EP4172520A1 - Soupape et procédé de régulation d'un milieu d'écoulement à l'aide de la soupape - Google Patents

Soupape et procédé de régulation d'un milieu d'écoulement à l'aide de la soupape

Info

Publication number
EP4172520A1
EP4172520A1 EP21739551.6A EP21739551A EP4172520A1 EP 4172520 A1 EP4172520 A1 EP 4172520A1 EP 21739551 A EP21739551 A EP 21739551A EP 4172520 A1 EP4172520 A1 EP 4172520A1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
switching mode
opening
housing
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Withdrawn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
EP21739551.6A
Other languages
German (de)
English (en)
Inventor
Lukas Kuhn
Horst Hartmann
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and 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 and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP4172520A1 publication Critical patent/EP4172520A1/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Withdrawn legal-status Critical Current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
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/025—Check valves with guided rigid valve members the valve being loaded by a spring
    • 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

Definitions

  • the invention relates to a valve having at least a valve housing and a piston and a method for controlling a fluid with the valve.
  • the valve has a housing with an opening at the end and an opening (transverse opening) which is radially remote from the valve axis.
  • the piston is designed in two stages and is axially movably guided on the inner wall of the valve housing.
  • One piston step is smaller in diameter than the other.
  • a connecting section of the piston that is almost conical in relation to the valve axis and with which the difference in diameter is bridged is formed between the piston stages.
  • a compression spring is clamped axially between the piston head and a support element. The support element is firmly seated on the valve housing. The valve works in two switching modes.
  • the piston has a piston surface which, in a first switching mode of the valve, radially covers the opening cross section of the end-side opening in the valve housing from the inside.
  • an annular further piston surface which has the same function as a closing edge, lies against a sealing seat of the valve housing in a sealing manner. Consequently, in the first switching mode, the front opening of the valve is closed by the piston.
  • an annular space is formed between the connecting section of the piston and an end section of the valve housing and a hollow cylindrical section of the valve housing. This annular space can be changed in its axial extent as a function of the piston stroke and has the front opening as an inlet and the transverse opening as an outlet.
  • a fluid acting with pressure on the piston surface exerts axial forces on the piston, through which the spring forces of the compression spring are overcome and a piston stroke is generated.
  • the piston lifts from the front opening or from the valve seat.
  • the fluid flows from the front opening towards the transverse opening through a flow channel which is formed by the annular space.
  • the object of the invention is to create a valve with improved valve characteristics.
  • the valve according to the invention has at least one valve housing and one piston.
  • the piston is axially longitudinally movably guided along a valve axis in the valve housing.
  • the mutually opposite axial directions are accordingly defined as the longitudinal directions in which the piston is movably guided in the valve housing. Is radial or the radial directions are thus oriented transversely to the valve axis.
  • valve is part of a device with which pressure, flow rate and flow direction of fluids are controlled and which has the following basic structure:
  • the valve sits in a housing.
  • the housing is, for example, the housing of a vehicle transmission, alternatively a machine part of the vehicle transmission, such as a shaft or a hub.
  • a flow channel leads to an opening at the end of the valve housing.
  • the front opening opens into a chamber.
  • At least one transverse opening is formed in the valve housing. The transverse opening also opens into a flow channel or into a chamber.
  • the valve has the following features:
  • the piston is a cup-shaped hollow cylindrical component and has two steps which are defined by diameters that differ from one another.
  • the first stage is smaller in diameter than the second stage.
  • the piston is preferably formed from sheet metal, but alternatively it is also solidly pressed or made from cast material. It is guided in an axially movable manner on the inside of the inner cylindrical jacket surface of the valve housing via an outer cylindrical area of a lateral surface of the second stage.
  • the jacket surface can cover the entire second piston stage, but alternatively it can also be only an outer cylindrical section of the second piston stage.
  • a first piston surface is formed on the face of the piston head.
  • the first piston surface is adjoined radially on the outside by a second piston surface.
  • the second piston surface is followed axially by an outer cylindrical first jacket surface of the first piston stage.
  • a third piston surface is formed radially between the jacket surface of the first piston stage and a control edge of the piston.
  • the control edge of the piston closes off the third piston surface radially on the outside and is a body edge which is slidably guided along the inner circumferential surface of the valve housing in a sealing manner.
  • An outer cylindrical second jacket surface of the second piston stage adjoins the control edge axially.
  • the valve seat is either formed separately from the valve housing and supported or fastened to the valve housing or is formed directly on the material of the valve housing.
  • the valve housing is preferably a formed part made of sheet steel.
  • the valve housing is generally a hollow cylindrical component, the hollow cylinder of which is provided with a bottom at one end.
  • the bottom has the front opening.
  • At least one second opening (transverse opening) is formed in the hollow cylinder.
  • the hollow cylinder can also have a plurality of second openings that are circumferentially spaced from one another and / or axially offset from one another.
  • the piston is acted upon by at least one spring, preferably a compression spring.
  • at least one compression spring is that compression springs are available as mass-produced goods in a wide variety of designs at low cost and thus the working areas of the valve can be individually adapted to different requirements, for example by selecting one or more springs with suitable spring forces (closing force or control forces) be able. Such adjustments and changes to the spring are possible even if the design of the valve is otherwise the same.
  • the valve works as follows:
  • the valve or device There are three switching modes of the valve or device according to the invention.
  • the first switching mode the valve is closed.
  • the piston rests against the valve seat in a sealing manner. There is no passage for fluid between the face opening and the transverse opening.
  • the second switching mode the front opening of the valve is released by the piston and fluid can flow into the interior of the valve.
  • the control edge of the piston is still in sealing contact with the valve housing, so that there is still no passage between the first and second openings in the second switching mode.
  • the control edge of the piston lies axially between the closing edge of the second opening of the valve housing and the valve seat in a sealing manner a section of the valve housing extending between the valve seat and the closing edge.
  • the piston is retracted axially so far that the control edge releases part of the transverse opening.
  • the fluid can flow in the device from a flow channel via the front opening and a flow chamber formed in the valve and from there via the second opening into a further flow channel or back to the first opening and from there into the other flow channel.
  • the valve is closed, i. that is, the first opening is closed by the piston.
  • a first piston surface of the piston covers the first opening from the inside with a view from the flow channel onto the first opening in the valve housing and at the same time a second piston surface rests against a valve seat under the action of a closing force.
  • the pressure of the fluid acting through the front opening on the first piston surface is either zero or so small that the axial actuating force acting on the piston surface is less than a closing force with which the piston sealingly counteracts, for example by means of a spring the valve seat is biased.
  • control force acting on the piston can also be generated by a fluid or, as a preferred embodiment of the invention provides, is preferably generated by means of the spring characteristic (s) of one or more compression springs inserted into the valve.
  • the second opening is completely closed by an outer jacket surface (second jacket surface) of the second piston stage.
  • an annular space or a closed annular chamber is delimited by a section of the inner jacket surface of the valve housing, the first jacket surface of the first piston stage and by the third piston surface.
  • the control edge of the piston is positioned axially between the end face of the valve and the second opening. More precisely, the control edge of the piston is positioned axially between a closing edge formed on the first opening of the valve housing and the end face of the valve housing and lies there against a section of the valve housing in a radially sealing manner.
  • Radial sealing is alternatively defined in the context of the invention as pressure-tight or partially permeable via a leakage gap.
  • An outer cylindrical casing section of the second piston stage axially adjoining the control edge is radially sealing on an inner cylindrical casing section of the Valve housing out.
  • the inner cylindrical jacket section of the valve housing extends axially between the section of the inner jacket surface of the valve housing that delimits the annular chamber and the closing edge formed on the second opening.
  • the closing edge is formed on the edge of the second opening, or is a section of this edge and delimits the second opening in the direction of the end face of the valve in radial contact with the piston.
  • a passage through the valve is therefore not yet open.
  • the actuation force which is caused by the pressure of the fluid on the first piston surface at the front opening, generates an opening force.
  • the opening force is greater than the closing force of the piston. This causes the piston to lift off the valve seat.
  • this opening force causes an axial stroke of the piston, but not yet the final opening of the valve.
  • the piston initially only lifts axially from the valve seat.
  • the pressure of the fluid “fills” the annular chamber and also acts on the third piston area. The total piston area on which the pressure of the fluid acts is increased.
  • the control edge of the piston was pushed axially over the closing edge of the second opening (transverse opening) under the action of the control forces, so that a second opening cross-section is formed at the second opening, delimited by the control edge and the closing edge.
  • a free passage from the flow channel via the frontal first opening and from there into the annular chamber, which is now designed as a flow chamber, and from there through the second opening is released.
  • the fluid can flow between the flow channels until a pressure drop in the pressure medium causes a stroke reversal and thus the displacement of the piston in the direction of the valve seat and the control edge moves over the closing edge again.
  • the pressure of the pressure medium initially acts again on the piston surface made up of the three piston surfaces, and the resulting counterforce dampens the movement of the piston in the direction of the valve seat.
  • the size of the control forces on the piston is always close to the closing forces of the spring.
  • the actuating force acting on the piston surface is reduced relatively quickly below the level of the pre-tensioning force (closing force) of the spring by the pressure equalization, so that the piston is guided back against the valve seat by the forces of the spring and the valve again is temporarily closed.
  • the pressure on the piston surface is again so high that the piston lifts slightly from the valve seat again.
  • valve according to the invention in particular the sealing abutment of the control edge of the piston axially between the closing edge of the second opening and the end face of the valve housing or the first opening on an inner cylindrical section of the valve housing, creates a passage for the pressure or fluid prevented by the valve in the second switching mode because the second opening is still closed by the jacket of the piston in the second switching mode.
  • the piston stroke is greater because the distance between the second opening or the closing edge of the second opening from the valve seat is greater due to the inner cylindrical section.
  • the reaction times of the piston between the first and third mode are increased, which also prevents "fluttering".
  • the effective piston area is first of all enlarged and thus a higher actuation force is generated on the piston.
  • the second switching mode is, so to speak, an intermediate switching mode with which the reaction of the piston to the balancing of the actuating and control forces is dampened and calmed by increased control forces.
  • the total piston area in the second switching mode results from the sum of the first piston area and the third piston area and roughly an outline of the second piston area in any imaginary radial plane in which the third piston area, which is designed as a ring area, and the first piston area, which is designed as a circular area, are also mapped leave.
  • the movement of the piston under the influence of the higher control force is dampened and the undesirable high-frequency oscillations of the piston between the first and second switching mode are avoided.
  • the position of the piston in the valve according to the invention away from the valve seat is maintained even at low pressures due to the increased actuation force due to the larger piston area, under the influence of which the piston on the valve of the previously known prior art would already strike the valve seat again. The valve reacts more sensitively.
  • the valve opens a passage for the fluid only in the additional third switching mode when the control edge of the piston releases a slot of the second opening that is delimited by the closing edge of the second opening and the control edge of the piston. Only now does the pressure on the piston decrease rapidly and the piston moves back axially in the direction of the valve seat. The control edge moves axially over the closing edge so that the second opening is closed again. However, the piston cannot hit the valve seat because the pressure of the fluid now acts immediately on the three piston surfaces and the actuating force on the piston comes close to the closing force of the spring (s) even with a slight build-up of pressure. The movement of the piston back to the valve seat is dampened.
  • first piston surface and at least one circular ring surface of the third piston surface are planar surfaces lying in parallel radial planes and thus parallel to one another, that is, the first piston surface is preferably a circular surface and the third piston surface is preferably a circular ring surface.
  • first piston surface is preferably a circular surface
  • the third piston surface is preferably a circular ring surface.
  • one or both piston surfaces are axially curved convexly or concavely in one or the other direction.
  • the reaction behavior of the piston and thus of the valve can advantageously be set via the design of the piston surface, but self-cleaning of the valve from residues / deposits of the fluid can also be positively influenced.
  • the third piston surface has two sections.
  • the one section which radially adjoins the first jacket surface of the first piston stage is the circular ring surface.
  • the other section, which extends radially outward from the circular ring surface to the control edge, has a curved or straight course inclined to the valve axis in any longitudinal section viewed along the valve axis.
  • the geometry of the second section is preferably described by the surface area of a truncated cone. Such a measure prepares a sharp transition to the control edge, which also keeps the contact between the inner circumferential surface of the valve housing and the piston free of deposits when the piston moves.
  • FIG. 1 - a valve 1 viewed in a longitudinal section along the valve axis 5 of the valve 1,
  • FIG. 2 - a section of the valve 1 shown in Figure 1 with the position of the piston 3 in a first switching mode of the valve 1,
  • FIG. 4 the detail according to FIG. 3, but with the position of the piston 3 in a third switching mode of the valve 1.
  • FIG. 1 - The valve 1 consists of a valve housing 2, a piston 3, a spring 4, a seal 31 and a support element 27.
  • the piston 3 is guided radially in the valve housing 2 and is pressed axially against a valve seat 14 with the spring 4.
  • the spring 4 dips axially into the piston 3 and rests against the bottom of the piston 3 there.
  • the seal 31 sits on a neck 32 of the valve housing 2 which surrounds a first opening 6.
  • the seal 31 is provided with a reinforcement 33 which carries and reinforces a sealing lip 34.
  • the valve housing 2 is designed in two stages and is provided with a first housing stage 25 and a second housing stage 26.
  • the housing steps 25 and 26 are designed essentially as a hollow cylinder.
  • the first housing step 25 is smaller in diameter than the second housing step 26.
  • the first housing step 25 has the first opening 6 on an end face 21.
  • the first opening 6 is surrounded by the neck 32 of the valve housing 2.
  • the first housing stage 25 is also provided with at least two second openings 7, which are designed as transverse openings at a radial distance from the valve axis 5 in the valve housing 2.
  • the illustrated valve housing 2 is a thin-walled formed part made of sheet metal and is provided at an end facing away from the end face 21 with a crimped step, at which the wall thickness of the valve housing 2 is reduced and crimped.
  • the rear edge of the valve housing 2 is slightly bent on the circumferential side radially in the direction of the valve axis 5 due to the flanged step, so that a circumferential groove 29 is formed.
  • the support element 27 is firmly supported in the circumferential groove 29.
  • the spring 4 is a helical spring which is clamped axially between the bottom of the piston 3 and the support element 27.
  • the first opening 6 is followed in the interior of the valve housing 2 by a valve seat 14 embossed in the material of the valve housing 2.
  • the second opening 7 is encircled with an edge 28 and provided on the edge 28 axially towards the end face 21 with a closing edge 16 which is formed there by a section of the edge 28 at the point, but can also be made separately .
  • the piston 3 is a thin-walled and cup-shaped formed part made of sheet metal and has a first piston stage 8 and a second piston stage 9.
  • the bottom of the piston 3 is provided on the side of the first opening 6 with a flat first piston surface 10 designed as a radial circular surface.
  • FIGS. 1 and 2 - The first piston surface 10 is followed radially by a second piston surface 11.
  • the first piston surface 10 is a circular surface which lies flat in an imaginary radial plane abutted perpendicularly from the valve axis 5.
  • the second piston surface 11 is curved, but can alternatively also be formed from one or more surface sections which are provided either with a curved contour and / or the contour of a jacket of a truncated cone.
  • An outer cylindrical first jacket surface 15 is formed on the outside circumferential side of the first piston step 8.
  • the first piston surface 10 ends at the second piston surface 11 and the second piston surface 11 merges radially into the first jacket surface 15 of the first piston step 8.
  • the first jacket surface 15 is followed by a third piston surface 12.
  • the third piston surface 12 merges at a control edge 13 of the piston 3 into an outer cylindrical second jacket surface 24 of the second piston stage 9.
  • a portion of the third piston surface 12 is a flat, circular ring surface 19 located in an imaginary radial plane pierced perpendicularly by the valve axis 5.
  • Another portion 20 of the third piston surface 12 is designed as a lateral surface of a truncated cone.
  • a section of the inner jacket surface 22 of the valve housing 2, the first jacket surface 15 and the third piston surface 12 jointly delimit an annular chamber 23.
  • the valve 1 is in a first switching mode.
  • the piston 3 is in a closed position.
  • the piston 3 is axially pretensioned by the closing forces of the spring 4 with the second piston surface 11 in a sealing manner against the valve seat 14.
  • Figure 2 - first switching mode of the valve 1 - the first piston surface 10 covers the inside of the valve housing 2 the circular surface-shaped first opening cross section 17 of the first opening 6 radially and thus completely closes it.
  • a section of the second jacket surface 24 of the second piston stage 9 rests in a sealing manner on an inner jacket surface 22 of the valve housing 2.
  • the control edge 13 of the piston 3 is positioned axially between the end face 21 of the valve 1 or the valve seat 14 and the closing edge 16.
  • the second jacket surface 24 completely covers the second opening 7 of the valve housing 2 in the axial direction and thus closes it, with the piston 3 in the first switching mode forming a radial seal with an outer cylindrical section of the second jacket surface 24 on one between the annular chamber 23 and the closing edge 16 inner cylindrical portion of the inner circumferential surface 22 rests in a sealing manner and is guided.
  • FIGS. 1 and 2 second switching mode of the valve 1 - the piston 3 was shifted to the right in the picture against the resistance of the spring 4 by the opening pressure of a fluid (not shown) on the first piston surface 10.
  • the opening force lifted the second piston surface 11 from the valve seat 14.
  • the volume of the annular chamber 23 is increased axially by the stroke of the piston 3 compared to the position of the piston 3 in the first switching mode (compare FIGS. 1 and 2).
  • the annular chamber 23 is open with respect to the first opening 6 and freely accessible to the fluid via the opening cross-section 17. The pressure of the fluid acts on the piston surfaces 10, 11 and 12.
  • the control edge 13 of the piston 3 has been moved axially away from the valve seat 14 compared to the first switching mode (see Figures 1 and 2) and is approximately at the level of the closing edge 16, but without to release the second opening 7 already.
  • the second jacket surface 24 still completely covers the second opening 7.
  • the control edge 13 of the piston 3 was moved axially over the edge 28 of the second opening 7 and thus over the closing edge 16 and the second opening 7 was thereby partially released by the piston 3.
  • the result is a free second opening cross-section 18 of the second opening 7, delimited by the control edge 13 and the closing edge 16 , 11, 12 limited flow chamber 30 is formed.
  • the annular chamber 23 is designed to be continuously open from the first opening 6 via the annular chamber 23 to the second opening 7 as the flow chamber 30.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

L'invention se rapporte à une soupape (1), comprenant au moins un boîtier de soupape (2) et un piston (3), le piston (3) étant logé dans le boîtier de soupape (2) et pouvant être déplacé d'un premier mode de commutation de la soupape (1) à un deuxième mode de commutation de la soupape (1) et d'un deuxième mode de commutation à un troisième mode de commutation de la soupape (1). L'invention se rapporte également à un procédé de régulation d'un milieu d'écoulement à l'aide de la soupape (1).
EP21739551.6A 2020-06-29 2021-06-22 Soupape et procédé de régulation d'un milieu d'écoulement à l'aide de la soupape Withdrawn EP4172520A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020116993.0A DE102020116993A1 (de) 2020-06-29 2020-06-29 Ventil und Verfahren zur Steuerung eines Strömungsmittels mit dem Ventil
PCT/DE2021/100529 WO2022002305A1 (fr) 2020-06-29 2021-06-22 Soupape et procédé de régulation d'un milieu d'écoulement à l'aide de la soupape

Publications (1)

Publication Number Publication Date
EP4172520A1 true EP4172520A1 (fr) 2023-05-03

Family

ID=76844959

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21739551.6A Withdrawn EP4172520A1 (fr) 2020-06-29 2021-06-22 Soupape et procédé de régulation d'un milieu d'écoulement à l'aide de la soupape

Country Status (5)

Country Link
US (1) US11982365B2 (fr)
EP (1) EP4172520A1 (fr)
CN (1) CN115803549A (fr)
DE (1) DE102020116993A1 (fr)
WO (1) WO2022002305A1 (fr)

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
UA11093A (uk) 1986-08-28 1996-12-25 Екер Машіненбау Гмбх Гідравлічhий клапаh
FR2817014A1 (fr) * 2000-11-17 2002-05-24 Montage Auto Camions Soc D Soupape de degazage
DE102004020275B4 (de) * 2004-03-15 2006-04-27 Brueninghaus Hydromatik Gmbh Ventil
JP4329645B2 (ja) * 2004-08-18 2009-09-09 株式会社豊田自動織機 逆止弁
KR100940820B1 (ko) * 2009-09-30 2010-02-04 동일기계공업 주식회사 차량용 가변용량 압축기의 석션밸브
WO2012058751A1 (fr) 2010-11-01 2012-05-10 Magna Powertrain Inc. Soupape de sûreté présentant un orifice
KR101120841B1 (ko) * 2012-01-05 2012-03-16 김기연 차량용 가변용량 압축기의 체크밸브
DE102012104286A1 (de) 2012-05-16 2013-11-21 Voss Automotive Gmbh Druckbegrenzungsventil
JP5993291B2 (ja) 2012-11-27 2016-09-14 日立オートモティブシステムズ株式会社 可変容量形ポンプ
TWM537535U (zh) * 2016-10-31 2017-03-01 Yu-Wen Lin 壓差式充氣裝置
DE102019108694A1 (de) 2019-04-03 2020-04-23 Schaeffler Technologies AG & Co. KG Getriebevorrichtung mit einer Vorrichtung zur Regelung von Drücken

Also Published As

Publication number Publication date
US20230313894A1 (en) 2023-10-05
WO2022002305A1 (fr) 2022-01-06
US11982365B2 (en) 2024-05-14
CN115803549A (zh) 2023-03-14
DE102020116993A1 (de) 2021-12-30

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