EP0667459B1 - Unité de soupape à électro-aimant proportionnel - Google Patents

Unité de soupape à électro-aimant proportionnel Download PDF

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Publication number
EP0667459B1
EP0667459B1 EP95100336A EP95100336A EP0667459B1 EP 0667459 B1 EP0667459 B1 EP 0667459B1 EP 95100336 A EP95100336 A EP 95100336A EP 95100336 A EP95100336 A EP 95100336A EP 0667459 B1 EP0667459 B1 EP 0667459B1
Authority
EP
European Patent Office
Prior art keywords
piston
valve unit
electromagnet
hydraulic
unit according
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
EP95100336A
Other languages
German (de)
English (en)
Other versions
EP0667459A1 (fr
Inventor
Bernd Niethammer
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.)
HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Hilite Germany GmbH
Original Assignee
HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Hydraulik Ring GmbH
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 HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH, Hydraulik Ring GmbH filed Critical HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Publication of EP0667459A1 publication Critical patent/EP0667459A1/fr
Application granted granted Critical
Publication of EP0667459B1 publication Critical patent/EP0667459B1/fr
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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B13/0442—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with proportional solenoid allowing stable intermediate positions
    • 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
    • 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
    • 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

Definitions

  • the invention relates to an electro-proportional solenoid valve unit according to the preamble of claim 1.
  • the invention is based, the generic electro-proportional solenoid valve unit the task to train so that the Flow rate of the hydraulic medium depending on the Current with which the electromagnet is applied, steadily changed.
  • the invention is illustrated by one in the drawing Embodiment explained in more detail.
  • the Drawing shows partly in longitudinal section and partly in view an electro-proportional solenoid valve unit according to the invention.
  • the piston of the valve unit in its initial position and in the lower half in one by a pestle shown an electromagnet shifted position.
  • the electro proportional solenoid valve unit has one Electromagnet 1, the plunger 2 of which rests on a piston 3. It is under the force of a compression spring 4, which pushes the piston 3 against the plunger 2.
  • the electromagnet 1 is designed in a known manner, so that it is not described in detail. It is on an installation housing 5 attached, which a receptacle 6 for has a valve housing 7. In it is the piston 3 longitudinally displaceable.
  • the valve housing 7 has connections 8 to 10, via which, controlled by the piston 3, hydraulic medium to or from a consumer in known Way is promoted.
  • On the installation housing 5 are the corresponding consumers and the hydraulic medium containing tank also connected in a known manner.
  • the compression spring 4 is supported on one in the valve housing 7 screwed adjusting screw 11. By different screwing in the adjusting screw 11 in the valve housing 7, the biasing force the compression spring 4 and thus the position of the piston 3 Infinitely adjustable magnetic force.
  • the adjusting screw 11 has a through opening through which the hydraulic medium can flow back to the tank.
  • the piston 3 is facing the adjusting screw 11 Side provided with a recess 12 on the Bottom 13 the compression spring 4 is supported.
  • the piston has a central one that extends in its axial direction Bore 14 in the direction of the plunger 2 of the electromagnet 1 is closed by a floor 15. On the plunger 2 of the electromagnet 1 lies on this base 15 on. A opens radially into the bore 14 of the piston 3 Opening 16 through which the hydraulic medium into the bore 14 of the piston 3 can reach.
  • the outside of the piston has an annular channel 17 which closed against the electromagnet 1 by an annular web 18 is.
  • the piston 3 has another ring channel 19, which is much longer than the ring channel 17 and opposite this ring channel 17 by a Ring web 20 is separated.
  • Shown in the top half of the drawing left end position of the piston 3 is the working connection 10 open to a hydraulic chamber 21 in which the compression spring 4 lies and in which the central bore 14 of the piston 3 opens.
  • Via the radial opening 16 is the central bore 14 with the annular channel 17 of the Piston 3 connected, in which the opening 16 opens.
  • In this left end position of the piston 3 is also the Working port 8 with the ring channel 19 of the piston 3rd connected. Since also the connection 9, which with the (not shown) pump of the hydraulic system via a connection 27 of the built-in housing 5 is connected to the Ring channel 19 is connected, is thus a connection between the working port 8 and the pressure port 9 available.
  • the other working connection 10 of the valve housing 7 is in this left end position of the piston 3 not closed, so that a connection to the hydraulic room 21 exists.
  • the piston 3 has in the left End position distance from the bottom 22 of the valve housing 7. This is a between the piston 3 and the bottom 22 further hydraulic space 23 formed by at least a bore 24 axially penetrating the piston 3, the must not come into contact with the opening 16 with the opposite hydraulic chamber 21 is connected.
  • the piston 3 a further, axially penetrating bore 25, which connects the two hydraulic spaces 21 and 23 with each other.
  • valve unit Unit connected, for example a piston-cylinder unit. If this unit is to be operated, the electromagnet 1 is switched on, causing the plunger 2 is extended. It moves the piston 3 against the force of the compression spring 4. When moving the piston 3 is the connection between the pressure port 9 and the working port 8 closed while the connection between the working connection 10 and the pressure connection 9 is opened. So that can be under pressure Hydraulic medium via the pressure connection 9 and the Ring channel 19 flow to the working connection 10, from which it via a connection 28 of the installation housing 5 to be driven Flow aggregate and put it in the desired one Press way.
  • the holes 24, 25 have in the illustrated embodiment smaller cross section than the central hole 14.
  • the holes 14 and 24, 25 can also be the same Diameter. It is also possible that the Compensating holes 24, 25 larger diameter than that have central bore 14 of the piston 3.
  • the piston 3 designed as a hollow piston Insert socket.
  • the outer wall of one Bush and / or in the inner wall of the bore of the piston can at least one each over the piston or Throughout the socket length can be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Servomotors (AREA)

Claims (5)

  1. Unité de soupape à électroaimant à action proportionnelle comportant un boítier (7), dans lequel est déplaçable, sous l'action d'un poussoir (2) de l'électroaimant (1) et à l'encontre de la force (4) d'un ressort, un piston (3) qui est agencé sous la forme d'un piston creux, qui comporte deux canaux annulaires (17,19), parmi lesquels un canal annulaire (19) est séparé d'une chambre hydraulique (21) située du côté du ressort et reliée à un raccord de réservoir, et l'autre canal annulaire (17) est relié par au moins une ouverture (16) à la cavité (14) du piston (3), et les deux canaux annulaires peuvent être reliés alternativement, lorsque l'électroaimant (1) est alimenté en courant et lorsqu'il n'est pas alimenté en courant, à deux raccords de travail (8,10), parmi lesquels un raccord de travail (8,10) peut être relié respectivement à un raccord de pression (9) et l'autre raccord de travail (10,8) peut être relié respectivement à un réservoir, caractérisée en ce que la cavité (21) située du côté du ressort est reliée, par l'intermédiaire d'au moins une canalisation de compensation (24,25), à un réservoir hydraulique (23) situé du côté de l'électroaimant et qui est séparé de la cavité (14) du piston (3) par un fond (15) du piston.
  2. Unité de soupape selon la revendication 1, caractérisée en ce que le poussoir (2) de l'électroaimant (1) s'applique contre le fond (15) de la cavité (14) du piston (3).
  3. Unité de soupape selon la revendication 1 ou 2, caractérisée en ce que la canalisation de compensation (24,25) est prévue dans le piston (3).
  4. Unité de soupape selon l'une des revendications 1 à 3, caractérisée en ce que la canalisation de compensation (24,25) est un perçage axial situé dans le piston (3).
  5. Unité de soupape selon l'une des revendications 1 à 4, caractérisée en ce que le piston (3) possède un renfoncement frontal (12), dans lequel pénètre un ressort de pression (4).
EP95100336A 1994-02-10 1995-01-12 Unité de soupape à électro-aimant proportionnel Expired - Lifetime EP0667459B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9402206U DE9402206U1 (de) 1994-02-10 1994-02-10 Elektroproportionalmagnet-Ventileinheit
DE9402206U 1994-02-10

Publications (2)

Publication Number Publication Date
EP0667459A1 EP0667459A1 (fr) 1995-08-16
EP0667459B1 true EP0667459B1 (fr) 1999-11-03

Family

ID=6904399

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95100336A Expired - Lifetime EP0667459B1 (fr) 1994-02-10 1995-01-12 Unité de soupape à électro-aimant proportionnel

Country Status (4)

Country Link
US (1) US5592972A (fr)
EP (1) EP0667459B1 (fr)
JP (1) JPH07224965A (fr)
DE (2) DE9402206U1 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19531444A1 (de) * 1995-08-26 1997-02-27 Hydraulik Ring Gmbh Betätigungseinheit für eine Verstelleinrichtung, vorzugsweise für eine Ventilhubverstelleinrichtung von Kraftfahrzeugen
JP3666072B2 (ja) * 1995-09-13 2005-06-29 アイシン精機株式会社 切替弁
US5894860A (en) * 1997-06-12 1999-04-20 General Motors Corporation Proportional pressure control solenoid valve
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
US6161585A (en) * 1999-03-26 2000-12-19 Sterling Hydraulics, Inc. High flow proportional pressure reducing valve
DE10006784A1 (de) * 2000-02-18 2001-08-23 Bosch Gmbh Robert Elektromagnet zur Betätigung des Stellglieds eines Ventils
AU2002211490A1 (en) * 2000-10-04 2002-04-15 The Trustees Of The University Of Pennsylvania Compositions and methods of using capsid protein from flaviviruses and pestiviruses
DE10150238C2 (de) * 2001-10-11 2003-09-25 Hydac Fluidtechnik Gmbh Druckregelventil, insbesondere Proportional-Druckregelventil
US6769252B2 (en) 2001-12-10 2004-08-03 Caterpillar Inc Fluid system having variable pressure relief
DE102005037480A1 (de) * 2005-08-09 2007-02-15 Schaeffler Kg Steuerventil und Verfahren zur Herstellung desselben
US8127786B2 (en) * 2008-04-03 2012-03-06 Hamilton Sundstrand Corporation Proportional selector valve for selecting between two pressure sources
US20180266169A1 (en) 2017-03-14 2018-09-20 Biofilm Ip, Llc Garage door systems and methods
US20180266172A1 (en) 2017-03-14 2018-09-20 Biofilm Ip, Llc Garage door systems and methods
DE102018208893A1 (de) * 2018-06-06 2019-12-12 Robert Bosch Gmbh Direktgesteuertes hydraulisches Wegeventil
US11261765B1 (en) * 2020-08-25 2022-03-01 Borgwamer Inc. Control valve assembly of a variable cam timing phaser
CN215487921U (zh) * 2021-07-22 2022-01-11 亘帝企业有限公司 流体压力比例阀

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3125143A1 (de) * 1981-06-26 1983-01-13 Mannesmann Rexroth GmbH, 8770 Lohr "druckminderventil"
US5117869A (en) * 1990-03-30 1992-06-02 Sterling Hydraulics, Inc. Solenoid valve
DE4131384C2 (de) * 1991-09-20 1994-10-06 Rexroth Mannesmann Gmbh Elektrisch betätigbares Ventil
DE4133536C2 (de) * 1991-10-10 1995-11-30 Hydraulik Ring Gmbh Hydraulikmagnetventil
AT398114B (de) * 1992-03-12 1994-09-26 Hoerbiger Fluidtechnik Gmbh Proportional-wegeventil

Also Published As

Publication number Publication date
JPH07224965A (ja) 1995-08-22
US5592972A (en) 1997-01-14
DE9402206U1 (de) 1994-05-05
EP0667459A1 (fr) 1995-08-16
DE59507148D1 (de) 1999-12-09

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