EP2225470B1 - Ventilanordnung - Google Patents

Ventilanordnung Download PDF

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Publication number
EP2225470B1
EP2225470B1 EP08854023.2A EP08854023A EP2225470B1 EP 2225470 B1 EP2225470 B1 EP 2225470B1 EP 08854023 A EP08854023 A EP 08854023A EP 2225470 B1 EP2225470 B1 EP 2225470B1
Authority
EP
European Patent Office
Prior art keywords
valve
connection
pressure
consumer
section
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
EP08854023.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2225470A1 (de
Inventor
Alfred Breunig
Josef HESSDÖRFER
Walter Kirsch
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP2225470A1 publication Critical patent/EP2225470A1/de
Application granted granted Critical
Publication of EP2225470B1 publication Critical patent/EP2225470B1/de
Not-in-force legal-status Critical Current
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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—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
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/8671—With annular passage [e.g., spool]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86831—Selective opening of plural ports

Definitions

  • the invention relates to a valve arrangement according to the preamble of claim 1.
  • Such a valve arrangement is used, for example, for controlling hydraulic consumers of a mobile working machine, for example a wheel loader, a bulldozer, a telescopic forklift or a downhole loader.
  • the data sheet RD 64 284 / 06.00 of Mannesmann Rexroth AG describes a LUDV mobile control block in which the pressure medium supply to the consumers is controlled via directional control valve sections, each with a continuously adjustable directional control valve. This is carried out with a speed part formed by a metering orifice and a pressure medium flow direction to and from the consumer-determining directional part.
  • the metering orifice is assigned to a LUDV pressure compensator.
  • LUDV load pressure independent flow distribution
  • LUDV load pressure independent flow distribution
  • the invention is not limited to LUDV systems.
  • the continuously adjustable directional control valve can be adjusted from a neutral or middle position in the direction of first positions, in which, for example, a hydraulic cylinder is retracted.
  • the directional valve section can be adjusted by switching a float valve and simultaneously driving the valve spool in the direction "lower" in a floating position in which both consumer ports and the pressure port are connected to the tank port, so that, for example, a dozer blade of a bulldozer only due to its own weight on the floor rests.
  • the disadvantage of this solution is that a separate float valve is needed.
  • valve arrangement in which the directional control valve is equipped with four positions (neutral position, lifting, lowering, floating position) of a valve spool.
  • position is to be understood in each case a plurality of intermediate positions, in each of which an opening cross section which is effective in the sense of the functions neutral, lifting, lowering and floating position can be changed.
  • the DE 196 08 758 A1 discloses a solution in which a valve spool of the directional control valve in five positions (floating position, lowering, neutral position, vibration damping and extension) is adjustable, wherein in the position "vibration damping" in the direction of retraction effective annulus of the hydraulic cylinder is connected to the tank.
  • the present invention seeks to provide a valve assembly in which both a rapid traverse and a floating position operation is made possible with low device complexity.
  • the valve arrangement has a continuously adjustable directional control valve with a valve slide guided in a valve bore, which can be adjusted from a spring-biased neutral position into a first direction, in which a pressure medium flow path between a consumer connection and the inlet connection and another consumer connection is opened with a drain connection.
  • a pressure medium flow path between the other consumer port and the inlet port and the first-mentioned consumer port and the drain port is turned on in a first position accordingly.
  • this is a position "extension” in which flows from the piston rod side pressure chamber of a differential cylinder pressure fluid and the piston rod downstream pressure chamber pressure fluid flows.
  • the pressure medium volume flow flowing from one consumer connection is summed to that pressure medium volume flow which flows to the other consumer connection - the directional control valve is then set in a rapid traverse position.
  • valve assembly is designed with a directional control valve, the valve spool is adjustable in five positions, the floating position is preferably achieved after passing through the rapid traverse position.
  • control of these functions by adjusting the directional control valve, so that in contrast to the above-described prior art no additional, manually or by means of a pilot control to be switched control valves or the like must be provided.
  • the inventive concept is not only in so-called LUDV directional control valves, but also in LS-way valves, where the pressures before and after a metering orifice on a pressure compensator, and in directional control valves for throttle control (6-way valves with circulation channel) applicable.
  • a residual cross section in the pressure medium flow path between the one consumer connection and the outlet connection is opened.
  • the valve spool is designed with a control edge over which an opening cross-section in Druckstoffströmungspfad between the one consumer connection and the drain port is openable in adjusting in the other direction, wherein at least one control or extension groove is formed at a distance from this control edge on the valve spool , on the adjustment in the other direction, an opening cross-section between the one consumer port and the drain port is aufêtbar and on the further adjustment of the valve spool in the direction of the rapid traverse this opening cross section is züstuerbar again. In a further adjustment in the direction of the floating position of said opening cross section is then controlled via the control edge.
  • the pressure medium connection of a consumer connection is first opened with the drain connection. This pressure medium connection is then closed during further adjustment in the direction of the rapid traverse and then opened again when moving the valve spool in the direction of its end position for adjusting the floating function on the control edge.
  • extension groove is particularly simple if this is designed as a circumferentially closed pocket on the outer circumference of the valve spool.
  • a longitudinal groove defining the aforementioned residual cross-section is hydraulically parallel to the extension groove, via which a residual cross-section in the pressure medium flow path from the one consumer connection to the outlet connection is opened when the valve slide is moved into the rapid traverse function.
  • This longitudinal groove has a smaller effective cross-section than the extension groove.
  • valve spool is biased by a centering spring assembly in its neutral position.
  • This centering spring assembly is designed with a pressure point spring, which comes into operative engagement with adjustment of the valve spool in the direction of the floating position, so that the Whypersoh can adjust this floating position only deliberately by overcoming a resistance.
  • Zentrierfederan extract usually has two the valve spool in both directions acting centering springs, one of these centering springs is supported on the pressure point spring, which acts on a larger bias voltage is, so that the pressure point spring is initially not compressed during the adjustment of the valve spool.
  • the pressure point spring is tied to a stop pin, which is biased against a housing fixed stop and on the valve slide directly or indirectly when adjusting in the direction of the floating position runs, so that the further displacement is made possible only by overcoming the Druckticianfedervorponent ,
  • the structure of the valve assembly is particularly simple when a rapid traverse channel is provided which connects when adjusting the valve spool in its rapid traverse position bypassing the directional control valve connected to the one consumer connection return line with a supply line connected to the inlet port, wherein the rapid traverse channel in the direction of the consumer connection locking check valve is provided.
  • the pressure medium can then flow away from the consumer via the rapid passage to the other pressure chamber, so that the consumer is moved at high speed.
  • the directional control valve of the valve arrangement is preferably designed as LUDV directional control valve with a directional and a speed part, the latter being formed by a metering orifice. This is followed by an individual pressure balance, which is acted upon by the pressure downstream of the metering orifice in the sense of reducing the pressure compensator opening cross-section of the highest load pressure of all driven consumers and in the sense of increasing the pressure compensator opening cross-section.
  • FIG. 1 shows a schematic diagram of a directional control valve section 1 of a mobile control block of a mobile work machine, such as a bulldozer.
  • a mobile control block has a plurality of directional valve sections, via which the individual hydraulic consumers of the working machine can be controlled.
  • the in FIG. 1 illustrated directional control valve section 1 is used to control a lifting cylinder of a dozer blade to hold this either in a predetermined position, lower, raise, lower in rapid traverse or operate in a floating position.
  • FIG. 1 only the components of the directional control valve section 1 which are essential for understanding the invention are shown. Further details will be apparent from the figures described below.
  • the basic structure of the directional control valve section 1 is known from the data sheet RE 64 284 / 06.00 described above, so that only the elements essential for understanding the invention are described here.
  • the directional valve section 1 has according to the circuit diagram in FIG. 1 a pressure port P, two working ports A, B, tank ports T1, T, a control port pst, and a control oil drain port L.
  • the pressure port P is connected to a pump line 2 connected to the pressure port of a not-shown pump via an LS pump regulator is controlled depending on the highest load pressure of all driven consumers of the machine. This load pressure is tapped by the consumers via the LS connection and a load reporting channel 4 as well as a switching valve cascade, not shown.
  • the amount of pump is adjusted by the pump controller so that the pump pressure is a predetermined pressure difference above the highest load pressure.
  • the two consumer ports A, B of the directional control valve section are via consumer lines 6, 8 with a bottom-side cylinder chamber 10 and a piston rod side Annular space 12 of a lifting cylinder 14 is connected.
  • the direction of movement and the speed of the lifting cylinder 14 are adjusted via a continuously adjustable directional control valve 16. This is carried out with a speed part formed by a metering orifice 18 and a directional part 20, wherein via the metering orifice 18 the pressure medium volume flow to the consumer 14 and via the directional part 20, the flow direction to or from the pressure chambers 10, 12 is determined.
  • directional control valve 16 is designed with five positions, wherein a valve slide described in more detail below is biased via a centering spring assembly 22 in a middle position (0) in which the aforementioned connections are shut off.
  • valve spool When moving the valve spool to the right (in the direction in FIG. 1 ), the valve spool is first brought into the (A) marked positions "extending" in which the hydraulic cylinder 14 extends and the dozer blade is lowered. In a further adjustment of the valve spool in the direction to the right the marked with (E) positions are reached, in which the hydraulic cylinder 14 is operated at rapid traverse. In this rapid traverse function, the pressure medium volume flow from the decreasing annular space 12 to the cylinder chamber 10 via the metering orifice 18 supplied pressure medium volume flow is summed.
  • By moving the valve spool in the direction of its (F) marked positions a floating position is set, in which the dozer blade rests on the ground due to its weight and may possibly follow bumps.
  • valve spool positions marked (H) are set, in which the hydraulic cylinder 14 retracts and the dozer blade is raised.
  • an individual pressure compensator 28 is arranged, which in the sense of reducing the flow cross section through the pressure in the load signaling channel 4, ie a control pressure corresponding to the highest load pressure and in the sense of an enlargement the flow cross-section is acted upon by the pressure downstream of the metering orifice 18.
  • the inlet connection of the individual pressure compensator 28 is connected via a pressure compensator duct 30 to a pressure connection P 'and the outlet connection of the pressure compensator via a duct 32 to a connection P "of the directional control valve 16.
  • a load-holding valve 34 for the leakage-free support of the load
  • Working port A of the directional control valve 16 is connected to the consumer port A and the consumer port B of the directional valve section 1 via a return passage 38 to the working port B of the directional control valve 16.
  • Two tank ports T, T1 of the directional control valve 16 are respectively via flow channels 40, 42 with connected to the tank ports T, T1 of the directional valve section 1.
  • the pressure port P of the directional control valve 16 is connected via an inlet channel 44 to the pressure port P of the directional control valve section 1.
  • the return passage 38 is connected via a rapid traverse passage 46 to the section of the arc passage 32 located between the pressure port P "and the load-holding valve 34.
  • a check valve 48 is provided which opens in the direction of the pressure port P".
  • FIG. 1 is removable, in the case in which the pressure downstream of the metering orifice 18 is greater than the instantaneous pressure in the Lastmeldekanal 4, the pressure compensator slide in the illustration according to FIG. 1 shifted to its left end position, so that according to this downstream of the metering orifice 18 pending pressure in the load reporting channel 4 is reported.
  • FIG. 2 shows a concrete embodiment of the directional control valve section 1 according to FIG. 1 in section.
  • this directional valve section 1 is part of a mobile control block formed of a plurality of such directional valve sections as well as an input member and an end plate.
  • the directional valve section 1 has a valve disc 50, in which a valve spool 52 receiving valve bore 54 is formed.
  • the valve bore 54 seen from left to right to a tank chamber 56, a Forward chamber 58, a pressure compensator output chamber 60, a pressure compensator input chamber 62, an inlet chamber 64, another pressure compensator output chamber 66, a return chamber 68 and another tank chamber 70 extended.
  • the tank chamber 56 is as in FIG. 2 indicated via the drain passage 40 to the tank port T, the flow chamber 58 via the flow channel 36 to the consumer port A, the pressure compensator output chamber 60 via the rapid traverse channel 46 and the check valve 48 to the return chamber 68, wherein the pressure compensator output chamber 60 in the illustration FIG. 1 corresponds to the port P ".
  • the return chamber 68 is above the in FIG. 2 indicated return channel 38 connected to the consumer port B.
  • the tank chamber 70 is in fluid communication with the tank connection T1 via the outlet channel 42.
  • valve spool 52 The construction of the valve spool 52 will be described with reference to the enlarged view in FIG. 3 explained. Accordingly, the valve spool 52 is divided by a plurality of mutually spaced annular grooves in two Endbunde 72, 74, a tank control collar 76, a Zulaufbund 78, the opening cross section of the metering orifice 18 determining control collar 80, an intermediate collar 82 and a Zulaufbund 84.
  • At Tank josbund 76 is a Tank thoroughlykante 85, the Zulaufbund 78 an inlet control edge 86, the control collar 80 each end face a Meßblenden rigorouskante 88, 90, the Zulaufbund 84 a Zulaufberichtkante 92 and formed on the opposite annular end face of the Endbundes 74 a floating position control edge 94.
  • control edges 85, 86, 88, 90 92, 94 are each carried out in a known manner with control grooves or control windows 96, of which in FIG. 3 by way of example only one of the floating position control edge 94 associated control window is provided with a reference numeral.
  • a longitudinal groove 102 is formed on the outer periphery of the Endbundes 74, the width (seen in the circumferential direction) and length (seen in the axial direction) is less than that of the Ausfahrnut 100.
  • This longitudinal groove 102 opens as shown in FIG FIG. 3 in the lower control window 96 of the floating position control edge 94. In the illustrated neutral position (0), this longitudinal groove 102 is open to the return chamber 68 out.
  • the return chamber 68 is connected to the pressure compensator output chamber 60 via the rapid passage 46, which is designed as an angular bore, and the check valve 48 inserted therein, the check valve opening to the pressure compensator output chamber 60.
  • neutral position (0) of the valve spool 52 are in FIG. 1 visible ports P, A, B, P ', P ", T, T1 of the directional control valve 16. Accordingly, in the illustration according to FIG FIG.
  • FIG. 1 shown individual pressure compensator 28 is inserted into a direction perpendicular to the directional valve axis 98 extending pressure compensator bore 104, wherein a pressure compensator piston 106 frontally, ie in the illustration according to FIG. 2 from bottom to top with the pressure in the pressure compensator input chamber 62 and the rear is acted upon by the tapped from the load detection channel 4 highest load pressure, which is present in a rear annular space 108 of the pressure compensator bore 104.
  • the pressure compensator cross section is fully open (pressure compensator piston 106 is displaced upward in the illustration), the pressure in the pressure compensator input chamber 62 is reported via internal bores 110 of the pressure compensator piston 106 into the annular space 108 and thus into the load reporting channel 4.
  • centering spring assembly 22 is according to FIG. 2 received in spring housings 112, 114, in which the two end portions of the valve spool 52 dip.
  • left spring housing 112 is a centering spring 116th supported, which acts via a spring bushing 118 on the adjacent end face of the valve spool 52, wherein the stroke of the spring bushing 118 to the right in FIG. 2 is limited by a housing-fixed stop 120.
  • the stroke of the valve spool 52 to the left in FIG. 2 is limited by a stroke limiter 122.
  • a centering spring 124 is also supported, which acts via a spring plate 126 on an annular end face of the valve spool 52, which dips into the centering spring 124 with a radially set back end portion 128.
  • a pressure point spring 130 is provided in the spring housing 112, which is clamped to a stop pin 132 between a stop ring 134 and a support ring 136 of the stop pin 132.
  • the two rings 134, 136 are supported in opposite directions on the stop pin 132.
  • the centering spring 124 is supported on the support ring 136, wherein the spring bias of the pressure point spring 130 is greater than that of the centering spring 124.
  • In the illustrated neutral position of the stop pin 132 is biased by the centering spring 124 with its stop ring 134 against a spring housing side stop 138, wherein the spring plate 126 in turn is supported on a housing-side stop.
  • In the illustrated neutral position (0) is an in FIG.
  • FIG. 4 The function of the above-described directional control valve section 1 is based on FIG. 4 in which the positions (A), (E), (F) and (H) according to FIG. 1 are shown.
  • valve spool 52 is displaced by setting a suitable control pressure via the pressure control valve 26 to the left in its (H) marked positions in which on the Meßblenden torturekante 90 a pressure medium connection between the inlet chamber 64 and the pressure compensator input chamber 62 is opened, this alsiere Cross section forms the flow cross section of the metering orifice 18.
  • the pressure medium can then flow via the individual pressure compensator 28 and the arc channel 32 to the pressure compensator output chamber 66 and from there via the controlled by the floating position control edge 94 cross section in the return chamber 68, from there to the consumer port B and from there via the consumer line 8 to the annulus 12th the lifting cylinder 14 flows.
  • the pressure medium displaced from the cylinder chamber 10 which is smaller in size occurs via the consumer line 6, the consumer port A, which now practically acts as a return channel, into the flow chamber 58, which is connected to the tank chamber 56 via the tank control edge 85, so that the pressure medium then flows through the drain passage 40 and the tank port T of the directional valve section 1 to the tank. That is, when adjusting the valve spool 52 in the positions (H) of the lifting cylinder 14 is retracted and raised accordingly the dozer blade.
  • FIG. 4b To lower the dozer blade of the directional control valve 52 is FIG. 4b by setting a suitable control pressure via the pilot valve 24 from the illustration in accordance with FIGS. 1 to 3 shifted to the right, in which case the opening cross-section of the metering orifice 18 between the inlet chamber 64 and the pressure compensator inlet chamber 62 is determined via the metering orifice control edge 88.
  • the pressure medium flowing away from the individual pressure compensator 28 flows via the arc channel 32 into the pressure compensator output chamber 60 and from there through the cross section controlled via the inlet control edge 86 into the inlet chamber 58 and then via the flow channel 36, the consumer port A and the consumer line 6 into the cylinder chamber 10.
  • the main part of the pressure medium volume flow flows from the return chamber 68 via the rapid traverse channel 46 and the then opening non-return valve 48 in the pressure compensator output chamber 60 and is summed there to the pressure medium flow rate from the inlet chamber 64 via the controlled by the orifice control edge 88 orifice plate cross section to the individual pressure compensator 28 and this flows via the arc channel 32 in the pressure compensator output chamber 60.
  • This comparatively large rapid traverse volume flow is then guided via the cross section opened by the feed control edge 86, the feed chamber 58 and the consumer port A to the cylinder chamber 10 of the lifting cylinder 14.
  • control edge 86 By forming the control edge 86 with control windows with respect to a full flow cross-section reduced flow cross-section is achieved that can build up in the annulus 12 such a pressure that the load does not fall uncontrollably, but the speed of the load is determined by the funded by the pump pressure medium , Via the control edge 86, the pressure decreases from the high pressure in the annular space 12 to the lower pressure in the cylinder space 10.
  • FIG. 4d This floating position (F) is in FIG. 4d shown.
  • the inlet chamber 64 is however, throttled across orifice plate control edge 90 is connected to pressure compensator output chamber 66, which in turn is open to return chamber 68.
  • the latter is connected via the floating position control edge 94 with the tank chamber 70, so that the pressure medium can flow from the inlet chamber 64 to the tank.
  • the consumer port B via the return chamber 68, the floating position control edge 94 and the tank chamber 70 is connected to the tank.
  • the other consumer port A is connected via the flow chamber 58 and thus opened via the annular groove between the coils 72, 76 connection to the tank chamber 56 also connected to the tank, so that the dozer blade in this floating position unevenness on the ground or can level due to its weight .
  • the floating position (F) can be achieved only by overcoming the bias of the pressure point spring 130, so that the operator has a clear feedback when the float position (F) is reached.
  • the stop pin 132 is taken from the end portion 128 of the valve spool 52 until the in Figure 4c right end portion of the stop pin 132 runs onto the end stop 144. Another adjustment to the right is not possible.
  • valve spool 52 is adjustable in five positions to extend the functions lift cylinder retract, rapid traverse of the lift cylinder and floating position of the lift cylinder and to allow adjustment to a neutral position.
  • valve arrangement with a continuously adjustable directional valve, the valve spool is adjustable in the direction of five positions to drive a consumer in two directions, to move in rapid traverse, operate in floating position or shut off the pressure medium connection to the consumer (neutral position).

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Servomotors (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
EP08854023.2A 2007-11-28 2008-11-08 Ventilanordnung Not-in-force EP2225470B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007057654 2007-11-28
DE200810008092 DE102008008092A1 (de) 2007-11-28 2008-02-08 Ventilanordnung
PCT/EP2008/009448 WO2009068173A1 (de) 2007-11-28 2008-11-08 Ventilanordnung

Publications (2)

Publication Number Publication Date
EP2225470A1 EP2225470A1 (de) 2010-09-08
EP2225470B1 true EP2225470B1 (de) 2016-07-13

Family

ID=40585978

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08854023.2A Not-in-force EP2225470B1 (de) 2007-11-28 2008-11-08 Ventilanordnung

Country Status (6)

Country Link
US (1) US8464758B2 (ja)
EP (1) EP2225470B1 (ja)
JP (1) JP5290315B2 (ja)
KR (1) KR101539213B1 (ja)
DE (1) DE102008008092A1 (ja)
WO (1) WO2009068173A1 (ja)

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IT1395462B1 (it) * 2009-09-03 2012-09-21 Brevini Fluid Power S P A Valvola di distribuzione
DE102010009704A1 (de) * 2010-03-01 2011-09-01 Robert Bosch Gmbh Hydraulischer Fahrantrieb und Verfahren zum Steuern eines derartigen Fahrantriebs
JP5602074B2 (ja) * 2011-03-16 2014-10-08 カヤバ工業株式会社 制御弁
KR101317073B1 (ko) * 2011-06-09 2013-10-11 주식회사 유압사랑 체크 오리피스 기능을 삽입한 프라이어리티 스풀 밸브
DE102013215754A1 (de) * 2013-08-09 2015-02-12 Robert Bosch Gmbh Ventil zum hydraulischen Ansteuern einer Zumessblende, über die ein hydraulischer Verbraucher mit Druckmittel versorgbar ist, sowie hydraulische Anordnung mit einer Zumessblende und mindestens einem derartigen Ventil
JP6725081B2 (ja) * 2017-09-13 2020-07-15 株式会社島津製作所 コントロールバルブ
DK3775576T3 (da) 2018-05-18 2022-08-08 Hydac Systems & Services Gmbh Styreindretning
DE102018207929A1 (de) * 2018-05-18 2019-11-21 Hydac Systems & Services Gmbh Ventil
US11187060B2 (en) 2018-05-23 2021-11-30 Halliburton Energy Services, Inc. Hydraulic control system for index downhole valves
BR112020020538B1 (pt) 2018-05-23 2024-04-30 Halliburton Energy Services, Inc Aparelho e método para controlar uma ou mais válvulas de controle
DE102018208893A1 (de) * 2018-06-06 2019-12-12 Robert Bosch Gmbh Direktgesteuertes hydraulisches Wegeventil
US10641297B2 (en) * 2018-08-17 2020-05-05 Robert Bosch Gmbh Hydraulic control valve
WO2023088590A1 (en) * 2021-11-16 2023-05-25 Parker Hannifin Emea S.À.R.L. Directional control valve system

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Also Published As

Publication number Publication date
US20100269935A1 (en) 2010-10-28
WO2009068173A1 (de) 2009-06-04
KR20100105553A (ko) 2010-09-29
DE102008008092A1 (de) 2009-06-04
JP5290315B2 (ja) 2013-09-18
KR101539213B1 (ko) 2015-07-27
JP2011504990A (ja) 2011-02-17
EP2225470A1 (de) 2010-09-08
US8464758B2 (en) 2013-06-18

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