WO2021018345A1 - Soupape pour réguler la pression d'un milieu d'écoulement - Google Patents

Soupape pour réguler la pression d'un milieu d'écoulement Download PDF

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Publication number
WO2021018345A1
WO2021018345A1 PCT/DE2020/100599 DE2020100599W WO2021018345A1 WO 2021018345 A1 WO2021018345 A1 WO 2021018345A1 DE 2020100599 W DE2020100599 W DE 2020100599W WO 2021018345 A1 WO2021018345 A1 WO 2021018345A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
valve
opening
valve housing
transition section
Prior art date
Application number
PCT/DE2020/100599
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 WO2021018345A1 publication Critical patent/WO2021018345A1/fr

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
    • 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
    • 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
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise

Definitions

  • Valve for regulating pressures of a fluid
  • the invention relates to a valve with a valve housing and with at least one piston, with the features:
  • the piston and the valve housing are arranged coaxially to one another, the valve axis being axially aligned,
  • the piston is axially movably received in the valve housing and is guided axially movably and radially centered in the valve housing via a piston jacket,
  • valve housing is provided with a first opening which is permeable to fluid and which can be closed by the piston head of the piston.
  • Pressure compensation valves are installed in the oil ducts of gearboxes. If the pressure of the gear oil in the oil channel rises to or above a defined pressure, a piston of the valve opens an inlet opening. The transmission oil flows through the valve via an outlet opening into a bypass or return channel until the pressure falls below the defined level and the inlet opening is closed again by the piston.
  • DE 196 19 703 A1 discloses the geometry of the sealing seats of valves for regulating pressures in fluid circuits.
  • the object of the invention is to create a valve which is inexpensive to manufacture and which functions reliably.
  • a valve is provided with a valve housing and with at least one piston, in which the piston and the valve housing are coaxial with one another on one imaginary valve axis are arranged.
  • the valve axis is aligned in the axial direction.
  • the piston has a piston crown and a piston skirt. The piston is axially movably received in the valve housing and guided axially movably and radially centered in the valve housing via the piston jacket.
  • the end of the valve housing is provided with a first opening which is permeable to fluid and which can be closed by the piston head of the piston.
  • the piston crown has a smaller outer diameter than the piston skirt.
  • the piston head and the piston skirt are connected to one another by means of a transition section formed on the piston. The piston head goes over to the transition section in the piston skirt.
  • the transition section extends from the piston head to the piston jacket and the piston jacket extends in the axial direction from the transition section away coaxially to the valve axis to one end of the piston.
  • the transition section has a radial channel-shaped recess that extends around the valve axis and is concave in the direction of the valve axis.
  • the recess is ra dial outside, that is radially removed from the valve axis, optionally rounded on the outside circumference with a very small radius at the transition to the piston skirt.
  • Valves in the form of pressure equalization valves are preferably made from sheet metal by forming. For manufacturing reasons, generous edge radii are provided, for example to ensure the service life of tools.
  • the piston is arranged with radial play in the valve housing, so that a longitudinal movement of the piston is possible at all. So there is a small movement gap between the piston and valve housing asbil det, which is necessary for the sliding fit of the piston. Surprisingly, it turned out that precisely these roundings in the area of the sliding seats of the piston have a detrimental effect on its function. The fine particles of metallic abrasion or dirt in the fluid collect in these areas and hinder or block the displacement of the piston in the valve. Because they are pulled into the movement gap when the piston closes, for example.
  • the piston produced by a drawing process is provided with a rounded edge on the outside at the transition from the piston crown to the piston skirt, the radius of which is equal to or less than 0.1 mm.
  • This radius can be embossed or ground.
  • the radial, channel-shaped depression on the outer circumference has a cone jacket surface in the shape of a truncated cone, facing the valve housing and oriented coaxially to the valve axis.
  • a truncated cone is a solid of revolution which is described above and below by a circular surface and has a conical surface between the circular surfaces.
  • the geometry of the imaginary larger circular area at the bottom of the truncated cone is given by the outer diameter of the piston skirt.
  • the geometry of the imaginary smaller circular area is specified by the shortest radial distance between the conical surface area and the piston or valve axis.
  • the conical surface extending between the two imaginary circular surfaces runs inclined to the valve axis.
  • Such a design of the transition area can preferably be produced by forming, such as embossing or upsetting.
  • the transition to the piston skirt is less abrupt and flatly inclined, but at the end it is so relatively sharp-edged that dirt particles that may be deposited in the area cannot be drawn into the movement gap when the piston moves.
  • the surface of the cone is described by any number of lines inclined to the valve axis with a cone angle and the valve axis intersecting at a common point of intersection. According to one embodiment of the invention it is provided that a respective supplementary angle to the cone angle enclosed between an imaginary radial plane penetrated perpendicularly by the valve axis and each of the surface line is an acute angle.
  • the outer circumference of the piston jacket is described by an outer cylindrical piston jacket surface, the conical jacket surface and the piston skirt surfaces are directly adjacent to one another. The wedge space is designed to run very flat and the pull-in effect is prevented.
  • Another embodiment of the invention provides that an outer cylindrical surface coaxial to the valve axis is formed on the piston on the transition section between the piston head and the conical surface, which has an advantageous effect on the non-cutting manufacture of the piston.
  • annular channel extending around the axis of rotation is formed between the transition section and the valve housing.
  • the ring channel is limited at least by the transition portion and an inner peripheral surface of the valve housing.
  • the first opening and the piston head are aligned coaxially to the valve axis.
  • the piston head is provided with a convex sealing edge that runs around the valve axis.
  • the sealing edge is in sealing contact with a concave sealing seat of the valve housing.
  • the sealing seat is formed on the first opening.
  • the valve has at least one spring and at least one support element.
  • the piston is movable against spring forces of the spring and the spring is supported at least in the first axial direction on the support element and in the second axial direction on the piston.
  • the valve housing is provided with a second opening which is at least partially closable by a piston skirt of the piston and permeable to the fluid.
  • the second opening is aligned in the valve housing transversely to the first opening and is directed towards the valve axis.
  • the piston is guided axially movably in the valve housing and radially centered in the valve housing via the piston jacket. This advantageously results in a substantially pressure-tight and at the same time axially movable guidance of the piston in the valve housing Ven, especially when the radial play with which the piston is radially centered in the housing is very small.
  • the sliding surfaces, d. h., The diameter of the inner cylindrical surface of the valve housing and the outer cylindrical surface of the piston can be adjusted very precisely when pulling these components without cutting from sheet metal without chip-breaking post-processing. If necessary, Gleitbe coatings on the surfaces of the components are advantageous.
  • the piston is guided axially movably in the valve housing against the spring forces of the spring from a closed position into an open position.
  • the first opening is closed by the piston crown and the two te opening at least partially through the piston skirt.
  • the piston head has lifted off the valve seat.
  • At least one edge or a contour of the piston releases the second opening analogously to a control edge, so that a connection is formed between the first opening and the second opening that is continuous for fluid.
  • the first opening axially opposite the open end of the valve housing is sealed against the fluid both in the closed position and in the open position by the piston, subject to a leakage gap caused by radial play through the piston.
  • the second opening which in this case is a return opening, is only partially closed by the piston skirt.
  • the result is that a gap-shaped passage opening of the second opening that is permeable to the fluid is not covered by the piston skirt in the closed position and is not closed by the piston.
  • the gap-shaped fürgangsöff voltage is limited at least in the closed position by a portion of the piston and an edge of the second opening.
  • annular channel is formed between the piston and the valve housing, which is directly connected to the valve seat.
  • the annular channel can be designed belie big by the design of the valve housing and the piston.
  • the annular channel fills with the fluid immediately after the piston lifts off the valve seat. The pressure of the fluid is thereby converted over a larger area of the piston.
  • annular channel is already open in the closed position of the piston at the gap-shaped through opening towards the second opening.
  • the valve is provided with a sleeve-shaped valve housing which has the edge of the sheet metal through a sleeve jacket aligned concentrically to the valve axis and a ra dial aligned in the direction of the valve axis and extending around the first opening.
  • the edge is optionally provided with a separate valve seat fastened to the edge or the valve seat is stamped directly into the edge of sheet metal.
  • the piston is sleeve-shaped with a hollow cylindrical piston skirt and a piston head that closes the piston on one side, the spring being axi al surrounded by the piston skirt and supported axially inside the piston on the piston head.
  • the piston is preferably made of sheet metal.
  • the piston crown is correspondingly thin-walled. Compared to solid pistons, there is thus more axial installation space available for the spring, since the interior of the piston is also available as installation space for the spring. As a result, more options are available when selecting and designing the spring, which can also consist of several springs connected in parallel or in series.
  • the second opening is aligned transversely to the first opening and introduced into a valve housing made of sheet metal, preferably by punching.
  • the second opening extends at a radial distance from the valve axis in the axial direction.
  • the central axis of the opening runs in the radial direction perpendicular to the valve axis, i.e. the second opening is oriented transversely to the first opening and is introduced into a valve housing made of sheet metal, preferably by punching.
  • the valve housing can be manufactured easily and inexpensively.
  • valve 1 is designed in this case as a pressure compensation valve in an oil flow of a vehicle transmission.
  • Figure 1 shows a longitudinal section along the valve axis 2 through the valve 1. The valve 1 is shown closed.
  • Figure 2 shows the detail Z of the valve 1 shown in Figure 1 in one possible embodiment, enlarged and not to scale.
  • Figure 3 shows the detail Z of the valve 1 shown in Figure 1 in a further possible union embodiment, enlarged and not to scale.
  • FIG. 4 with the detail Y, additionally serves to explain the embodiment shown in FIG.
  • FIG. 5 shows the valve 1 from FIG. 1 open.
  • FIG. 6 serves to describe the problem on the basis of the prior art and, analogous to the illustration according to FIG. 4, shows a detail of a known transition area, not to scale and enlarged.
  • FIG. 1 - The valve 1 has a valve housing 3, a piston 4, a support element 5 and a spring 8.
  • the valve housing 3 and the piston 4 are designed to be essentially rotationally symmetrical and are arranged coaxially to the valve axis 2.
  • the valve axis 2 is axially aligned.
  • the piston 4 is axially movable but radially closely guided in the valve housing 3 with little radial play and is provided with a piston skirt 6 and a piston head 7.
  • the piston skirt 6 is formed from a hollow cylinder and coaxially aligned with the valve axis 2 and extends from the Kol benboden 7 in the direction of the support element 5.
  • the spring 8 is a compression spring and plunges axially into the piston 4 and is axially in one direction the piston base 7 and supported in the other axial direction on a support element 5 such that a spring 8 is clamped axially between the piston base 7 and the support element 5.
  • the support element 5 engages with projections 9 in a circumferential groove 10 of the Valve housing 3 and is there supported by the spring action of the projections 9 firmly carry.
  • the piston 4 is movable from a closed position shown in FIG. 1 against the action of the spring forces of the spring 8 into an open position shown in FIG.
  • FIGS. 1 and 5 - The sleeve-shaped valve housing 3 is provided with a first opening 11 permeable to fluid and with a second opening 12.
  • the first opening 11 is formed on the head side of the pressure equalization valve on the valve housing 3, arranged coaxially to the valve axis 2 and pierced perpendicularly by the valve axis 2.
  • the second opening 12 is directed transversely to the first opening 11, i. This means that the second opening 12 extends at a radial distance from the valve axis 2 in the axial direction.
  • the center axis of the second opening runs in the radial direction perpendicular to the valve axis 2.
  • FIGS. 2, 3 and 5 - A valve seat 13 is formed on the edge of the valve housing 3 at the first opening 11.
  • the valve seat 13 preferably has a concave inwardly curved dome-shaped surface 14 (FIGS. 2 and 3) on the valve housing 3, which corresponds to a convex annular surface 15 of the piston 4.
  • the piston boom 7 is axially adjoined by a transition section 16 at which the piston head 7 merges into the piston skirt 6 and the piston skirt 6 merges into the piston head 7.
  • FIG. 1 - In the closed position of the piston 4, the second opening 12 is largely closed by the piston skirt 6, but a gap-shaped passage opening 18 which is permeable to fluid remains.
  • the gap-shaped through opening 18 is limited by the piston skirt 6 or by the transition section 16 of the piston 4 and an edge of the valve housing 3 at the second opening 12 Publ.
  • the valve chamber 19, the rear of the piston surface 17 of the Piston head 7 extends to the end 21 of valve 1, is sealed off from first opening 11 by means of piston 4.
  • an annular gap (movement gap) formed between the piston skirt 6 and the valve housing 3 due to lower radial play is not taken into account.
  • FIGS 1, 2 and 3 In the closed position, an annular channel 20 is formed between the piston 4 and the valve housing 3, which is delimited by the transition section 16 on the piston 4 and a section of the valve housing 3.
  • the section of the valve housing 3 extends from the valve seat 13 towards the hollow cylindrical sleeve jacket of the valve housing 3.
  • FIG. 1 The annular channel 20 is open in the closed position at the gap-shaped passage opening 18 and otherwise closed all round. It is assumed that the pressure equalizing valve shown in FIG. 1 is installed in a device (not shown) in the closed position of the piston 4. In this position, the force exerted by the pressure of a fluid on the surface 17 of the piston head is less than or equal to a counterforce acting on the back of the piston head 7 inside the pressure compensation valve.
  • the counterforce is primarily a result of the spring force exerted on the rear side of the piston head 7 of the spring 8 clamped between the piston head 7 and the support element 5.
  • FIG. 5 - When the pressure at the first opening 11 increases, the piston 4 moves axially in the direction of the supporting element 5 into the open position and releases the valve seat 13 and thus the first opening 11.
  • the fluid symbolized by the plurality of arrows flows through the first opening 11 through the interior of the pressure compensation valve via the second opening 12 out again.
  • the piston 4 subject to a leakage gap (movement gap) predetermined by the radial play also seals the rear side of the pressure compensation valve with respect to its open end 21.
  • the transition section 16 is designed in the form of a concave groove-shaped groove and connects the piston head 7 with the piston skirt 6.
  • the outer diameter D1 of the piston head 7 is smaller than the outer diameter D2 of the piston skirt 6.
  • the transition section 16 extends from the piston head 7th from up to the piston skirt 6 and the piston skirt 6 extends in the axial direction away from the transition section 16 coaxially to the valve axis 2 to one end of the piston 4.
  • the transition section 16 is a running around the valve axis 2 and curved concavely in the direction of the valve axis 2, radial groove-shaped recess.
  • the surface 17 of the piston head 7 can, as shown, be a flat circular surface, but alternatively also a convex or concave or otherwise three-dimensional structured surface.
  • the piston head 7 and the piston skirt 6 are connected to one another by means of the transition section 16 in such a way that, in the channel-shaped recess, an outer cylindrical section with an outer cylindrical surface 22, which extends axially with the valve axis 2 and runs around the valve axis, initially follows the annular surface 15 , then the section is followed by a flute throat 23 as a transition into an axial shoulder 24 extending in the radial direction and the axial shoulder 24 finally ends at the transition to the piston skirt 6 at an edge 25.
  • Figure 2 - For the embodiment shown with Figure 2, the edge 25 is described by a radius RA, which has a maximum value of 0.1 mm.
  • FIGS. 3 and 4 - the transition section 16 has on an axial shoulder 24 a cylindrical circular ring surface 27 lying in a radial plane E, which follows the flute groove 23 radially.
  • On the annular surface 27 follows a first edge 31 facing the valve housing 3 and aligned coaxially to the valve axis 2 Kegelman telology 26, which is described by the shape of an imaginary truncated cone.
  • the first edge 31 is an edge running around the valve axis 2.
  • Figure 1 - The truncated cone and thus the conical surface 26 is described by any number of surface lines inclined to the valve axis 2 with a cone angle ⁇ ( Figure 4) and in their extension the valve axis 2 in a common intersection point 28 (see Figure 1) intersecting surface lines from which due to the sectional views in the Figures 1 and 4 each only the surface line 30 and in Figure 1 the surface lines 29 and 30 are visible.
  • the cone angle ⁇ is the angle ⁇ enclosed between the respective surface lines 29 or 30 and the valve axis 2 or between the respective surface line 29 or 30 and a line P parallel to the valve axis (FIG. 4).
  • FIG. 6 - The inventive design of the transition section 16 described with FIGS. 1 to 4 can prevent that, as shown in FIG. 6 as internal prior art in the form of a test sample by the applicant, in the direction of arrow 36 Dirt particles 34 are drawn between the piston skirt 6 and the valve housing 3 and prevent the movement of the piston 4 in the valve housing 3. Between the piston 4 and the valve housing 3 there is a pointed, wedge-shaped annular gap 37 in the direction of movement of the piston 4, in which the dirt particles 34 easily jam when the piston 4 moves into the closed position of the piston 4 shown in FIG. Reference number

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

L'invention concerne une soupape (1) avec un boîtier de soupape (3) et au moins un piston (4), ayant les caractéristiques suivantes : - le piston (4) et le boîtier de soupape (3) sont disposés de façon coaxiale l'un par rapport à l'autre sur un axe de soupape imaginaire (2), l'axe de soupape (2) étant orienté dans une première direction axiale et dans une seconde direction axiale opposée à la première direction axiale, - le piston (4) ayant une base de piston (7) et une enveloppe de piston (6), - le piston (4) est reçu de manière à pouvoir se déplacer axialement dans le boîtier de soupape (3) et est par conséquent guidé dans le boîtier de soupape (3) de manière à pouvoir se déplacer axialement sur l'enveloppe de piston (6) et de manière centrée radialement, et - le boîtier de soupape (3) comprend une première ouverture (11) à travers laquelle peut passer un milieu d'écoulement, et qui peut être fermée par la base de piston (7) du piston (4).
PCT/DE2020/100599 2019-07-26 2020-07-08 Soupape pour réguler la pression d'un milieu d'écoulement WO2021018345A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019120221.3 2019-07-26
DE102019120221.3A DE102019120221A1 (de) 2019-07-26 2019-07-26 Ventil zur Regelung von Drücken eines Strömungsmittels

Publications (1)

Publication Number Publication Date
WO2021018345A1 true WO2021018345A1 (fr) 2021-02-04

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Application Number Title Priority Date Filing Date
PCT/DE2020/100599 WO2021018345A1 (fr) 2019-07-26 2020-07-08 Soupape pour réguler la pression d'un milieu d'écoulement

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WO (1) WO2021018345A1 (fr)

Families Citing this family (1)

* 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

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL57560C (fr) * 1900-01-01
DE2130162A1 (de) * 1970-06-23 1972-01-27 Kh Awiazionnij I Druckdifferenz-Absperrventil
DE3120606A1 (de) * 1981-05-23 1983-07-28 Bayerische Motoren Werke AG, 8000 München Ventil zur druckbegrenzung in hydraulischen anlagen
DE4218325A1 (de) * 1992-06-03 1993-12-09 Rexroth Mannesmann Gmbh 2/2-Wegeventil
DE19619703A1 (de) 1995-05-18 1996-11-21 Caterpillar Inc Ventil-Interface für ein Sitzventil
EP0798471A2 (fr) * 1996-03-25 1997-10-01 Hydrolux S.A.R.L. Soupape à deux voies sous forme de cartouche
DE102014213751A1 (de) * 2014-05-23 2015-11-26 Continental Teves Ag & Co. Ohg Ventilbaugruppe
CN107835910A (zh) * 2015-05-15 2018-03-23 株式会社电装 溢流阀以及使用了该溢流阀的高压泵
WO2019057374A1 (fr) * 2017-09-25 2019-03-28 Robert Bosch Gmbh Vanne de commande de fluide sous pression, notamment destinée à commander un sens de circulation dans un circuit de fluide sous pression et pompe à piston, notamment destinée à refouler un fluide sous pression dans un système de freinage de véhicule à régulation électronique du patinage
WO2020114550A1 (fr) * 2018-12-06 2020-06-11 Schaeffler Technologies AG & Co. KG Soupape et procédé de fabrication d'une soupape et dispositif de régulation des pressions d'un fluide dans une transmission de véhicule pourvu d'une soupape conçue comme une soupape de compensation de pression

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL57560C (fr) * 1900-01-01
DE2130162A1 (de) * 1970-06-23 1972-01-27 Kh Awiazionnij I Druckdifferenz-Absperrventil
DE3120606A1 (de) * 1981-05-23 1983-07-28 Bayerische Motoren Werke AG, 8000 München Ventil zur druckbegrenzung in hydraulischen anlagen
DE4218325A1 (de) * 1992-06-03 1993-12-09 Rexroth Mannesmann Gmbh 2/2-Wegeventil
DE19619703A1 (de) 1995-05-18 1996-11-21 Caterpillar Inc Ventil-Interface für ein Sitzventil
EP0798471A2 (fr) * 1996-03-25 1997-10-01 Hydrolux S.A.R.L. Soupape à deux voies sous forme de cartouche
DE102014213751A1 (de) * 2014-05-23 2015-11-26 Continental Teves Ag & Co. Ohg Ventilbaugruppe
CN107835910A (zh) * 2015-05-15 2018-03-23 株式会社电装 溢流阀以及使用了该溢流阀的高压泵
WO2019057374A1 (fr) * 2017-09-25 2019-03-28 Robert Bosch Gmbh Vanne de commande de fluide sous pression, notamment destinée à commander un sens de circulation dans un circuit de fluide sous pression et pompe à piston, notamment destinée à refouler un fluide sous pression dans un système de freinage de véhicule à régulation électronique du patinage
WO2020114550A1 (fr) * 2018-12-06 2020-06-11 Schaeffler Technologies AG & Co. KG Soupape et procédé de fabrication d'une soupape et dispositif de régulation des pressions d'un fluide dans une transmission de véhicule pourvu d'une soupape conçue comme une soupape de compensation de pression

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