EP2198357A2 - Soupape à tiroir - Google Patents

Soupape à tiroir

Info

Publication number
EP2198357A2
EP2198357A2 EP08804599A EP08804599A EP2198357A2 EP 2198357 A2 EP2198357 A2 EP 2198357A2 EP 08804599 A EP08804599 A EP 08804599A EP 08804599 A EP08804599 A EP 08804599A EP 2198357 A2 EP2198357 A2 EP 2198357A2
Authority
EP
European Patent Office
Prior art keywords
valve
slide
pressure
valve sleeve
sleeve
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.)
Withdrawn
Application number
EP08804599A
Other languages
German (de)
English (en)
Inventor
Stefan A. Drumm
Lothar Schiel
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.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
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 Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of EP2198357A2 publication Critical patent/EP2198357A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
    • 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
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/04—Control of fluid pressure without auxiliary power
    • G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
    • G05D16/101—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger the controller being arranged as a multiple-way valve
    • 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
    • Y10T137/86702—With internal flow passage
    • 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 slide valve according to the preamble of patent claim 1.
  • a further disadvantage results from the fact that the pressure medium, as it flows through the variable pressure build-up passage cross-section, experiences flow velocities whose axial component is directed counter to the flow direction present further downstream. This flow direction reversal can lead to undesirable turbulence and flow noise.
  • the slide valve shown in longitudinal section is used to control the hydraulic pressure at a working port A to values between a low pressure and a high pressure, for which purpose an axially symmetrical valve slide 1 is received linearly movable in a valve sleeve 3.
  • the advantageously very short valve sleeve 3 is fitted pressure-tight in a housing 4, whereby hydraulic chambers are delimited, which are connected to the low and high pressure port T, P and the working port A.
  • the pressure-tight connection of the valve sleeve 3 and housing 4 can be realized in a known manner by static seals, but preferably a press connection - for example, the pressing a steel sleeve into an aluminum housing - which requires no further sealing measures.
  • the pressure ports T, P, A are preferably realized by easy to produce bores.
  • first position (pressure reduction position) of the valve slide 1 of the working port A is on the one side hollow drilled valve spool 1 and arranged in the vicinity of the closed end of the valve spool 1 radial bore 9 with the Niederbuchan- Closing T connected.
  • first position (pressure reduction position) of the valve slide 1 of the working port A is on the one side hollow drilled valve spool 1 and arranged in the vicinity of the closed end of the valve spool 1 radial bore 9 with the Niederdruckan- Closing T connected.
  • valve spool 1 When operating the valve spool 1 under an acting in the figure to the left on the valve spool 1 Ventilan Kunststoff F in ascending order, with the shutting off and releasing the fluid connections between the pressure ports T, P, A advantageously by two on the front sides of the valve sleeve 3 circumferential low and high pressure control edges 5, 6 takes place.
  • control edges 5, 6 are used for the pressure build-up and dismantling, which cooperate with the Schieber horrkanten that the release of the hydraulic passage cross section is uniform over the entire circumference of the guide gap between valve spool 1 and valve sleeve 3.
  • the control edges 5, 6 of the valve sleeve 3 are formed as circumferential edges in the circumferential direction to the axis of symmetry S, which form a part of the lateral surface of the valve sleeve 3.
  • valve sleeve 3 if for the purpose of training the control edges 5, 6 in a particularly simple manufacturing process, only the two ends are ground flat.
  • the high pressure is conducted from the port P through the valve sleeve 3 into an outer groove of the valve slide 1, and thus stands at the pressure buildup control edge "from the inside.”
  • a circumferential groove 12 forms a hydraulic valve on the valve slide 1 together with the jacket surface of the valve sleeve 3 Annular chamber 15, which via a radial bore 11 in the Ven- tilhülse 3 is permanently connected to the high pressure port P in connection.
  • each closed control edge is reduced by the sealing effect of a gap to an unavoidable leakage volume flow.
  • These columns are releasable in the intended operation, any suspended particles in the pressure medium, which can settle in these columns are flushed away during a pressure control again.
  • a sealing ring 8 is provided, which reduces the gap flow to virtually zero, thus preventing flooding of dirt particles.
  • the elastomeric sealing ring 8 is preferably inserted in a web 17 of the valve slide 1 which runs around the axis of symmetry S, namely in a groove arranged between the two annular chambers 15, 16, so that a hydraulic separation of the annular chambers 15, 16 is ensured.
  • a control edge free of the entire circumference can no longer guide the slider.
  • valve slide 1 within the annular chambers 15, 16 has a plurality of radial projections which project for the purpose of radial guidance of the valve spool 1 within the axial bore of the valve sleeve 3 to the lateral surface , wherein the projections in the circumferential direction with each other and in the axial direction of the annular chambers 15, 16 delimiting circumferential webs 17 are spaced such that the hydraulic flow is not impaired.
  • the radial bore 9 connects the axial bore in the valve slide permanently with a formed on the outside of the valve slide 1 annular chamber 16. This results depending on the slide movement, a variable passage cross section as a variable connection of the annular chamber 16 to the low pressure port T, which by moving the valve spool 1 relative to Valve sleeve 3 is also lockable. In the shut-off state, the outflow of pressure medium from the working connection A to the low-pressure connection T is prevented except for the leakage which is unavoidable in the case of a gap seal.
  • connection AT remains closed while the connection PA is opened by the trained in the valve sleeve 3 high-pressure control edge 6 and formed in the valve spool 1 high-pressure control edge extending over the entire circumference of the control edges Release the passage opening.
  • the low-pressure control edge 5 and the high-pressure control edge 6 are preferably formed at the opposite ends of the cylindrical valve sleeve 3 and so make it particularly simple and inexpensive by surface grinding of the cylinder bottom and top surface.
  • the closure of the low-pressure control edge 5 is initially effected by the jacket surface of the valve slide 1 before the high-pressure control edge 6 can be released by the valve slide 1 in order to overflow the high-pressure connection P along the tapered section of the jacket surface of the valve slide 1 High pressure control edge 6 to allow the working port A.
  • valve spool 1 and the valve sleeve 3 takes place radially and to a certain extent tangentially from the inside to the outside, over the radial junction of the high pressure port P, the pressure medium is initially deflected axially in the tapered portion along a circumferential groove of the valve spool 1, before it between the valve spool 1 and the high pressure control edge 6 can flow out circularly.
  • the length of the valve sleeve 3 is determined by the axial distance between the low pressure and high pressure control edge 5, 6, whereby the valve spool 1 is guided exclusively between the low pressure and high pressure control edge 5, 6 in the valve sleeve 3. This causes even with a very tight slide fit a smooth movement of the valve spool 1, which is also guided free of transverse forces precisely in the valve sleeve 3.
  • valve sleeve 3 is bounded on both sides to the low pressure and high pressure control edge 5, 6 by arbitrarily large selectable chambers 2, 10 in the housing 4, whereby the overflow of the aforementioned two control edges 5, 6, the pressure medium in each case one or the other relatively wide chamber 2, 10th flows, whereby the occurring at the overflow of the edges high flow velocities are reduced, which causes a noise-preventing flow calming, before it reaches the working pressure or low pressure port A, T.
  • the left chamber 10 is thus axially limited by the provided with the working port A portion of the housing 4 and the high pressure control edge 6 at the left end portion of the valve sleeve 3, while the right chamber 2 from the low pressure control edge 5 at the right end portion of the valve sleeve 3 to extends axially to the wall of the housing 4.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Multiple-Way Valves (AREA)
  • Sliding Valves (AREA)

Abstract

L'invention concerne une soupape à tiroir, avec un tiroir de soupape (1) axialement mobile par rapport à la douille de soupape (3). Afin de définir la taille de sections de passage variables tant pour une liaison d'élévation de la pression entre un branchement à haute pression (P) et un branchement de travail (A) que pour une liaison de diminution de la pression entre le branchement de travail (A) et un branchement à basse pression (T), des arêtes de commande faisant le tour de la circonférence sont formées sur la circonférence extérieure du tiroir de soupape (1), et elles coopèrent avec des arêtes de commande (5, 6) de la douille de soupape (3). Selon l'invention, les arêtes de commande (5, 6) de la douille de soupape (3) sont réalisées sous la forme d'arêtes faisant le tour de la circonférence relativement à l'axe de symétrie (S), arêtes qui font partie d'une surface d'enveloppe de la douille de soupape (3).
EP08804599A 2007-10-02 2008-09-23 Soupape à tiroir Withdrawn EP2198357A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007047201 2007-10-02
DE102008037981.6A DE102008037981B4 (de) 2007-10-02 2008-08-16 Schieberventil
PCT/EP2008/062682 WO2009047115A2 (fr) 2007-10-02 2008-09-23 Soupape à tiroir

Publications (1)

Publication Number Publication Date
EP2198357A2 true EP2198357A2 (fr) 2010-06-23

Family

ID=40418311

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08804599A Withdrawn EP2198357A2 (fr) 2007-10-02 2008-09-23 Soupape à tiroir

Country Status (4)

Country Link
US (1) US8251097B2 (fr)
EP (1) EP2198357A2 (fr)
DE (1) DE102008037981B4 (fr)
WO (1) WO2009047115A2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009006890A1 (de) 2009-01-30 2010-08-05 Continental Teves Ag & Co. Ohg Schieberventil
DE102009012952A1 (de) 2009-03-12 2010-09-16 Continental Teves Ag & Co. Ohg Ventilbaugruppe
US8960226B2 (en) * 2011-01-12 2015-02-24 Gm Global Technology Operations, Llc Transmission hydraulic control system having fluid bypass sleeve
US20150101674A1 (en) * 2012-12-20 2015-04-16 Hydril Usa Distribution, Llc Subsea pressure regulator
AT513849B1 (de) * 2013-03-04 2014-08-15 Tmt Bbg Res And Dev Gmbh Steuerung der Arbeitsfrequenz eines Schlagwerkes

Family Cites Families (17)

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Publication number Priority date Publication date Assignee Title
US1825290A (en) * 1928-09-27 1931-09-29 Chicago Pneumatic Tool Co Throttle handle
US2893428A (en) * 1956-05-22 1959-07-07 Int Basic Economy Corp Solenoid operated pressure balanced flow valve
US3189049A (en) * 1963-08-02 1965-06-15 Carl M Carlson Multi-channel valve
US3318333A (en) * 1965-01-28 1967-05-09 Novi Tool And Machine Company Pressure-sealed piston-and-cylinder assembly
DE7030280U (de) * 1970-08-12 1971-04-22 Festo Maschf Stoll G Ventil.
US3706322A (en) * 1971-03-22 1972-12-19 Carl M Carlson Valve
US3910466A (en) * 1974-01-09 1975-10-07 Roean Ind Air actuated plastic compound dispensing device
US3927830A (en) * 1974-09-25 1975-12-23 Borg Warner Control valve
DE3125143A1 (de) * 1981-06-26 1983-01-13 Mannesmann Rexroth GmbH, 8770 Lohr "druckminderventil"
DE19622948C2 (de) * 1996-06-07 2001-08-02 Mannesmann Rexroth Ag Manuell betätigbares hydraulisches Vorsteuergerät
DE19708741C2 (de) 1997-03-04 2001-02-22 Dbt Gmbh Druckgesteuertes 3/2-Wegeventil
DE19727180C2 (de) 1997-06-26 2003-12-04 Hydraulik Ring Gmbh Hydraulisches Ventil, insbesondere zur Steuerung einer Nockenwellenverstellung in einem Kraftfahrzeug
DE19853670C5 (de) 1998-11-20 2019-01-10 Hilite Germany Gmbh Einrichtung zur Nockenwellenverstellung
DE19953209A1 (de) 1999-11-05 2001-06-13 Fluidtech Gmbh Ventil, insbesondere Druckregelventil
DE10213258C1 (de) * 2002-03-25 2003-08-14 Bosch Rexroth Ag Pneumatisches Schieberventil miteinem spritzgegossenen Ventilgehäuse
DE202005014866U1 (de) * 2005-06-21 2006-02-02 Dams-Blasberg Vertriebs Gmbh Ventilpatrone
DE102007031290A1 (de) * 2007-01-31 2008-08-07 Continental Teves Ag & Co. Ohg Schieberventil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009047115A2 *

Also Published As

Publication number Publication date
US8251097B2 (en) 2012-08-28
WO2009047115A2 (fr) 2009-04-16
DE102008037981A1 (de) 2009-04-09
WO2009047115A3 (fr) 2010-07-29
DE102008037981B4 (de) 2023-01-26
US20100243941A1 (en) 2010-09-30

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