EP1629207B1 - Hydraulische steueranordnung - Google Patents

Hydraulische steueranordnung Download PDF

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Publication number
EP1629207B1
EP1629207B1 EP04739454A EP04739454A EP1629207B1 EP 1629207 B1 EP1629207 B1 EP 1629207B1 EP 04739454 A EP04739454 A EP 04739454A EP 04739454 A EP04739454 A EP 04739454A EP 1629207 B1 EP1629207 B1 EP 1629207B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
axis
valves
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.)
Expired - Lifetime
Application number
EP04739454A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1629207A1 (de
Inventor
Wolfgang Kauss
Didier Desseux
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1629207A1 publication Critical patent/EP1629207A1/de
Application granted granted Critical
Publication of EP1629207B1 publication Critical patent/EP1629207B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0832—Modular valves
    • F15B13/0839—Stacked plate type 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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow 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
    • 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
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0832—Modular valves
    • F15B13/0842—Monoblock type valves, e.g. with multiple valve spools in a common housing
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0871—Channels for fluid
    • 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]

Definitions

  • the invention relates to a hydraulic control arrangement for load pressure-independent control of a consumer according to the preamble of patent claim 1.
  • each consumer is assigned an adjustable metering orifice with a downstream pressure compensator, the latter keeping the pressure drop across the metering orifice constant so that the quantity of fluid flowing to the corresponding hydraulic consumer depends solely on the opening cross section of the metering orifice and not on the load pressure of the consumer or on the pump pressure depends.
  • each consumer port is associated with an aspirating valve which is perpendicular to the plane of a valve disc receiving the valve assembly.
  • this known solution lacks a check valve for leak-free shut-off of the consumer.
  • the invention has for its object to provide a hydraulic control arrangement in which all components required for the control of the consumer in a compact manner in a valve housing section, preferably a valve disc are summarized.
  • the control arrangement is preferably integrated in a valve disc, wherein a directional control valve forming a LUDV orifice plate and two shut-off valves each associated with a consumer port are located in the valve disc plane and two pilot valves respectively assigned to the two shut-off valves are installed in such a way are that their axes are oriented perpendicular to the two axes of the directional control valve and the check valves.
  • the pressure / suction valve associated with a consumer connection is arranged perpendicular to the axes of the above-described valve elements, ie perpendicular to the plane of the pane.
  • a special feature of the invention further consists in that the pilot valves arranged perpendicularly to the axis of the directional control valve are actuated mechanically via a ram which can be displaced axially by a valve spool of the directional control valve in order to unlock the check valves and to allow a pressure medium discharge from the consumer.
  • the solution according to the invention is characterized by a special compactness, wherein all essential, required in a LUDV system components are taken up with minimal space.
  • the directional control valve, the check valves and the pilot valves are arranged parallel to the disc plane ( Figure 1) and the Nachsaugventil perpendicular to the disc plane, so that the valve disc can be made with minimal effort due to the simple channel guide.
  • the axis of the measuring diaphragm of the directional valve downstream LUDV pressure compensator extends in the disc plane.
  • the axis of the individual pressure compensator is arranged centrally between the axes of the two pilot valves, so that the valve disc has a nearly axisymmetric structure.
  • the axis of the two Nachsaugventile is arranged in the region which is encompassed by the axis of the two check valves, the two axes of the pilot valves and the axis of the directional control valve.
  • the valve slide of the directional control valve has an actuation section, via which a plunger guided perpendicular to the directional control valve axis can be axially displaced to open the pilot valve.
  • this plunger is guided in a portion of the valve disc or the valve housing.
  • the axis of the pilot valve crosses the axis of the respective associated check valve.
  • the installation of the Nachsaugventile is particularly simple when lying in the region of these Nachsaugventile to the load ports leading working channels in a plane which are arranged offset to a tank channel containing a plane of the valve disc.
  • Figure 1 shows a section through a valve disc 1 of a control block of a mobile implement, such as a shovel, wherein the valve elements for each function (eg traction drive, lifting / lowering, bucket operate, etc.) are each combined in a valve disc.
  • the valve disc 1 shown in Figure 1 has two consumer ports A, B and a pressure port P (not shown), a tank port T (not shown) and a plurality of control terminals (including an LS port).
  • a continuously adjustable directional control valve 2 with a valve slide 4, which is guided axially displaceably in a valve disc 1 in the transverse direction passing through axial bore 6.
  • the valve slide 4 forms together with the axial bore 6 a speed part, also called orifice 8 and two directional parts 10, 12, via which the direction of the pressure fluid flow from and to the load ports A, B is determined.
  • an individual pressure compensator 14 Downstream of the metering orifice, an individual pressure compensator 14 (LUDV pressure compensator) is provided which is acted upon in the opening direction by the pressure downstream of the metering orifice 8 and in the closing direction by the force of a control spring (not shown) and the highest load pressure of the consumers.
  • This load pressure is tapped via a load pressure signaling line 16 and reported in the spring chamber of the pressure compensator. Under certain circumstances, the control pen can be dispensed with.
  • each check valve 18, 20 by means of a pilot valve 22, 24 can be unlocked.
  • the axes of these pilot valves 22, 24 extend in the embodiment shown in Figure 1 perpendicular to the axis of the directional control valve 2 and the common axis of the two check valves 18, 20, wherein the axis of the pilot valves 22, 24, the axis of the associated directional control valve 18 and 20 crosses ,
  • the actuation of the pilot valves 22, 24 takes place in each case via a plunger 30, 32, which is axially displaceable over the valve spool 4.
  • two pressure / Nachsaugventile 26, 28 are used in the valve disc 1, which open a connection to the tank port T at a predetermined pressure at the consumer port A, B and in the case of a pressure medium undersupply, a suction of pressure medium allow the tank.
  • the two axes of the pressure / Nachsaugventile 26, 28 are within that range, by the common axis of the two check valves 18, 20, the axis of the directional control valve second as well as the two axes of the pilot valves 22, 24 is clamped.
  • Both the individual pressure compensator 14 and the check valves 18, 20, the pilot valves 22, 24 and the pressure / Nachsaugventile 26, 28 are inserted into valve holes of the valve disc 1, which from the outside, i. are drilled from the end faces (pressure compensator, pilot valves, check valves) or from the large area of the valve disc 1 forth (pressure / Vietnamesegventile) and are shut off after insertion of the respective valve body by screw plugs or the like.
  • FIG. 2 shows the directional control valve 2 of the valve disk 1.
  • the valve slide 4 has a multiplicity of annular grooves, by means of which it is subdivided into a central measuring diaphragm collar 34, two control collars 36, 38 arranged on both sides thereof, and two tank collars 40, 42 arranged laterally therefrom.
  • the two end portions 44, 46 protrude from the valve disc 1.
  • flanges are flanged to the valve disc, record the centering springs for the valve spool 4 or control elements.
  • the annular end faces of the two tank collars 40, 42 lying on the outside in FIG. 2 are each designed as inclined control surfaces 50, 52, against which the plunger 30 and 32 are not biased in the center position of the control slide.
  • the other two annular end faces of the tank collar 40, 42 are provided with control notches 54, 56.
  • 34 fine control notches 58, 60 open in the annular surfaces of the central Meßblendenbundes.
  • the pressure port P opens into a pressure chamber 62, which is formed by an annular groove of the axial bore 6.
  • the axial bore is still extended to a connecting space 64, two annular spaces 66, 68, two drainage spaces 70, 72 and two outer tank spaces 74, 76. Between the above-described spaces each remain webs, which cooperate with the control edges of the valve spool 4.
  • the connecting space 64 opens into a pressure compensator channel 78, which leads to the inlet of the individual pressure compensator 14.
  • the output of the individual pressure compensator is connected via two channels 80, 82 to the annular spaces 66, 68.
  • the two drainage spaces 70, 72 each open into a consumer channel 84, 86 which extends to the entrance of the check valves 18 and 20, respectively.
  • each of the two tank chambers 74, 76 opens a tank channel 88, 90 (see FIG. 1), which leads to the respective associated pressure / suction valve 26, 28.
  • FIG. 3 shows that part of the valve disk 1 in which the check valve 20 and the pilot valve 24 as well as a part of the individual pressure compensator 14 are accommodated.
  • the check valve 20 has a designed as a hollow piston locking piston 96 which is guided axially displaceably in a check valve bore 94. This is shut off with a screw plug 98, on which a spring 100 is supported, via which the locking piston 96 is biased against a valve seat 102.
  • the locking piston 96 is designed with a seat difference. In the blocking position shown, the connection between the consumer channel 86 and connected to the consumer port B working channel 104 is closed. This working channel 104 extends from the consumer port B to the pressure / Nachsaugventil 28th
  • a nozzle 106 is provided, via which a spring 100 receiving spring chamber 108 is connected to the working channel 104.
  • This spring chamber 108 can be relieved via the pilot valve 24 to the tank T out.
  • the pilot valve has a seat bushing 110 inserted into a bore 112.
  • a pilot seat 114 is formed, against which a valve body 116 is biased by means of a pilot spring 118. This is supported on a locking ring 120 inserted into the socket 110.
  • the bore 112 intersects the check valve bore 64, the valve bush 110 with the valve body 116 and the pilot control spring 118 being inserted into a region of the bore 112 which is disposed beyond the check valve bore 94 in the representation according to FIG.
  • the mouth region of the bore 112 remote from the valve sleeve 110 is shut off by a closure screw 112.
  • the axis of the bore 112 extends coaxially to the axis of the plunger 82, which is guided in a guide projection 124 of the valve disc 1.
  • the bore 112 opens into the tank space 76, so that the end portion of the plunger 32 located at the top in FIG. 3 can dip into the opening encompassed by the pilot seat 114 and can be brought into contact with the valve body 116.
  • the pressure compensator piston 126 is biased by an axial projection 128 against a wall of the pressure compensator channel 78 and has on the adjacent annular end face control notches 130, which form a control edge over which the connection between the pressure compensator channel 78 and the channels 80, 82 auf tortbar.
  • the pressure relief valve is a unit.
  • the compression spring presses on seat element 138 and disc 142, which is positively connected to 144 and 146.
  • the elements 144 and 146 are a part.
  • the tapered end of 146 is pulled by the compression spring to the internal seat 138.
  • the cone spring 200 pushes the assembled unit 138 into a seat in the housing.
  • FIG. 4 shows a sectional side view in the region of the pressure / after-suction valve 26.
  • the consumer connection A opens into a working channel 132.
  • This (corresponding to the working channel 104 of the working connection B) leads to a radial connection of the pressure / suction valve 18.
  • This is in a Used Nachsaugbohrung 134 through which the working channel 132 is connected to the tank channel 88.
  • a Nachsaugventilsitz 136 is formed, against which a Nachsaugkegel 138 is biased by a compression spring 140.
  • This is supported on a spring plate 142, which in turn is fastened to a piston rod 144 of a guided in the Nachsaugkegel 138 pressure limiting piston 146.
  • the piston rod 144 with the spring plate 142 is supported on a support screw 148, which is screwed from a large area of the valve disc 1 forth in the Nachsaugbohrung 134.
  • a seat for the pressure limiting piston 146 is provided, against which it is biased by the force of the compression spring 140.
  • the pressure in the spring chamber of the pressure / Vietnamesegventils 26 is reported via pressure holes 150 of the Nachsaugkegels 138 to the seat for the pressure limiting piston 146.
  • the structure according to the invention with a symmetrical in the representation of Figure 1 construction with respect to the axis of the individual pressure compensator 14 and with the intersecting axes of the check valve 18, 20 and the associated pilot valve 22, 24 and arranged perpendicular thereto pressure / Nachsaugventilen 26, 28 allows to combine all the hydraulic components required for LUDV control and leak-free support of a consumer in a minimum space.
  • valve spool 4 of the directional control valve 2 is moved to the right in the illustration according to FIG. 1 in order to return pressure medium via the consumer connection A to the consumer and from this via the consumer connection B to the tank T. Due to the axial displacement of the valve spool 4 to the right, a metering orifice cross-section is opened via the control notches 58 of the metering orifice collar 34, so that pressure medium can flow from the pressure chamber 62 into the pressure compensator channel 78.
  • the pressure compensator is brought into an open position with sufficient pump pressure by the effective pressure in the opening direction, so that the pressure medium via the channel 80 and the annular space 66 in the open Outflow space 70 can flow.
  • With sufficient pressure in the consumer channel 84 of the locking piston 96 of the check valve 18 is lifted against the force of the spring 100 of its valve seat 102, so that the pressure medium to the consumer A is promoted ,
  • the load pressure building up at the consumer is reported via the LS channel 16 into the spring chamber of the individual pressure compensator 14. This adjusts to a control position in which the pressure drop across the inlet orifice is kept constant.
  • a hydraulic control arrangement for load pressure-independent control of a consumer, with a Zulaufmessblende forming a directional control valve, an associated individual pressure compensator, each one the consumer connections associated shut-off valve, which is unlocked by a pilot valve and a Nachsaugventil, via which to avoid cavitation pressure medium from a tank is nachsaugbar.
  • the directional control valve and the check valves are arranged along two parallel axes, while the axes of the two pilot valves are arranged perpendicular to these two axes.
  • the suction valves are again perpendicular to the axes of the directional control valves, the check valves and the Nachsaugventile.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Valves (AREA)
EP04739454A 2003-06-04 2004-05-28 Hydraulische steueranordnung Expired - Lifetime EP1629207B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003125294 DE10325294A1 (de) 2003-06-04 2003-06-04 Hydraulische Steueranordnung
PCT/EP2004/005836 WO2004109123A1 (de) 2003-06-04 2004-05-28 Hydraulische steueranordnung

Publications (2)

Publication Number Publication Date
EP1629207A1 EP1629207A1 (de) 2006-03-01
EP1629207B1 true EP1629207B1 (de) 2006-11-02

Family

ID=33482508

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04739454A Expired - Lifetime EP1629207B1 (de) 2003-06-04 2004-05-28 Hydraulische steueranordnung

Country Status (6)

Country Link
US (1) US7213501B2 (ja)
EP (1) EP1629207B1 (ja)
JP (1) JP2006526745A (ja)
AT (1) ATE344394T1 (ja)
DE (2) DE10325294A1 (ja)
WO (1) WO2004109123A1 (ja)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4276491B2 (ja) * 2003-08-04 2009-06-10 日立建機株式会社 方向切換弁ブロック
DE102006012030A1 (de) * 2006-03-14 2007-09-20 Robert Bosch Gmbh Hydraulische Ventilanordnung
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
DE102008018936A1 (de) * 2008-04-15 2009-10-22 Robert Bosch Gmbh Steueranordnung zur Ansteuerung eines Wegeventils
DE102008031745A1 (de) 2008-07-04 2010-01-07 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
JP7116584B2 (ja) * 2018-05-07 2022-08-10 川崎重工業株式会社 弁装置

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125120A (en) * 1964-03-17 hasbany
US3595271A (en) * 1969-06-30 1971-07-27 Int Harvester Co Directional flow control valve with float and check valve structure
FR2593265B1 (fr) * 1986-01-17 1988-04-22 Rexroth Sigma Distributeur de fluide hydraulique sous pression
DE4028887C2 (de) * 1990-09-12 2003-08-07 Bosch Gmbh Robert Hydraulische Steuereinrichtung
DE4417962A1 (de) * 1994-05-21 1995-11-23 Rexroth Mannesmann Gmbh Steueranordnung für wenigstens zwei hydraulische Verbraucher
DE19627306A1 (de) * 1996-07-06 1998-01-08 Bosch Gmbh Robert Sperrventil mit Druckbegrenzung
FR2756349B1 (fr) * 1996-11-26 1999-01-22 Mannesmann Rexroth Sa Distributeur hydraulique avec clapet antiretour
DE19835015A1 (de) 1998-08-03 2000-02-10 Linde Ag Hydrostatisches Antriebssystem
DE10001665B4 (de) * 2000-01-17 2008-05-08 Linde Material Handling Gmbh Ventilanordnung zur Absicherung und leckölfreien Absperrung eines hydraulischen Verbrauchers

Also Published As

Publication number Publication date
DE502004001913D1 (de) 2006-12-14
EP1629207A1 (de) 2006-03-01
WO2004109123A1 (de) 2004-12-16
ATE344394T1 (de) 2006-11-15
US7213501B2 (en) 2007-05-08
DE10325294A1 (de) 2004-12-23
US20060150807A1 (en) 2006-07-13
JP2006526745A (ja) 2006-11-24

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