EP1481167A1 - Dispositif a soupapes - Google Patents

Dispositif a soupapes

Info

Publication number
EP1481167A1
EP1481167A1 EP03706251A EP03706251A EP1481167A1 EP 1481167 A1 EP1481167 A1 EP 1481167A1 EP 03706251 A EP03706251 A EP 03706251A EP 03706251 A EP03706251 A EP 03706251A EP 1481167 A1 EP1481167 A1 EP 1481167A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
pilot
arrangement according
main
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP03706251A
Other languages
German (de)
English (en)
Other versions
EP1481167B1 (fr
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
Priority claimed from DE10218783A external-priority patent/DE10218783A1/de
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1481167A1 publication Critical patent/EP1481167A1/fr
Application granted granted Critical
Publication of EP1481167B1 publication Critical patent/EP1481167B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • 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
    • 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
    • Y10T137/86622—Motor-operated
    • Y10T137/8663—Fluid motor

Definitions

  • the invention relates to a valve arrangement for controlling loads independent of load pressure.
  • Valve arrangements of this type are used, for example, in LUDV systems, as are known from WO 95/32364 AI and data sheet RD 64 127/04.98 (hydraulic valves for mobile applications).
  • An LUDV system includes, for example, a variable displacement pump that can be controlled so that it produces a pressure at its outlet that is a certain difference above the highest load pressure of all hydraulic consumers.
  • An adjustable metering orifice with a downstream pressure compensator is assigned to each of the consumers, the latter keeping the pressure drop across the metering orifice constant, so that the quantity of pressure medium 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.
  • the pressure balances of the system ensure that, in the case in which the hydraulic pump has been adjusted to the maximum stroke volume and the pressure medium flow is not sufficient to maintain the predetermined pressure drop across the metering orifices, the pressure balances of all actuated hydraulic consumers in Closing direction can be adjusted so that all pressure medium flows are reduced by the same percentage.
  • the disk-shaped valve housing with an integrated check valve could be used instead of the check valve fitted. Since such leakage-free designs are only used comparatively rarely in comparison to the conventional designs described above, such a custom-made design could only be realized with a comparatively high financial outlay.
  • the invention has for its object to provide a compact valve assembly that can be produced with minimal effort.
  • a plunger is formed on the end of the main slide of the main valve, which, when the main slide is actuated appropriately, lifts the pilot piston from its pilot seat, so that a control surface of the check valve which is effective in the closing direction is relieved.
  • the main slide is particularly simple when the plunger is used as an insert in the main slide.
  • the valve housing placed on the side can be constructed particularly compactly in that the axis of the pilot valve runs parallel to the axis of the check valve.
  • control surface of the shut-off valve which is effective in the closing direction, is connected via the pilot valve to a control connection, which has one in the axial displacement of the main slide of the main valve described at the beginning comparatively low pressure, for example corresponding to the tank pressure.
  • the pilot piston of the pilot valve is preferably provided with fine control grooves, via which the connection to the low-pressure connection, for example the control connection described above, is gradually opened.
  • a pressure relief / suction valve is assigned to the shut-off valve.
  • a connection of this valve is connected via a tank channel to a tank connection of the valve arrangement.
  • the construction of the laterally attached valve housing is particularly simple if this tank channel surrounds a housing cartridge of the check valve as an annular channel, which preferably extends from the laterally attached valve housing into the valve disk.
  • the main slide is biased into its neutral division by a return spring device.
  • This return spring device is designed such that the return spring, which acts counter to the setting direction for actuating the pilot valve, only becomes effective after a predetermined initial stroke of the main spool, so that the main spool initially only has to be displaced essentially against the force acting on the pilot piston.
  • this is achieved in that the return spring in question is supported on a spring plate which only runs onto a support shoulder after the aforementioned initial stroke, so that after the run-up the further axial displacement of the main slide against the force of the return spring.
  • FIG. 1 is a greatly simplified circuit diagram of the valve assembly according to the invention.
  • Figure 2 shows a section through a valve assembly according to the invention in disc design
  • FIG. 3 shows a partial representation of the valve arrangement from FIG. 2.
  • FIG. 1 shows a greatly simplified hydraulic diagram of a directional valve element 2 for controlling a double-acting hydraulic cylinder 4.
  • the directional valve element 2 is designed with a pressure connection P, a tank connection T, two working connections A, B, an LS connection (not shown) and two control connections a, b.
  • the working port A is connected to a piston chamber-side cylinder chamber 6 and the other working port B is connected to an annular chamber 8 of the hydraulic cylinder.
  • the directional valve element 2 contains a main valve 10 designed as a continuously adjustable directional valve, the main slide 12 of which is biased into the zero position shown by a return spring device 14.
  • the main slide 12 is displaced by applying a control pressure via the two control connections a, b.
  • the main valve 10 is designed with a speed part forming a metering orifice (not shown in FIG.
  • the metering orifice is followed by a pressure compensator 16, indicated schematically in FIG. 1, which is acted upon in the opening direction by the pressure at the outlet of the metering orifice and in the closing direction by the load pressure on the consumer (hydraulic cylinder 4).
  • the downstream pressure compensator 16 keeps the pressure drop across the metering orifice formed by the main valve 10 constant, so that a flow pressure-independent flow distribution (LUDV) is made possible.
  • LUDV flow pressure-independent flow distribution
  • a pilot-operated check valve 18 is provided in the directional valve element 2, the pilot valve 20 of which is arranged approximately coaxially with the valve axis of the main valve 10. That is, shut-off valve 18 and pilot valve 20 are arranged separately from one another in the variant according to the invention.
  • the check valve 18 allows a pressure medium flow from the main valve 10 to the working port A; a pressure medium flow in the reverse direction is only possible when the pilot valve 20 is actuated.
  • pilot valve 20 Via the pilot valve 20 an effective control surface in the closing direction of the check valve can be relieved, so that the check valve 18 is opened by the pressure in the cylinder chamber 6 and a pressure medium flow from the cylinder chamber 6 to the tank connection T is possible.
  • the pilot valve 20 is actuated according to the invention by means of a tappet 22 of the main slide 12, by means of which a pilot piston 24 can be lifted off a valve seat, so that the pressure medium acting on the control surface of the check valve 18 acting in the closing direction can be released towards the control connection a.
  • a control pressure which corresponds approximately to the tank pressure.
  • a pressure / suction valve 28 is arranged, which on the one hand limits the pressure in the working channel 26 to a maximum value and, when the pressure is exceeded, opens a tank channel 30 leading to the tank port T, in the case a very rapid extension movement of the hydraulic cylinder 4, for example caused by driving movements etc. a suction of pressure medium from the tank channel 30 enables.
  • a pilot-controlled pressure / Infeed valve 34 is provided, via which the pressure in the further working channel 32 can be limited to a variable maximum value and via which pressure medium can be fed from the tank channel 30 into the further working channel 32.
  • the working connection B, the pressure connection P, the tank connection T, the control connection b (not shown) and the LS connection are formed in the valve disk 36.
  • the valve disk 36 is penetrated by a valve bore 40 in which the main slide 12 of the main valve 10 is guided.
  • a central pressure chamber 42, a pressure compensator channel 44, two connecting channels 46, 48, the working channel 26, the further working channel 32 and tank channel sections 50, 52 open in the radial direction.
  • the main slide 12 is at its left end section with an end-face annular collar 54 and formed at its right end portion with an annular collar 56.
  • the main slide 12 has two control collars 58, 60 of the directional part, the control collar 58 being assigned to the working connection A and the control collar 60 to the working connection B. Between the two control collars 58, 60 is located at the measuring diaphragm collar 62, which is provided with fine control grooves 64 in both ring end faces.
  • the return spring device 14 is placed on the right side surface of the valve disk 36 in FIG.
  • This has a return spring 68, the right end section of which is supported in FIG. 2 on a spring plate 70 which is guided axially displaceably on a sliding guide 72 inserted into the main slide 12 on the end face.
  • This sliding guide has a radial shoulder 74 against which the spring plate 70 is biased to the right by the force of the return spring 68.
  • the other end of the return spring 68 is supported on a further spring plate 76, which in turn is biased against the end face of the main slide 12 via the return spring 68.
  • a further spring plate 76 which in turn is biased against the end face of the main slide 12 via the return spring 68.
  • the further spring plate 76 is sliding on the right annular collar 56 of the main slide 12 and on the slide guide 72 guided.
  • the spring plates 70, 76 can thus move towards one another when the main slide 12 is axially displaced.
  • the return spring 68 and spring plates 70, 76 receiving spring chamber 82 is encompassed by a cover 84 and can be acted upon by the pressure at the control connection b.
  • the working channel 32 assigned to the working connection B can be connected to the tank channel T via the pressure / feed valve 34 in order to limit the pressure in the working channel 26 or to suck in pressure medium from the pressure medium tank.
  • the pressure / feed valve shown in Figure 2 is designed with pilot control. It is a cartridge-type standard component, so that further explanations are unnecessary.
  • the pressure compensator 16 is inserted, the valve axis of which runs at right angles to that of the main valve 10.
  • the pressure compensator piston 82 is in the opening direction by the pressure downstream of the measuring orifice 82 delimited by the measuring orifice collar 62 and in the closing direction by the pressure at the LS channel and
  • the output connection 84 of the pressure compensator 16 is connected via a load holding valve 86, 88 to the connection channel 46 assigned to the working connection A and to the connecting channel 48 assigned to the working connection B.
  • a load holding valve 86 is in principle a non-return valve which enables a pressure medium flow from the outlet connection 84 of the pressure compensator 16 to the associated channel 44 or 46 and in
  • the work port A is in the side Valve housing 38 is formed.
  • the pilot valve 20 which is formed coaxially to the main valve 10, the check valve 18 assigned to it and the pressure / suction valve 28 assigned to the working connection A, are accommodated, the axes of these valve elements being parallel (18, 28) or coaxial (20) Axis of the main valve 10 run.
  • valve housing Details of the valve housing are explained below with reference to the partial representation according to FIG. 3.
  • the tank bore 112 is formed by a vertical bore and a horizontal bore intersecting it, the vertical bore being closed by a closure piece 114, while the pressure / suction valve 28 is inserted into the horizontal bore.
  • the tank bore 112 opens into an annular space 116 which is delimited by a radially enlarged part of the transverse bore 96 of the valve housing 38 and the outer circumference of the end section 94 of the housing cartridge 92.
  • the tank channel section 50 opens into this annular space 116, so that the tank bore 112 is connected to the tank connection T.
  • the pressure medium flows from the pressure compensator 16 via the load holding valve 86 into the connecting channel 46. Due to the axial displacement of the main slide 12, a control edge formed by the control collar 58 has opened the connection between the connecting channel 46 and the further working channel 32, so that the pressure medium can flow into the axial bore 98 of the housing cartridge 92 of the check valve 18 via the working channel 26.
  • the pressure of the pressure medium is so great that the cone 102 is lifted against the force of the compression spring 104 and the low pressure force in the spring chamber 105 from the valve seat 100 and the pressure medium via the radial bore star 108 and the channel 110 to the working connection A and from there a working line 148 (FIG. 1) can flow into the cylinder space 6 - the piston of the hydraulic cylinder 4 extends.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)

Abstract

L'invention concerne un dispositif à soupapes servant à actionner des consommateurs (4) indépendamment de la pression de charge, comprenant une soupape principale (10), qui présente une partie directionnelle et une partie d'obturation doseuse. Ledit dispositif à soupapes présente une soupape d'arrêt (18) conçue pour bloquer sans fuite une conduite de travail qui mène vers le consommateur. Ladite soupape d'arrêt (18) est pourvue d'une soupape pilote (20), par l'intermédiaire de laquelle une chambre de pression de ladite soupape d'arrêt (18), qui agit dans le sens de fermeture, peut être déchargée vers un réservoir ou une source basse pression. Selon l'invention, ladite soupape pilote (20) est ouverte par un tiroir principal (12) de ladite soupape principale (10).
EP03706251A 2002-03-04 2003-01-27 Dispositif a soupapes Expired - Fee Related EP1481167B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10209399 2002-03-04
DE10209399 2002-03-04
DE10218783A DE10218783A1 (de) 2002-03-04 2002-04-26 Ventilanordnung
DE10218783 2002-04-26
PCT/DE2003/000209 WO2003074883A1 (fr) 2002-03-04 2003-01-27 Dispositif a soupapes

Publications (2)

Publication Number Publication Date
EP1481167A1 true EP1481167A1 (fr) 2004-12-01
EP1481167B1 EP1481167B1 (fr) 2008-04-16

Family

ID=27789724

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03706251A Expired - Fee Related EP1481167B1 (fr) 2002-03-04 2003-01-27 Dispositif a soupapes

Country Status (5)

Country Link
US (1) US7080663B2 (fr)
EP (1) EP1481167B1 (fr)
JP (1) JP4495973B2 (fr)
DE (1) DE50309629D1 (fr)
WO (1) WO2003074883A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007263142A (ja) * 2006-03-27 2007-10-11 Toyota Industries Corp 油圧制御装置
DE102006060326B4 (de) * 2006-12-20 2008-11-27 Sauer-Danfoss Aps Hydraulische Ventilanordnung
DE102006060334B4 (de) * 2006-12-20 2011-08-25 Sauer-Danfoss Aps Hydraulische Ventilanordnung

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4359931A (en) * 1981-01-19 1982-11-23 The Warner & Swasey Company Regenerative and anticavitation hydraulic system for an excavator
JPH06193606A (ja) * 1992-12-22 1994-07-15 Komatsu Ltd 圧力補償弁を備えた操作弁
JP3154605B2 (ja) * 1993-11-17 2001-04-09 川崎重工業株式会社 作動シリンダの制御装置
DE4417962A1 (de) 1994-05-21 1995-11-23 Rexroth Mannesmann Gmbh Steueranordnung für wenigstens zwei hydraulische Verbraucher
JP3502164B2 (ja) * 1994-07-25 2004-03-02 株式会社ナブコ 多連方向切換弁装置
DE19646447A1 (de) 1996-11-11 1998-05-14 Rexroth Mannesmann Gmbh Ventilgehäuse
DE19831595B4 (de) * 1998-07-14 2007-02-01 Bosch Rexroth Aktiengesellschaft Hydraulische Schaltung
DE19835015A1 (de) 1998-08-03 2000-02-10 Linde Ag Hydrostatisches Antriebssystem
DE19909714B4 (de) * 1999-03-05 2008-05-21 Linde Material Handling Gmbh Steuerventileinrichtung für einen hydraulischen Verbraucher
DE10033757B4 (de) * 2000-07-12 2011-06-22 Linde Material Handling GmbH, 63743 Steuereinrichtung für einen hydraulischen Verbraucher
DE10047632B4 (de) * 2000-09-26 2014-01-02 Linde Hydraulics Gmbh & Co. Kg Ventileinrichtung für einen doppelt wirkenden hydraulischen Verbraucher
US6581639B2 (en) * 2000-10-20 2003-06-24 Case Corporation Low leak boom control check valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO03074883A1 *

Also Published As

Publication number Publication date
WO2003074883A1 (fr) 2003-09-12
US7080663B2 (en) 2006-07-25
JP2005519243A (ja) 2005-06-30
US20050115620A1 (en) 2005-06-02
EP1481167B1 (fr) 2008-04-16
DE50309629D1 (de) 2008-05-29
JP4495973B2 (ja) 2010-07-07

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