WO2020114560A1 - Soupape et dispositif de régulation de la pression d'un fluide dans une transmission de véhicule muni d'une soupape - Google Patents

Soupape et dispositif de régulation de la pression d'un fluide dans une transmission de véhicule muni d'une soupape Download PDF

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Publication number
WO2020114560A1
WO2020114560A1 PCT/DE2019/101045 DE2019101045W WO2020114560A1 WO 2020114560 A1 WO2020114560 A1 WO 2020114560A1 DE 2019101045 W DE2019101045 W DE 2019101045W WO 2020114560 A1 WO2020114560 A1 WO 2020114560A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
valve
opening
valve housing
throttle
Prior art date
Application number
PCT/DE2019/101045
Other languages
German (de)
English (en)
Inventor
Lukas Kuhn
Horst Hartmann
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2020114560A1 publication Critical patent/WO2020114560A1/fr

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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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0209—Check valves or pivoted valves
    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0433—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with vibration preventing means
    • 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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0466—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with a special seating surface

Definitions

  • the invention relates to a valve with a valve housing, at least one piston, at least one support element and at least one spring, with the features:
  • the piston and the valve housing are arranged coaxially to one another on an imaginary valve axis, the valve axis being axially aligned in a first axial direction and in a second axial direction opposite to the first axial direction,
  • the piston is axially movable in the valve housing against spring forces of the spring, the spring being supported at least in the first axial direction on the support element and in the second axial direction on the piston,
  • the support element is supported on the valve housing
  • the piston has a piston crown and a piston skirt
  • valve housing is provided with a fluid-permeable first opening, which can be closed by the piston crown,
  • the invention also relates to a device for regulating pressures of a fluid in a vehicle transmission with egg nem such valve.
  • a valve of the type is disclosed in EP 1 382 893 A1.
  • This valve is a pressure relief valve in a hydraulic circuit. It consists of a valve housing, a piston with a ball, a spring and a support element. In a closed position, the ball and piston are biased by the spring in the direction of the front opening of the Ventilge housing.
  • the spring designed as a compression spring is supported axially in one direction on the piston head and axially in the other direction on a disk-shaped support element and is also guided radially there.
  • the support element is anchored positively and non-positively in the valve housing.
  • the ball closes the opening in the closed position.
  • the valve sits in a housing with channels. The opening at the front of the solid valve housing flows into a supply channel with a high pressure level.
  • the outlet of the valve is provided on the rear of the valve housing at an opening axially opposite the end face and is connected to a discharge channel. higher pressure levels fluidically connected.
  • the valve opens when the pressure in the supply channel exceeds a predetermined limit.
  • One or more throttle openings in the support element regulate the flow rate of the hydraulic fluid through the valve into the discharge channel and thus the desired pressure reduction in the supply channel, so that the support element also fulfills the function of a throttle plate.
  • the object of the invention is to provide a valve and a device for regulating pressures with such a valve, which are simple to manufacture inexpensively and can be used variably.
  • a throttle disk is arranged as a separate component between the piston and the support element.
  • the advantage of this invention results from the fact that a valve with a throttle disk which is formed separately from the throttle bores in the support element according to the known prior art can be adjusted more variably to control or opening pressures.
  • the throttle plate which is either a component made of a metal or plastic, can be mass-produced but also in smaller lots inexpensively and with very precisely designed throttle openings or dimensions.
  • the flow cross section of the throttle openings can be changed with simple means and the damping of the axial movement of the piston or of axial vibrations of the piston can be adjusted.
  • the other components of the valve can remain unchanged.
  • the support element can be made as a simple stamped part, for example from sheet metal, and thereby for example from spring steel, regardless of the requirements for the accuracy of a throttle disc. Any deformation of the support element during pressing or crimping has no influence on the accuracy of the throttle openings.
  • the throttle opening is designed as at least one between the valve housing and the throttle disk for the fluid through a casual throttle gap.
  • the cross section of the throttle opening or throttle gap which is preferably an annular gap, is advantageous over the diameter of the throttle sel disks predetermined and essentially results from the difference between the inner diameter of the valve housing and the outer diameter of the throttle plate.
  • the throttle plate is arranged according to the invention between one end of the spring and the support element and is preferably clamped there axially between the Fe formed as a compression spring and the support element under the effect of the spring preload.
  • an embodiment of the invention provides that the throttle plate is attached to the support element.
  • This solution can be advantageously configured in that the support element has a through hole in the center, in which a fastening means of the pressure disk preferably engages in a form-fitting manner and the pressure disk is centered in a simple manner in the disk-shaped support element.
  • An embodiment of the invention provides that the spring lies axially on the throttle disk and is guided and centered radially in the valve housing via the throttle disk.
  • the invention also provides a device for regulating pressures of a flow in a vehicle transmission.
  • the device is formed from a section of a transmission component, from at least a first channel and a second channel, and from the valve.
  • the valve is a pressure compensation valve.
  • the channels run in a Ge housing or a component of the vehicle transmission.
  • the first channel leads to the first opening in the section of the transmission component in which the pressure compensation valve is located.
  • the pressure compensating valve has a fluid-permeable second opening in the valve housing, which opens into the second channel.
  • the second opening is oriented transversely to the axial directions and can be closed by the piston skirt.
  • a further embodiment of the invention provides that the piston is guided against the spring forces of the spring from a closed position into an open position axially distant from the closed position in an axially movable manner in the valve housing.
  • the first opening is closed by means of the piston.
  • the first opening is released by the piston, so that in the open position via the first opening and the second opening a passage for the fluid free through the valve housing is formed.
  • FIG. 1 shows an overall view of a pressure compensation valve 1 according to the invention
  • FIG. 2 shows a longitudinal section through the pressure compensation valve 1 or through a section of a device 30 for regulating pressures of a fluid in an otherwise not shown vehicle transmission along the valve axis 6 of the pressure compensation valve 1, the piston 3 being in a closed position I.
  • FIG. 3 the rear view of the pressure compensation valve 1 according to FIG. 1,
  • FIG. 4 shows the longitudinal section according to FIG. 2 through the pressure compensation valve 1 or the device 30 along the valve axis 6 of the pressure compensation valve 1, the piston 3, however, being in an open position II and
  • FIG. 5 shows an enlarged and not to scale representation of the detail X of the valve 20 from FIG. 2.
  • the pressure compensation valve 1 has a valve housing 2, a piston 3, a support element 4 and a spring 5.
  • the valve housing 2 and the piston 3 are essentially formed in a rotationally symmetrical manner and arranged coaxially with a valve axis 6.
  • the valve axis 6 is aligned axially.
  • the piston 3 is axially movable but radially guided with little radial play in the valve housing 2 and provided with a piston skirt 9 and a piston crown 7.
  • the piston skirt 9 is hollow-cylindrical and is aligned coaxially with the valve axis 6 and extends from the piston head 7 in the direction of the support element 4.
  • the spring 5 is a compression spring and axially in one direction on the piston crown 7 of the piston 3 and in the other axial direction on the throttle plate 32 on the support element 4 so that the spring 5 axially between the piston crown 7 and the support element 4 is clamped.
  • the support element 4 is seated at one end 19 of the valve housing 2.
  • the throttle disk 32 is arranged as a separate component between the piston 3 and the support element 4.
  • the support element 4 engages with the projections 28 in a circumferential groove 21 of the valve housing 2 and is firmly supported there.
  • the support member 4 has a disc-shaped base 23 from which the projections 28 slightly inclined to the valve axis 6 in the circumferential groove 21. Between the projections 28 of the support member 4 are formed for fluid-permeable tra peziform gaps 16. In addition, the support member 4 has a central through hole 22.
  • the throttle disc 32 is provided with a flat base body 24 which lies flat against the base 23.
  • a closure 25, which determines the center of the throttle disk, is located in the center of the throttle disk 32. In the illustration shown with FIG. 5, the closure 25 is designed like a stopper and sits in the through hole 22, as a result of which it is closed impervious to fluid.
  • the closure 25 is provided with at least one holding means 26, by means of which the throttle disk 32 is held on the support element 4.
  • the throttle plate 32 is made of a metal, preferably sheet steel.
  • the holding means 26 is a collar made of plastically displaced metal.
  • the throttle plate can also be formed from plastic and the collar can alternatively also be formed by individual snap hooks 26.
  • the outer diameter of the throttle disk 32 is smaller than the inner diameter of the Ventilge housing 2, so that an annular gap 34 is formed between the disk and the inner wall of the valve housing.
  • the throttle disk 32 extends radially in the direction of the valve housing 2 such that the trapezoidal gaps 16 are at least partially covered from the center and are formed in the form of throttle gaps for the fluid-permeable throttle openings 33.
  • the throttle gaps are in the circumferential direction from the edges each Weil two projections 28 and in the radial direction towards the center by the throttle disc 32 and outwardly through the valve housing 2.
  • the sleeve-shaped valve housing 2 is provided with a flow-permeable first opening 8 and on its sleeve jacket 14 with a two-th opening 10.
  • the first opening is formed on the head side of the pressure compensation valve 1 on the valve housing 2, arranged coaxially to the valve axis 6 and penetrated perpendicularly by the valve axis 6.
  • the second opening 10 is oriented transversely to the first opening 8, that is to say that the second opening 10 extends at a radial distance from the valve axis 6 in the axial direction.
  • the central axis 27 of the opening 10 extends in the radial direction perpendicular to the valve axis 6.
  • the valve seat 17 preferably has a concave inwardly curved ka lotten-shaped surface which corresponds to a convex annular surface 29 of the piston 3.
  • the piston crown 7 is axially adjoined by a transition section 11, at which the piston base 7 merges into the piston skirt 9 and the piston skirt 9 into the piston crown 7.
  • the transition section 1 1 is formed in the form of a concave groove and connects the piston crown 7 to the piston skirt 9.
  • the annular surface 29 joins the surface 31 of the piston crown 7 and leads into the transition segment 11.
  • the surface 31 can alternatively be a flat circular surface, but it can also be a convex or concave or otherwise three-dimensionally structured surface.
  • the valve housing 2 and the Kol ben 3 are sleeve-shaped components, which are preferably cold-formed from flat sheet material, that is, drawn and punched.
  • the device 30 for regulating pressures of a fluid in a vehicle transmission is formed from at least a portion of a transmission component 35, a first channel 36, a second channel 37 and the pressure compensation valve 1.
  • the pressure compensation valve 1 is seated in a through bore 38, the diameter of which is equal to that of the first channel 36 or larger or smaller than the first channel 36.
  • the first channel 36 leads to the first opening 8.
  • the second opening 10 is aligned to the second channel 37 so that it opens into the second channel 37.
  • FIG. 2 The piston 3 is biased axially against the valve seat 17 in the closed position I by the action of the spring 5 and closes the first opening 8 with the piston head 7 in this position.
  • the closed position I is accordingly the position of the piston head 7 to the valve seat 17th in the closed state of the valve 3.
  • the annular surface 29 bears against the valve seat 17.
  • the second opening 10 is largely closed by the piston jacket 9, but a gap-shaped passage opening 12 which is permeable to fluid remains.
  • the gap-shaped passage opening 12 is limited by a jacket section of the piston skirt 9 or by a transition section 11 of the piston 3 and an edge of the valve housing 2 at the second opening 10 Publ.
  • the open cross section axially opposite the first opening 8 at the open end 19 of the valve housing 2 is also closed by the piston 3.
  • An annular gap (leakage gap) formed between the piston skirt 9 and the valve housing 2 due to the smaller radial clearance is not taken into account.
  • a Annular channel 13 is formed between the piston 3 and the valve housing 2, which is delimited by the transition section 11 on the piston 3 and a section of the valve housing 2.
  • the section 15 extends from the valve seat 17 to the sleeve casing of the valve housing 2.
  • the annular channel 13 is open at the gap-shaped through opening 12 and is otherwise closed all round.
  • the force exerted on the surface 31 of the piston crown by the pressure of a fluid in the first channel 36 is less than or equal to a counterforce acting on the rear side of the piston crown 7 in the interior of the pressure compensation valve 1.
  • the counterforce is a result of the force generated by a counterpressure inside the pressure compensation valve 1 on the rear of the piston crown 7 and primarily the spring force exerted on the rear of the piston crown 7 of the spring 5 clamped between the piston crown 7 and the support element 4.
  • FIG. 4 - If the pressure in the first channel 36 increases so much that the surface force 31 on the piston head 7 exceeds the counterforce, the piston 3 moves axially in the direction of the support element 4 in the open position II and releases the valve seat 17.
  • fluid located on the rear of the piston head 7 is displaced from the interior of the pressure compensation valve 1 via the throttle openings 33 and the axial movement or possible axial oscillating movements of the piston 3 are damped.
  • the fluid flows through a passage 18 thus opened, via the first opening 8, through the interior of the pressure compensation valve 1, via the second opening 10 into the second channel 37.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)

Abstract

L'invention concerne une soupape (20) comportant un carter (2) de soupape, au moins un piston (3), au moins un élément d'appui (4) et au moins un ressort (5), et présentant les caractéristiques suivantes : - le piston (3) et le carter (2) de soupape sont agencés coaxialement l'un par rapport à l'autre sur un axe (6) imaginaire de la soupape, l'axe (6) de la soupape étant orienté axialement dans une première direction axiale ainsi que dans une seconde direction axiale opposée à la première direction axiale, - le piston (3) est logé dans le carter (2) de soupape mobile axialement à l'encontre des forces du ressort (5), le ressort (5) prenant appui au moins dans la première direction axiale sur l'élément d'appui (4) et dans la seconde direction axiale sur le piston (3), - l'élément d'appui (4) prend appui sur le carter (2) de soupape, - le piston (3) présente un fond (7) de piston et une jupe (9) de piston, - le carter (2) de soupape est muni d'une première ouverture (8) laissant passer le fluide, qui peut être fermée par le fond (7) de piston, - le piston (3) peut être déplacé dans le carter (2) de soupape par la jupe (9) de piston axialement par rapport au ressort (5) en direction de l'élément d'appui (4), - le carter (2) de soupape présente à une extrémité (19) éloignée axialement de la première ouverture (8) au moins une ouverture d'étranglement laissant passer le fluide, qui est délimitée par un disque d'étranglement (32).
PCT/DE2019/101045 2018-12-06 2019-12-05 Soupape et dispositif de régulation de la pression d'un fluide dans une transmission de véhicule muni d'une soupape WO2020114560A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018131098.6A DE102018131098A1 (de) 2018-12-06 2018-12-06 Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels in einem Fahrzeuggetriebe mit einem Ventil
DE102018131098.6 2018-12-06

Publications (1)

Publication Number Publication Date
WO2020114560A1 true WO2020114560A1 (fr) 2020-06-11

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PCT/DE2019/101045 WO2020114560A1 (fr) 2018-12-06 2019-12-05 Soupape et dispositif de régulation de la pression d'un fluide dans une transmission de véhicule muni d'une soupape

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DE (1) DE102018131098A1 (fr)
WO (1) WO2020114560A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019120225A1 (de) * 2019-07-26 2021-01-28 Schaeffler Technologies AG & Co. KG Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels mit dem Ventil sowie Vorrichtung zur Sicherung des Ventils in dem Getriebebauteil
DE102021107639A1 (de) 2021-03-26 2022-09-29 Mann+Hummel Gmbh Wasserabscheider mit einem Drosselelement, Verwendung eines Wasserabscheiders und Brennstoffzellensystem mit einem Wasserabscheider

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1810550A1 (de) * 1968-11-23 1970-06-04 Ernst Heinkel Ag Kegelsitzventil
DE3120606A1 (de) * 1981-05-23 1983-07-28 Bayerische Motoren Werke AG, 8000 München Ventil zur druckbegrenzung in hydraulischen anlagen
DE19505129A1 (de) * 1995-02-16 1996-08-22 Rexroth Mannesmann Gmbh Vorgesteuertes Druckbegrenzungsventil
FR2817014A1 (fr) * 2000-11-17 2002-05-24 Montage Auto Camions Soc D Soupape de degazage
EP1382893A1 (fr) 2002-07-12 2004-01-21 TRW Automotive Pumps S.r.l. Soupape anti-retour pour circuits hydrauliques
DE102008057393A1 (de) * 2008-11-14 2010-05-20 Schaeffler Kg Rückschlagventil in Patronenbauform
DE102009053612A1 (de) * 2009-11-17 2011-05-19 Robert Bosch Gmbh Vorgesteuertes Druckbegrenzungsventil
ITRE20110027A1 (it) * 2011-04-19 2012-10-20 Renato Besacchi Valvola di non ritorno per oli e fluidi in genere.
US20140311596A1 (en) * 2012-01-05 2014-10-23 Kodaco Co., Ltd. Check valve for variable capacity compressor of vehicle
CN204153230U (zh) * 2014-08-12 2015-02-11 常州福磊石材有限公司 防堵塞单向节流阀
DE102014213751A1 (de) * 2014-05-23 2015-11-26 Continental Teves Ag & Co. Ohg Ventilbaugruppe

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1810550A1 (de) * 1968-11-23 1970-06-04 Ernst Heinkel Ag Kegelsitzventil
DE3120606A1 (de) * 1981-05-23 1983-07-28 Bayerische Motoren Werke AG, 8000 München Ventil zur druckbegrenzung in hydraulischen anlagen
DE19505129A1 (de) * 1995-02-16 1996-08-22 Rexroth Mannesmann Gmbh Vorgesteuertes Druckbegrenzungsventil
FR2817014A1 (fr) * 2000-11-17 2002-05-24 Montage Auto Camions Soc D Soupape de degazage
EP1382893A1 (fr) 2002-07-12 2004-01-21 TRW Automotive Pumps S.r.l. Soupape anti-retour pour circuits hydrauliques
DE102008057393A1 (de) * 2008-11-14 2010-05-20 Schaeffler Kg Rückschlagventil in Patronenbauform
DE102009053612A1 (de) * 2009-11-17 2011-05-19 Robert Bosch Gmbh Vorgesteuertes Druckbegrenzungsventil
ITRE20110027A1 (it) * 2011-04-19 2012-10-20 Renato Besacchi Valvola di non ritorno per oli e fluidi in genere.
US20140311596A1 (en) * 2012-01-05 2014-10-23 Kodaco Co., Ltd. Check valve for variable capacity compressor of vehicle
DE102014213751A1 (de) * 2014-05-23 2015-11-26 Continental Teves Ag & Co. Ohg Ventilbaugruppe
CN204153230U (zh) * 2014-08-12 2015-02-11 常州福磊石材有限公司 防堵塞单向节流阀

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