EP2585888A1 - Soupape de régulation de pression à régulation continue - Google Patents

Soupape de régulation de pression à régulation continue

Info

Publication number
EP2585888A1
EP2585888A1 EP11723417.9A EP11723417A EP2585888A1 EP 2585888 A1 EP2585888 A1 EP 2585888A1 EP 11723417 A EP11723417 A EP 11723417A EP 2585888 A1 EP2585888 A1 EP 2585888A1
Authority
EP
European Patent Office
Prior art keywords
armature
connection
valve according
bore
control valve
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.)
Ceased
Application number
EP11723417.9A
Other languages
German (de)
English (en)
Inventor
Werner Buse
Franz-Josef Schnelker
Rolf Dohrmann
Christoph Sadowski
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.)
Pierburg GmbH
Original Assignee
Pierburg 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 Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP2585888A1 publication Critical patent/EP2585888A1/fr
Ceased legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/20—Control of fluid pressure characterised by the use of electric means
    • G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
    • G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
    • G05D16/2022—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means actuated by a proportional solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7781—With separate connected fluid reactor surface
    • Y10T137/7793—With opening bias [e.g., pressure regulator]

Definitions

  • the invention relates to a Druckregeiventii with a housing having a wound on a bobbin coil, an axially displaceable in a bearing armature, a core and a Fiussieit issued, and having a first Anschiussbohrung for connection to a tank and a connecting piece, wherein the Anschiussstutzen having a valve seat for a Ventiigiied the anchor.
  • Such pressure control valves are used in particular in hydraulic actuators, in controls for motor vehicle automatic transmission or in combination with a pressure or flow-controlled engine oil pump. These can be so-called 0 n / off valves or so-called modulator valves, which have the advantage that the throughput is infinitely variable.
  • a stepwise controllable pressure regulator which is known from DE 44 02 523 C2 should be mentioned here.
  • the armature of a per se known working according to the proportional principle Druckregeiventii cooperates with a valve member, which can be expressed in simplified terms, a connection between a consumer port and a tank and close. The Anschiussbohrung to the tank and the connection to the consumer are formed in a connecting piece.
  • the invention is therefore an object of the invention to provide a pressure relief valve, which is infinitely variable at a low control effort and has good damping properties. Moreover, it should be as inexpensive and easy to produce.
  • a second connection bore is provided for connection to a consumer and that in the remote from the core end of the connecting piece a control bore is provided with a mounted therein regeiorgan, wherein the armature and the Regeiorgan at least in the opening direction of the pressure control valve in a force-transmitted active connection.
  • the first connection hole to connect to a tank and the second connection hole with the consumer to be controlled.
  • the control pressure is applied, which acts together with the magnetic force in the direction and sum against the spring force. In this way, a simple oil pressure control of the consumer is ensured, wherein the Regeiorgan is also still available as an integrated damping device.
  • the housing is constructed from a lower part and an upper part, wherein the lower part has the connection piece and the connection holes and is non-positively or positively arranged in the upper part of the housing, wherein the core-oriented part of the lower part is provided a bearing bush for the armature and in the usual bore of the connecting piece a bearing bush for the Regeiorgan is provided.
  • the Regeiorgan is designed as a piston element, it is easily possible to seal the connection to the consumer against the connection to the controlled variable.
  • a particularly easy-to-install pressure control valve is provided in that the armature and the control element are made in one piece, wherein the Ventilgiied and the Regeiorgan by a reduced diameter connecting body, which is designed as a connecting rod, are connected. The difference between the diameter of the bore of the valve seat and the connecting rod then yield the flow area in front of the valve seat, wherein compensate in the closed state, the forces acting on the valve seat and the Regeiorgan forces from the control pressure.
  • the interior is to be acted upon with atmospheric pressure in that the first connection bore is formed above the valve seat and the second connection bore between the valve member and Regeiorgan is formed.
  • the bearing bushing for the armature is set back with respect to the first connection bore, there is a trouble-free flow between a consumer and the tank.
  • the anchor has a transverse groove in the case of a separate anchor or as a transverse bore in the case of a one-piece anchor-Regeforgan- composite and a longitudinal bore, such that in the interior of Druckregelventiis above the anchor atmospheric pressure prevails, the risk of oil leakage to the environment or The risk of damage to the electromagnetic drive due to pressure fluctuations is very low.
  • the lower part is constructed in two parts, wherein the armature is mounted in the first part and the first connection bore is formed, and wherein in the second part of the valve seat and the second connection bore and the connecting piece are formed with the control element.
  • the penetration depth of the second part is adjustable in the first part, such that the stroke of the armature can be adjusted, a fine adjustment of the pressure control valve is possible during assembly. This is possible in a special way if the second part is pressed into the first part.
  • the core may have a pin made of a non-magnetizable material which acts as a stop element for the armature and as a spring seat for a spring, which supports the armature resiliently relative to the core.
  • a further fine adjustment is made possible in that the pin is adjustably arranged in the core.
  • the core has an adjusting bore at the end facing away from the armature, in which an adjusting screw is arranged. It is particularly advantageous if the core has a substantially peripheral recess in the region of the adjusting bore on the side directed towards the coil.
  • FIGURE shows a sectional view of a preferred embodiment of a pressure control valve, wherein the integration into a Oil circuit to illustrate the operation is shown schematically.
  • the Druckregeiventäl 1 comprises a housing 2, which is essentially composed of an upper part 3 and a lower part 4.
  • the upper part 3 has an electromagnetic drive unit 5 which acts on an armature 7 which is arranged so as to be axially displaceable in a bearing 6.
  • the electromagnetic drive 5 consists essentially of a coil 8, a core 9 and a flux guide 10, which consists of a return plate 11 and a yoke 12.
  • the executed in plastic housing 2 also has a plug 13 for connection to a known and not shown Steuerungsmodui on.
  • the electromagnetic drive 5 acts on the armature 7, which has a Ventiigfied 14 at its end facing away from the core 9.
  • the valve member 14 is connected in the present case via a connecting rod 15 with a control member 16 and tapered to ensure a U-shaped system.
  • the armature 7, the valve member 14, the connecting rod 15 and the Regeiorgan 16 are made in one piece in the present case.
  • the armature 7 is biased by a spring 17 relative to the core 9 in a closed position.
  • the spring 17 is guided by a pin 18 which is adjustably arranged in the core 9 during assembly. At the same time, this pin 18 serves as the upper stop element for the armature 7.
  • an adjusting screw 19 is provided, which is arranged in a Justierbohrung 20 and on the fine adjustment of the electromagnetic drive 5 is possible to the effect that the course of the magnetic field lines can be affliusst .
  • a recess 21 is furthermore provided which is intended to prevent scattering of the magnetic field lines in the region of the adjusting screw 19 and accordingly enables a linear fine adjustment during assembly.
  • the lower part 4 is constructed in two parts in the present embodiment, wherein in the first part 23, the bearing bush 6 is set back for the armature 7 with respect to a connection bore 24. It should be clear that with the term connection hole also a number of holes in the lower part 4 may be included.
  • connection bore 24 leads to a non-illustrated tank having an atmospheric pressure p 0 .
  • a valve seat 25 is provided, which cooperates with the valve member 14. Instead of the conical Ausbiidung of the valve member 14 and the valve seat 25 may be carried out accordingly. Due to the fact that the bearing 6 for the armature 7 is set back in relation to the connection bore 24 in the part 23 of the lower part 4, a trouble-free flow is ensured when opening the pressure control valve 1 to the tank.
  • the valve seat 25 is formed in the present case by the second part 26, which also has the connecting piece 38, the lower part 4. The second part 26 is pressed into the first part 23, whereby the stroke of the armature 7 is adjustable during assembly.
  • the control pressure p 2 of the consumer 28 which is for example a controllable ⁇ fpumpe.
  • a control bore 39 is provided, which has a second bearing bush 29, in which the control member 16, which is formed in the present case as a piston is mounted friction.
  • the control pressure p 1 which represents the engine oil pressure in the present case.
  • the anchor has in the present embodiment, a transverse bore 30 and a longitudinal bore 31 which ensure a connection of an interior 32 with the atmospheric pressure Po.
  • a transverse bore 30 and a longitudinal bore 31 which ensure a connection of an interior 32 with the atmospheric pressure Po.
  • the pressure control valve 1 now works as follows.
  • a known motor oil pump 28 which is designed as a controllable F Schogeizellenpumpe to be controlled.
  • the per se known vane pump 28 delivers the engine oil to the engine 33 whereby the excess oil is returned to the tank at the atmospheric pressure pO.
  • the pumped engine oil has the pressure pi.
  • a maximum delivery volume is achieved with maximum eccentricity of the axis of rotation of the aviation pump 28, wherein the eccentricity is accomplished by a displacement of a slide 34 in the aviation cell pump 28.
  • a minimal delivery volume is achieved with a centric arrangement of the axis of rotation.
  • the slide 34 cooperates with 2 control chambers 35, 36, wherein in both control chambers 35, 36, the pressure pi is applied.
  • the abutment surface of the slide 34 is designed to be larger, so that when the pressure control valve 1 is switched off, the slide 34 causes the greatest eccentricity and thus the highest delivery volume (Faii - Safe function). If a reduction of the eccentricity and thus a reduction in the delivery volume of the fly-shaft pump 28 are desired, the pressure-regulating valve 1 is actuated and the pressure in the control chamber 36 is correspondingly reduced. Accordingly, the oil is at the pressure p 2 at the second connection hole 27.
  • the pressure control valve 1 can be closed; that is by a nozzle 37 and the different area ratio of the contact surfaces of the slide 34 ensures that a rapid displacement of the axis of rotation of the vane pump 28 takes place to the eccentric position.
  • the engine oil pressure pi is applied, whereby the engine oil pressure is regulated even when the pressure regulating valve 1 is not switched on, if it is too high.
  • the pressure control valve 1 is used to dissipate at a high delivery volume resulting from leaks and movement gaps accumulating oil leakage.

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Safety Valves (AREA)

Abstract

L'invention concerne un modulateur de pression pourvu d'un carter, qui présente une bobine enroulée sur un support de bobine, un induit pouvant se déplacer axialement dans un logement, un noyau et un dispositif de guidage de flux. Un raccord de pression de commande, un raccord de pression de régulation et un raccord de reflux sont agencés dans ledit carter, le raccord de pression de commande pouvant être obturé par l'induit, le carter étant réalisé sensiblement en deux parties, une partie inférieure présentant un manchon de raccordement ainsi qu'un orifice de raccordement et étant assemblée à force ou par complémentarité de forme avec une partie supérieure du carter. Une douille-palier destinée à l'induit est placée dans la partie du manchon de raccordement orientée vers le noyau et une douille de butée destinée à l'induit est agencée dans la partie opposée du manchon de raccordement.
EP11723417.9A 2010-06-25 2011-05-24 Soupape de régulation de pression à régulation continue Ceased EP2585888A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010025175 DE102010025175A1 (de) 2010-06-25 2010-06-25 Stufenlos regelbares Druckregelventil
PCT/EP2011/058410 WO2011160910A1 (fr) 2010-06-25 2011-05-24 Soupape de régulation de pression à régulation continue

Publications (1)

Publication Number Publication Date
EP2585888A1 true EP2585888A1 (fr) 2013-05-01

Family

ID=44474954

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11723417.9A Ceased EP2585888A1 (fr) 2010-06-25 2011-05-24 Soupape de régulation de pression à régulation continue

Country Status (5)

Country Link
US (1) US9062570B2 (fr)
EP (1) EP2585888A1 (fr)
JP (1) JP5921537B2 (fr)
DE (1) DE102010025175A1 (fr)
WO (1) WO2011160910A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010055025A1 (de) * 2010-12-17 2012-06-21 Pierburg Gmbh Elektromagnetventil
DE102012109094A1 (de) * 2012-09-26 2014-03-27 Pierburg Gmbh Regelventilvorrichtung für einen Hydraulikkreislauf sowie Verfahren zur Regelung des Förderdrucks einer variablen Ölpumpe
DE102012024851A1 (de) * 2012-12-19 2014-06-26 Erwin Weh Druckregelventil
DE102013207863A1 (de) * 2013-04-30 2014-10-30 Mahle International Gmbh Vorrichtung zur Steuerung eines Gaswechselventils einer Brennkraftmaschine
CN105697966B (zh) * 2016-03-24 2018-12-18 上海交通大学 应用于tbm主梁鞍架导轨的润滑系统及其建立方法
CN106151144A (zh) * 2016-08-11 2016-11-23 张广 一种基于磁流变效应的单向阀
CN108591584B (zh) * 2018-05-31 2024-04-12 温州大学 一种控制转阀的压电驱动装置

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Also Published As

Publication number Publication date
DE102010025175A1 (de) 2011-12-29
US20130112293A1 (en) 2013-05-09
WO2011160910A1 (fr) 2011-12-29
JP5921537B2 (ja) 2016-05-24
JP2013531767A (ja) 2013-08-08
US9062570B2 (en) 2015-06-23

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