °, the third longitudinal pocket and the fourth longitudinal pocket by 90 ° and the fourth and fifth longitudinal pocket offset by 90 ° to each other, wherein the first longitudinal pocket and the third longitudinal pocket are coaxial.
  • the angular spacing of the longitudinal pockets arranged on a circumferential section is at least 90 °.
  • the rotary valve preferably has a safety device, which is an adjustment of the Rotary slide from the home position indicates.
  • a safety device which is an adjustment of the Rotary slide from the home position indicates.
  • the safety device has a shear pin which is sheared off during the adjustment of the rotary valve.
  • At the front end portion of the rotary valve is preferably formed a circumferential groove for receiving a sealing element, in particular a sealing ring in order to reduce the leakage losses.
  • the rear end face of the rotary valve defines a void with an adjacent end face of the valve bore.
  • FIG. 1 2 shows a schematic circuit diagram of a control arrangement designed as valve disk 1 for supplying pressure medium to a first consumer port C and a second consumer port D.
  • This essentially consists of a 4/3-way valve 6 actuated via two pilot valves 2, 4 and one as 6/3-way valve.
  • Rotary valve 8 trained emergency valve.
  • the pressure medium supply of the valve disc 1 takes place in the illustrated embodiment via a pump port P which is connected to a pump, not shown, is conveyed via the pressure medium in a pump line 10.
  • a pump port P which is connected to a pump, not shown, is conveyed via the pressure medium in a pump line 10.
  • From the pump line 10 branches a bypass line 12 to a tank channel 13, which opens into a tank connection T.
  • a continuously operable inlet pressure compensator 14 is arranged, which is acted upon in the opening direction by the pressure in the pump line 10 and in the closing direction of the highest load pressure of all connected to the load terminals C, D consumers and a spring 16.
  • the highest load pressure is tapped in a known manner via a shuttle valve cascade 18 of all consumers of the system and is connected via a load indicator line 20 to the inlet pressure compensator 14.
  • the control device 1 is designed as a LS (Load Sensing) system, in which the highest load pressure of the driven load via the load reporting line 20 and a LS port LS reported to a pump, not shown, and this is controlled so that in the pump line 10th a certain pressure difference .DELTA.p is above the load pressure lying pump pressure, wherein the Pressure difference Ap of the force of the spring 16 corresponds.
  • From the pump line 10 branches off a further bypass line 22 to the tank channel 13 and the tank port T, in which a primary pressure relief valve 24 is arranged, via which the maximum pressure in the pump line 10 is limited.
  • the pump can be designed as a fixed displacement pump with speed-controlled drive or as a variable displacement pump.
  • a control pressure line 26 for supplying a control pressure source 28 consisting of a pressure reducing valve 30 and a pressure relief valve 32 from.
  • a control output line 34 of the pressure reducing valve 30 is connected to a Steurdruckstras effet 36 for Reduditation of pending in the control pressure line 26 pump pressure to the maximum control pressure.
  • the control pressure limiting valve 32 is connected to the control pressure supply line 36 and a control pressure relief line 38 to limit the maximum pressure in the control pressure supply line 36.
  • a connection Y is present on the valve disc 1.
  • a connection X to the external control oil supply of the valve disc 1 is closed.
  • the pressure medium supply to the load terminals C, D is controlled.
  • This has a pressure port P and two working ports A, B, which in the illustrated spring-biased basic position (0) via a respective drainage restrictor 40 with a tank port T of the directional control valve 6 and connected via the tank line 64 to the tank channel 13 and the tank port T of the valve disc 1 are.
  • the pressure port P of the valve disk 1 is connected to the input port P of Directional valve connected via the pump line 10.
  • a further outflow measuring throttle 40 between the working connection A and the tank connection T of the directional control valve 6 is opened via a control edge.
  • the drainage measuring throttle 40 is located between the working connection B and the tank connection T.
  • the working connections A, B are connected to the consumer connections C and D via two working channels 42, 44.
  • These are connected to a pressure input P via a bypass line 48 to the control pressure supply line 36, with a tank outlet T via a bypass line 50 with the control pressure relief line 38 and with a control output R via a respective control channel 52, 54 and a pilot line 56, 58, each with a control room 60, 62 of the directional control valve 6 connectable.
  • the invention is in the control oil flow path, that is arranged between the pilot valves 2, 4 and the directional control valve 6, the manually actuable Notbetuschistil 8 over which the directional control valve 6 in the illustrated basic position (0) of the pilot valves 2, 4 is adjustable to a position Supplying consumer connections C, D with pressure medium.
  • the directional control valve 6 can be operated even in case of failure of the electrical and / or hydraulic supply. This makes it possible to supply the consumer ports C, D with pressure medium and to move connected implements and the like in a safe position, or to ensure emergency operation.
  • the emergency actuation valve 8 as a 6/3-way rotary valve with a pressure port P two control input terminals X1, X2, two control output terminals Y1, Y2 and a control pressure port Z is executed.
  • the control input terminals X1, X2 are connected via the control channel 52 to the pilot valve 2 and via the control channel 54 to the pilot valve 4.
  • the control output connections Y1, Y2 are connected via the pilot control lines 56, 58 to one of the two control chambers 60, 62 of the directional control valve 6, the pressure connection P to the pump line 10 and the control pressure connection Z to the control pressure line 26.
  • control input terminals X1, X2 are respectively connected to the control output terminals Y1, Y2 and the pressure port P is connected to the control pressure port Z.
  • the directional control valve 6 is due to the spring bias in the illustrated basic position (0), wherein the working channels 42, 44 are connected via a tank line 64 and the tank channel 13 to the tank port T of the control arrangement 1.
  • the directional control valve 6 can be operated even in the event of failure of the electrical and / or hydraulic supply via the emergency control valve 8 .
  • the pressure required to actuate the consumer can be applied by means of an auxiliary pump (not shown) which can be connected to the pump line 10 or the pressure connection P.
  • the control pressure port Z and the control input port X1 are locked in a first shift position (a) of the emergency operating valve 8, and the pressure port P is connected to the control output port Y1 and the control input port X2 is connected to the control output port Y2.
  • the control chamber 62 is acted upon by the pump pressure, the directional control valve 6 is adjusted to its switching position (b) and the consumer port D is supplied with pressure medium.
  • the control pressure port Z and the control input port X2 are disabled, and the pressure port P is connected to the control output port Y2 and the control input port X1 is connected to the control output port Y1.
  • FIG. 2 This has a hatched valve housing indicated by a hatched portion 66 with a valve bore 68 and a guided therein approximately cylindrical rotary valve 70. This has at a front end portion 72 a circumferential groove 74 for receiving a sealing ring 76 (see FIG. 3 ) and merges into a likewise cylindrical handling section 78 with a smaller diameter.
  • the rotary valve 8 has the pressure port P, two control input ports X1, X2 and two control output ports Y1, Y2 and a control pressure port Z, wherein the control input port X2 frontally into the rotary valve 70 receiving valve bore 68 and the control input terminal X1, the control output terminals Y1, Y2, the Pressure port P and the control pressure port Z circumferentially open in the valve bore 68.
  • a rear end face 80 of the rotary valve 70 defines an empty space 84 with an adjacent end face 82 of the valve bore 68.
  • annular grooves 86, 88 are formed, which define two annular channels 90, 92 with the valve bore 68, wherein in the first annular channel 90 of the pressure port P and in the other second annular channel 92nd a first control input terminal X1 opens and the other peripherally opening ports Y1, Y2, Z open at an axial distance from the annular channels 90, 92 in the valve bore 68.
  • the second control output terminal X2 opens as an axial connection in an adjacent to the second annular channel 92 rear end of the end face 80 of the rotary valve 70 limited end portion 94 of the valve bore 68.
  • the first control control output port Y1 opens in the area between the annular channels 90, 92 of the second Steuerausgangsanschuss Y2 and the by 90 ° offset control pressure port Z in the first annular channel 90 adjacent the front end portion 72 of the rotary valve 70 a.
  • an axial channel 96 is formed, which opens via two mutually perpendicular radial bores 98, 100 in the periphery of the front end portion 72 of the rotary valve 70.
  • the radial bores 98, 100 are hydraulically connected to the second control output port Y2 in the home position (0) and in a first control position (a) of the rotary valve 70.
  • first longitudinal pocket 102 is hydraulically connected to the control pressure port Z and the second longitudinal pocket 104 is hydraulically connected to the second control pressure output port Y2 in a second actuating position (b).
  • a third longitudinal pocket 106 extends, which in the first setting position (a) is connected to the first control output connection Y1.
  • a fourth Longitudinal pocket 108 and a fifth longitudinal pocket 110 extend from the second annular groove 88 toward the first annular groove 86, wherein the fourth longitudinal pocket 108 in the basic position (0) and the fifth longitudinal pocket 110 in the second switching position (b) is connected to the first control output terminal Y1 ,
  • the longitudinal pockets 102 to 110 extend along the rotary valve surface and have an approximately rectangular basic shape, which is rounded in the region of the terminals in each case arcuately.
  • the first longitudinal pocket 102 and the second longitudinal pocket 104 are arranged by 180 °, the third longitudinal pocket 106 and the fourth longitudinal pocket 108 by 90 ° and the fourth longitudinal pocket 108 and fifth longitudinal pocket 110 offset by 90 ° to each other.
  • the first longitudinal pocket 102 and the third longitudinal pocket 106 are coaxial with each other. That the angular distance of the arranged on a peripheral portion longitudinal pockets is at least 90 °.
  • connections and the longitudinal pockets can also be arranged at other angular intervals in the valve housing or in the rotary valve.
  • the control input terminals X1, X2 are respectively connected to the control output terminals Y1, Y2 and the pressure port P is connected to the control pressure port Z.
  • a control of the directional control valve 6 via the pilot valves 2, 4 and a pressure medium supply of the control pressure source 28 is possible (see FIG. 1 ).
  • the control pressure port Z and the control input port X1 are locked and the pressure port P is connected to the control output port Y1 and the control input port X2 is connected to the control output port Y2 in a first shift position (a) of the emergency operating valve 8 (-90 ° position).
  • the control chamber 62 is acted upon by the pump pressure, the directional control valve 6 is adjusted to its switching position (b) and the consumer port D is supplied with pressure medium (see FIG. 1 ).
  • the control pressure port Z and the control input port X2 are blocked and the pressure port P is connected to the control output port Y2 and the control input port X1 is connected to the control output port Y1.
  • the control chamber 60 is acted upon by the pump pressure, the directional control valve 6 in its switching position (a) adjusted and the consumer port C supplied with pressure medium. That is, in the switching positions (a), (b) of the rotary valve 8, it is possible to supply the load ports C, D with pressure medium and connected implements and the like to move to a safe position, or to ensure emergency operation.
  • FIG. 3 which shows a sectional view of an actuating device 114 of the rotary valve 8
  • this has an operating handle 116 with an approximately hollow cylindrical base body 118, which forms a holding portion 124 of reduced diameter at an end portion 122 facing the housing cover 120 of the valve housing 66.
  • the holding portion 124 has at its inner periphery 126 a front side annular projection 128 which engages behind a mushroom-shaped projection 130 of the housing cover 120 and rotatably defines the operating handle 116 on the housing cover 120.
  • the housing cover 120 is rotatably screwed to the valve housing 66 and the operating handle 116 rotatably connected to the cylindrical handling portion 78 of the rotary valve 70.
  • a circumferential groove 74 for receiving the sealing ring 76 is formed to prevent leakage from the limited by the housing cover 120 and the rotary valve 70 annular space 132 to the outside.
  • the rotary valve 70 is fixed in the illustrated basic position (0) by a spring 136 loaded ball 138, which is inserted into a radial blind hole 140 of the housing cover 120.
  • the spring-loaded ball 138 exits from the blind hole 140 sections and gangs in a recess 142 of the rotary valve 70 a.
  • a radially projecting stop pin 144 is inserted, which extends in a non-circumferential groove 146 of the housing cover 120 and limits the adjustment of the rotary valve 70 to + 90 ° to -90 °. As a result, the two rotated switching positions of the rotary valve 70 are defined.
  • a hydraulic control arrangement 1 for controlling a consumer in particular a mobile working device, which can be connected via a pre-pilot valve arrangement 47 piloted directional control valve 6 with a pump or a Druckschsenke (tank), wherein the pilot valve assembly 47th at least one pressure reducing valve 30 for adjusting a control pressure in a control oil flow path, which is connected to a control chamber 60, 62 of the directional control valve when switching the pilot valve assembly 47 from a home position (0) to actuate the consumer.
  • a manually actuable emergency actuation valve 8 is arranged in the control oil flow path, via which the directional control valve 6 in the basic position (0) of the pilot valve arrangement 47 can be adjusted to a position in order to actuate the consumer.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
EP06100715A 2005-02-09 2006-01-23 Hydraulische Steueranordnung Not-in-force EP1691083B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005005927A DE102005005927A1 (de) 2005-02-09 2005-02-09 Hydraulische Steueranordnung

Publications (3)

Publication Number Publication Date
EP1691083A2 EP1691083A2 (de) 2006-08-16
EP1691083A3 EP1691083A3 (de) 2007-05-02
EP1691083B1 true EP1691083B1 (de) 2009-05-20

Family

ID=36218654

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EP06100715A Not-in-force EP1691083B1 (de) 2005-02-09 2006-01-23 Hydraulische Steueranordnung

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Country Link
EP (1) EP1691083B1 (da)
AT (1) ATE431906T1 (da)
DE (2) DE102005005927A1 (da)
DK (1) DK1691083T3 (da)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006018706A1 (de) 2006-04-21 2007-10-25 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102007029355A1 (de) 2007-06-26 2009-01-02 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102007029358A1 (de) 2007-06-26 2009-01-02 Robert Bosch Gmbh Verfahren und hydraulische Steueranordnung zur Druckmittelversorgung zumindest eines hydraulischen Verbrauchers
DE102007054138A1 (de) 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102008018936A1 (de) * 2008-04-15 2009-10-22 Robert Bosch Gmbh Steueranordnung zur Ansteuerung eines Wegeventils
DE102008043273A1 (de) * 2008-10-29 2010-05-06 Zf Friedrichshafen Ag Hydraulische Steuerung
DE102012203386A1 (de) * 2012-03-05 2013-09-05 Robert Bosch Gmbh Steueranordnung
CN103925261B (zh) * 2014-04-10 2015-11-18 中煤科工集团西安研究院有限公司 一种钻机用电液控制防碰装置
CN105351407B (zh) * 2015-12-17 2017-06-30 中石化石油工程机械有限公司第四机械厂 一种组合刹车控制装置

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS599763B2 (ja) * 1981-03-02 1984-03-05 日立建機株式会社 コントロ−ルバルブの操作油圧回路
DE4223536C2 (de) * 1992-07-17 2003-12-11 Zahnradfabrik Friedrichshafen Drehschieberventil, insbesondere für Hilfskraftlenkungen
DE9210647U1 (de) * 1992-08-10 1993-12-16 Heilmeier & Weinlein Hydraulische Steuervorrichtung
DE19531867A1 (de) * 1994-09-07 1996-03-14 Barmag Barmer Maschf Hydraulische Steuerung
DE4435339C2 (de) * 1994-10-01 2003-06-05 Bosch Rexroth Ag Anordnung zur Ansteuerung eines hydraulisch betätigbaren Hauptventils
US5626070A (en) * 1996-02-29 1997-05-06 Caterpillar Inc. Control logic for a multiple use hydraulic system
DE19948232A1 (de) * 1999-07-10 2001-01-11 Mannesmann Rexroth Ag Wegeventilscheibe, insbesondere für ein mobiles Arbeitsgerät
DE19961017C3 (de) * 1999-12-17 2003-08-28 Zf Lenksysteme Gmbh Vorrichtung zum Steuern von Druckmedium, insbesondere für Lenkungen von Kraftfahrzeugen
DE202004004861U1 (de) * 2004-03-25 2004-06-09 Bosch Rexroth Ag Handhilfsbetätigbares pneumatisches Mehrwegeventil

Also Published As

Publication number Publication date
EP1691083A3 (de) 2007-05-02
EP1691083A2 (de) 2006-08-16
DK1691083T3 (da) 2009-09-14
DE102005005927A1 (de) 2006-08-17
DE502006003754D1 (de) 2009-07-02
ATE431906T1 (de) 2009-06-15

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