WO2020114560A1 - Valve and device for the control of pressures of a flow medium in a vehicle transmission with a valve - Google Patents

Valve and device for the control of pressures of a flow medium in a vehicle transmission with a valve 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
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WO
WIPO (PCT)
Prior art keywords
piston
valve
opening
valve housing
throttle
Prior art date
Application number
PCT/DE2019/101045
Other languages
German (de)
French (fr)
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/en

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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

The invention relates to a valve (20) with a valve housing (2), at least one piston (3), at least one supporting element (4) and at least one spring (5), with the features: - the piston (3) and the valve housing (2) are arranged coaxially with respect to one another on an imaginary valve axis (6), wherein the valve axis (6) is oriented axially in a first axial direction and in a second axial direction which is opposed to the first axial direction, - the piston (3) is received in the valve housing (2) such that it can be moved axially counter to spring forces of the spring (5), wherein the spring (5) is supported on the supporting element (4) at least in the first axial direction and on the piston (3) in the second axial direction, - the supporting element (4) is supported on the valve housing (2), - the piston (3) has a piston crown (7) and a piston skirt (9), - the valve housing (2) is provided with a first opening (8) which is permeable to flow medium and which can be closed by way of the piston crown (7), - the piston (3) can be displaced here axially counter to the spring (5) in the direction of the supporting element (4) in a manner which is guided in the valve housing (2) via the piston skirt (9), - the valve housing (2) has, at an end (19) which is axially remote from the first opening (8), at least one throttle opening which is permeable for the flow medium and which is delimited by way of a throttle plate (32).

Description

Ventil und Vorrichtung zur Regelung von Drücken eines Strömungsmittels in einem Valve and device for regulating pressures of a fluid in one
Fahrzeuqqetriebe mit einem Ventil Vehicle gearbox with a valve
Gebiet der Erfindung Field of the Invention
Die Erfindung betrifft ein Ventil mit einem Ventilgehäuse, wenigstens einem Kolben, mindes tens einem Stützelement und zumindest einer Feder, mit den Merkmalen: 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:
der Kolben und das Ventilgehäuse sind zueinander koaxial auf einer gedachten Ven tilachse angeordnet, wobei die Ventilachse in eine erste axiale Richtung sowie in eine zur ers ten axialen Richtung entgegengesetzte zweite axiale Richtung axial ausgerichtet ist, 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,
der Kolben ist gegen Federkräfte der Feder axial beweglich in dem Ventilgehäuse auf genommen, wobei die Feder zumindest in die erste axiale Richtung an dem Stützelement und in die zweite axiale Richtung an dem Kolben abgestützt ist, 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,
das Stützelement ist an dem Ventilgehäuse abgestützt, the support element is supported on the valve housing,
der Kolben weist einen Kolbenboden und einen Kolbenmantel auf, the piston has a piston crown and a piston skirt,
das Ventilgehäuse ist mit einer strömungsmitteldurchlässigen ersten Öffnung verse hen, welche durch den Kolbenboden verschließbar ist, the valve housing is provided with a fluid-permeable first opening, which can be closed by the piston crown,
der Kolben ist über den Kolbenmantel in dem Ventilgehäuse geführt dabei axial gegen die Feder in Richtung des Stützelementes verschiebbar. Die Erfindung betrifft auch eine Vor richtung zur Regelung von Drücken eines Strömungsmittels in einem Fahrzeuggetriebe mit ei nem derartigen Ventil. the piston is guided over the piston jacket in the valve housing and axially displaceable against the spring in the direction of the support element. The invention also relates to a device for regulating pressures of a fluid in a vehicle transmission with egg nem such valve.
Hintergrund der Erfindung Background of the Invention
Ein Ventil der Gattung ist in EP 1 382 893 A1 offenbart. Dieses Ventil ist ein Druckbegren zungsventil in einem hydraulischen Kreislauf. Es ist aus einem Ventilgehäuse, einem Kolben mit einer Kugel, einer Feder und aus einem Stützelement gebildet. In einer Schließstellung sind Kugel und Kolben mittels der Feder in Richtung der stirnseitigen Öffnung des Ventilge häuses vorgespannt. Die als Druckfeder ausgebildete Feder stützt sich dabei axialen die eine Richtung an dem Kolbenboden und axial in die andere Richtung an einem scheibenförmig ausgebildeten Stützelement ab und wird dort auch radial geführt. Das Stützelement ist form- und kraftschlüssig in dem Ventilgehäuse verankert. Die Kugel verschließt in der Schließstel lung die Öffnung. Das Ventil sitzt in einem Gehäuse mit Kanälen. Die stirnseitige Öffnung des massiven Ventilgehäuses mündet strömungstechnisch in einen zuführenden Kanal mit hohem Druckniveau. Der Ausgang des Ventiles ist rückseitig des Ventilgehäuses an einer der stirn seitigen Öffnung axial gegenüberliegend vorgesehen und mit einem abführenden Kanal nied- rigerem Druckniveaus strömungstechnisch verbunden. Das Ventil öffnet, wenn der Druck in dem zuführenden Kanal eine vorgegebene Grenze überschreitet. Eine bzw. mehrere Drossel öffnungen im Stützelement regeln die Durchflussmenge des hydraulischen Strömungsmittels durch das Ventil in den abführenden Kanal und damit die angestrebte Druckminderung in dem zuführenden Kanal, so, dass das Stützelement zugleich die Funktion einer Drosselscheibe er füllt. 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.
Beschreibung der Erfindung Description of the invention
Die Aufgabe der Erfindung ist es, ein Ventil und eine Vorrichtung zur Regelung von Drücken mit einem derartigen Ventil zu schaffen, die sich einfachen kostengünstig hersteilen sowie va riabel einsetzen lassen. 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.
Diese Aufgabe ist mit einem Ventil nach dem Gegenstand des Anspruchs 1 und einer Vorrich tung zur Regelung von Drücken eines Strömungsmittels in einem Fahrzeuggetriebe nach ei nem weiteren Anspruch gelöst. This object is achieved with a valve according to the subject matter of claim 1 and a device for regulating pressures of a fluid in a vehicle transmission according to another claim.
Erfindungsgemäß ist eine Drosselscheibe als separates Bauteil zwischen dem Kolben und dem Stützelement angeordnet. Der Vorteil dieser Erfindung ergibt sich daraus, dass ein Ventil mit einer gegenüber den Drosselbohrungen im Stützelement nach dem bekannten Stand der Technik separat zu dem Stützelement ausgebildeten Drosselscheibe variabler auf zu regelnde bzw. Öffnungsdrücke einstellbar ist. Die Drosselscheibe, die wahlweise ein Bauelement aus einem Metall oder aus Kunststoffen ist, kann als Massenware aber auch in kleineren Losen kostengünstig und mit sehr genau ausgebildeten Drosselöffnungen bzw. Abmessungen her gestellt werden. Der Strömungsquerschnitt der Drosselöffnungen kann mit einfachen Mitteln verändert werden und so die Dämpfung der Axialbewegung des Kolbens bzw. von axialen Schwingungen des Kolbens eingestellt werden. Die anderen Bauelemente des Ventils können unverändert verbleiben. Das Stützelement kann unabhängig von den Anforderungen an die Genauigkeit einer Drosselscheibe als einfaches Stanzteil, zum Beispiel aus Blech, und dabei beispielsweise aus einem Federstahl, hergestellt werden. Eventuelle Verformungen des Stüt zelements beim Einpressen bzw. Einbördeln haben keinen Einfluss auf die Genauigkeit der Drosselöffnungen. According to the invention, 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.
Nach einer Ausgestaltung der Erfindung ist vorgesehen, dass die Drosselöffnung als wenigs tens ein zwischen dem Ventilgehäuse und der Drosselscheibe für die Strömungsmittel durch lässiger Drosselspalt ausgebildet ist. Der Querschnitt der Drosselöffnung bzw. des Drossel spaltes, der vorzugsweise ein Ringsspalt ist, ist vorteilhaft über den Durchmesser der Dros- selscheibe vorbestimmt und ergibt sich im Wesentlichen aus der Differenz des Innendurch messers des Ventilgehäuses und des Außendurchmessers der Drosselscheibe. According to one embodiment of the invention, it is provided that 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.
Die Drosselscheibe ist gemäß der Erfindung zwischen dem einen Ende der Feder und dem Stützelement angeordnet und dort bevorzugt zwischen der als Druckfeder ausgebildeten Fe der und dem Stützelement unter Wirkung der Federvorspannung axial eingeklemmt. In die sem Zusammenhang sieht eine Ausgestaltung der Erfindung vor, dass die Drosselscheibe an dem Stützelement befestigt ist. Der Vorteil einer derartigen Lösung liegt darin, dass die Dros selscheibe vor der Montage in das Ventil bereits an dem Stützelement zentriert und so befes tigt werden kann, dass die Drosselscheibe während der Montage des Ventils nicht gesondert zugeführt und aufwendig ausgerichtet werden muss. Diese Lösung lässt sich dadurch vorteil haft ausgestalten, dass das Stützelement mittig ein Durchgangsloch aufweist, in die ein Befes tigungsmittel der Druckscheibe vorzugsweise formschlüssig eingreift und die Druckscheibe auf einfache Weise in dem scheibenartig ausgebildeten Stützelement zentriert ist. 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. In this context, an embodiment of the invention provides that the throttle plate is attached to the support element. The advantage of such a solution is that the throttle plate is already centered on the support element prior to installation in the valve and can be fastened in such a way that the throttle plate does not have to be supplied separately during assembly of the valve and has to be aligned in a complex manner. 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.
Eine Ausgestaltung der Erfindung sieht vor, dass die Feder axial an der Drosselscheibe an liegt sowie über die Drosselscheibe radial in dem Ventilgehäuse geführt und zentriert ist.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.
Durch diese Ausführung der Drosselscheibe kann auch mit einfachen Mitteln auf ein kompli ziertes Design der Stützfeder verzichtet werden. With this design of the throttle plate, a complicated design of the support spring can also be dispensed with using simple means.
Mit der Erfindung ist weiterhin eine Vorrichtung zur Regelung von Drücken eines Strömungs mittels in einem Fahrzeuggetriebe vorgesehen. Die Vorrichtung ist aus einem Abschnitt eines Getriebebauteils, aus zumindest einem ersten Kanal und einem zweiten Kanal sowie aus dem Ventil gebildet. Das Ventil ist ein Druckausgleichsventil. Die Kanäle verlaufen in einem Ge häuse oder einem Bauteil des Fahrzeuggetriebes. Der erste Kanal führt in dem Abschnitt des Getriebebauteils, in welchem das Druckausgleichsventil sitzt, zu der ersten Öffnung. Das Druckausgleichsventil weist eine für Strömungsmittel durchlässige zweite Öffnung im Ventil gehäuse auf, die in den zweiten Kanal mündet. Die zweite Öffnung ist gemäß einer Ausgestal tung der Erfindung quer zu den axialen Richtungen ausgerichtet und von dem Kolbenmantel verschließbar. 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. According to one embodiment of the invention, the second opening is oriented transversely to the axial directions and can be closed by the piston skirt.
Eine weitere Ausgestaltung der Erfindung sieht vor, dass der Kolben gegen die Federkräfte der Feder aus einer Schließstellung in eine axial von der Schließstellung entfernte Öffnungs stellung axial beweglich in dem Ventilgehäuse geführt ist. In der Schließstellung des Kolbens ist die erste Öffnung mittels des Kolbens verschlossen. In der Öffnungsstellung des Kolbens ist die erste Öffnung durch den Kolben freigegeben, so dass in der Öffnungsstellung über die erste Öffnung und die zweite Öffnung ein für die Strömungsmittel freier Durchlass durch das Ventilgehäuse gebildet ist. 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. In the closed position of the piston, the first opening is closed by means of the piston. In the open position 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.
Beschreibung der Zeichnungen Description of the drawings
Die Erfindung wird nachfolgend anhand eines Ausführungsbeispiels und weiteren Ausgestal tungen näher beschrieben. Es zeigen: The invention is described below with reference to an embodiment and further Ausgestal lines. Show it:
Figur 1 eine Gesamtansicht eines erfindungsgemäßen Druckausgleichsventils 1 , FIG. 1 shows an overall view of a pressure compensation valve 1 according to the invention,
Figur 2 einen Längsschnitt durch das Druckausgleichsventil 1 bzw. durch einen Ausschnitt ei ner Vorrichtung 30 zur Regelung von Drücken eines Strömungsmittels in einem ansonsten nicht weiter dargestellten Fahrzeuggetriebe entlang der Ventilachse 6 des Druckausgleichs ventils 1 , wobei der Kolben 3 in einer Schließposition I steht. 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.
Figur 3 die Rückansicht des Druckausgleichsventils 1 nach Figur 1 , FIG. 3 the rear view of the pressure compensation valve 1 according to FIG. 1,
Figur 4 den Längsschnitt nach Figur 2 durch das Druckausgleichsventil 1 bzw. die Vorrich tung 30 entlang der Ventilachse 6 des Druckausgleichsventils 1 , wobei der Kolben 3 jedoch in einer Öffnungsposition II steht und 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
Figur 5 eine vergrößerte und nicht maßstäbliche Darstellung des Details X des Ventils 20 aus der Figur 2. FIG. 5 shows an enlarged and not to scale representation of the detail X of the valve 20 from FIG. 2.
Figuren 2 und 4 - Das Druckausgleichsventil 1 weist ein Ventilgehäuse 2, einen Kolben 3, ein Stützelement 4 und eine Feder 5 auf. Das Ventilgehäuse 2 und der Kolben 3 sind im Wesent lichen rotationssymmetrisch ausgebildet und koaxial zu einer Ventilachse 6 angeordnet. Die Ventilachse 6 ist axial ausgerichtet. Der Kolben 3 ist axial beweglich aber radial mit geringem radialem Spiel in dem Ventilgehäuse 2 geführt und mit einem Kolbenmantel 9 sowie einen Kolbenboden 7 versehen. Der Kolbenmantel 9 ist hohlzylindrisch ausgebildet und koaxial zur Ventilachse 6 ausgerichtet und erstreckt sich von dem Kolbenboden 7 aus in Richtung des Stützelements 4. Figures 2 and 4 - 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.
Figuren 2, 3, 4 und 5 - Die Feder 5 ist eine Druckfeder und axial in die eine Richtung an dem Kolbenboden 7 des Kolbens 3 und in die andere axiale Richtung über die Drosselscheibe 32 an dem Stützelement 4 so abgestützt, dass die Feder 5 axial zwischen dem Kolbenboden 7 und dem Stützelement 4 eingespannt ist. Das Stützelement 4 sitzt an einem Ende 19 des Ventilgehäuses 2. Die Drosselscheibe 32 ist als separates Bauteil zwischen dem Kolben 3 und dem Stützelement 4 angeordnet. Das Stützelement 4 greift mit den Vorsprüngen 28 in ei ne Umfangsnut 21 des Ventilgehäuses 2 ein und ist dort fest abgestützt. Figures 2, 3, 4 and 5 - 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.
Figuren 3 und 5 - Das Stützelement 4 weist eine scheibenförmig ausgebildete Basis 23 auf, von der die Vorsprünge 28 leicht zur Ventilachse 6 geneigt in die Umfangsnut 21 abgehen. Zwischen den Vorsprüngen 28 des Stützelements 4 sind für strömungsmitteldurchlässige tra pezförmige Lücken 16 ausgebildet. Außerdem weist das Stützelement 4 zentral ein Durch gangsloch 22 auf. Die Drosselscheibe 32 ist mit einem flachen Grundkörper 24 versehen, welcher flach an der Basis 23 anliegt. Zentral mittig der Drosselscheibe 32 befindet sich ein Verschluss 25, welcher das Zentrum der Drosselscheibe bestimmt. In der mit Figur 5 gezeig ten Darstellung ist der Verschluss 25 stopfenartig ausgeführt und sitzt in dem Durchgangsloch 22, wodurch dieses gegen Strömungsmittel undurchlässig verschlossen ist. Weiterhin ist der Verschluss 25 mit wenigstens einem Haltemittel 26 versehen, durch das die Drosselscheibe 32 an dem Stützelement 4 gehalten ist. In dem dargestellten Beispiel ist die Drosselscheibe 32 aus einem Metall, vorzugsweise aus Stahlblech. Das Haltemittel 26 ist ein Kragen aus plastisch verdrängtem Metall. Alternativ kann die Drosselscheibe auch aus Kunststoff gebildet sein und der Kragen kann alternativ auch durch einzelne Schnapphaken 26 gebildet sein. Der Außendurchmesser der Drosselscheibe 32 ist kleiner als der Innendurchmesser des Ventilge häuses 2, sodass ein Ringsspalt 34 zwischen der Scheibe und der Innenwandung des Ventil gehäuses ausgebildet ist. Die Drosselscheibe 32 erstreckt sich radial soweit in Richtung des Ventilgehäuses 2, dass die trapezförmige Lücken 16 vom Zentrum aus zumindest teilweise verdeckt sind und für das strömungsmitteldurchlässige Drosselöffnungen 33 in Form von Drosselspalten gebildet sind. Die Drosselspalte sind in Umfangsrichtung von den Kanten je weils zweier Vorsprünge 28 und in radialer Richtung zum Zentrum hin durch die Drossel scheibe 32 und nach außen hin durch das Ventilgehäuse 2 begrenzt. Figures 3 and 5 - 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. Furthermore, 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. In the example shown, the throttle plate 32 is made of a metal, preferably sheet steel. The holding means 26 is a collar made of plastically displaced metal. Alternatively, 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.
Figuren 1, 2 und 4 - Das hülsenförmig ausgebildete Ventilgehäuse 2 ist mit einer für Strö mungsmittel durchlässigen ersten Öffnung 8 und an seinem Hülsenmantel 14 mit einer zwei ten Öffnung 10 versehen. Die erste Öffnung ist kopfseitig des Druckausgleichsventils 1 an dem Ventilgehäuse 2 ausgebildet, koaxial zur Ventilachse 6 angeordnet und senkrecht von der Ventilachse 6 durchstoßen. Die zweite Öffnung 10 ist quer zur ersten Öffnung 8 ausge richtet, d. h., dass sich die zweite Öffnung 10 mit radialem Abstand zur Ventilachse 6 in axia ler Richtung erstreckt. Die Mittenachse 27 der Öffnung 10 verläuft in radialer Richtung senk recht zur Ventilachse 6. Figuren 2 und 4 - Der Ventilsitz 17 weist vorzugsweise eine konkav nach innen gewölbte ka lottenförmige Fläche auf, die mit einer konvexen Ringfläche 29 des Kolbens 3 korrespondiert. Dem Kolbenboden 7 schließt sich axial ein Übergangsabschnitt 11 an, an dem der Kolbenbo den 7 in den Kolbenmantel 9 bzw. der Kolbenmantel 9 in den Kolbenboden 7 übergeht. Der Übergangsabschnitt 1 1 ist in Form einer Hohlkehle konkav-rinnenförmig ausgebildet und ver bindet den Kolbenboden 7 mit dem Kolbenmantel 9. Die Ringfläche 29 schließt sich der Flä che 31 des Kolbenbodens 7 an und leitet in den Übergangsabschnitt 11 über. Die Fläche 31 kann wie dargestellt eine flache Kreisfläche alternativ aber auch eine konvex oder konkav bzw. anderweitig dreidimensional strukturierte Fläche sein. Das Ventilgehäuse 2 und der Kol ben 3 sind hülsenförmigen Bauelemente, die vorzugsweise aus flachem Blechmaterial kalt ge formt, d. h., gezogen und gestanzt werden. Figures 1, 2 and 4 - 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. Figures 2 and 4 - 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. As shown, 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.
Figuren 2 und 4 -Die Vorrichtung 30 zur Regelung von Drücken eines Strömungsmittels in einem Fahrzeuggetriebe ist aus wenigstens einem Abschnitt eines Getriebebauteils 35, einem ersten Kanal 36 einem zweiten Kanal 37 und aus dem Druckausgleichsventil 1 gebildet. Das Druckausgleichsventil 1 sitzt in einer Durchgangsbohrung 38, deren Durchmesser gleich dem des ersten Kanals 36 oder größer bzw. kleiner als der erste Kanal 36 ist. Der erste Kanal 36 führt zur ersten Öffnung 8. Die zweite Öffnung 10 ist zu dem zweiten Kanal 37 so ausgerich tet, dass diese in den zweiten Kanal 37 mündet. Figures 2 and 4 - 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.
Figuren 2 und 4 - Der Kolben 3 ist aus einer mit Figur 2 dargestellten Schließstellung I gegen die Wirkung der Federkräfte der Feder 5 in eine mit Figur 4 dargestellte Öffnungsstellung II axial beweglich. Figures 2 and 4 - The piston 3 is axially movable from a closed position I shown in Figure 2 against the action of the spring forces of the spring 5 in an open position II shown in Figure 4.
Figur 2 - Der Kolben 3 ist in der Schließstellung I durch die Wrkung der Feder 5 axial gegen den Ventilsitz 17 vorgespannt und verschließt in dieser Position die erste Öffnung 8 mit dem Kolbenboden 7. Die Schließstellung I ist dementsprechend die Position des Kolbenbodens 7 zum Ventilsitz 17 im geschlossenen Zustand des Ventils 3. Dabei liegt die Ringfläche 29 dich tend an dem Ventilsitz 17 an. Die zweite Öffnung 10 ist in der Schließstellung I des Kolbens 3 größtenteils durch den Kolbenmantel 9 verschlossen, wobei jedoch eine für Strömungsmittel durchlässige spaltförmige Durchgangsöffnung 12 verbleibt. Die spaltförmige Durchgangsöff nung 12 ist dabei durch einen Mantelabschnitt des Kolbenmantels 9 bzw. durch einen Über gangsabschnitt 11 des Kolbens 3 sowie einen Rand des Ventilgehäuses 2 an der zweiten Öff nung 10 begrenzt. Der der ersten Öffnung 8 am offenen Ende 19 des Ventilgehäuses 2 axial gegenüberliegende offene Querschnitt ist durch den Kolben 3 ebenfalls verschlossen. Dabei ist ein zwischen dem Kolbenmantel 9 und dem Ventilgehäuse 2 aufgrund geringeren Radial spiels ausgebildeter Ringsspalt (Leckspalt) nicht berücksichtigt. In der Schließstellung I ist ein Ringkanal 13 zwischen dem Kolben 3 und dem Ventilgehäuse 2 ausgebildet, der durch den Übergangsabschnitt 11 am Kolben 3 und einem Abschnitt des Ventilgehäuses 2 begrenzt wird. Der Abschnitt 15 erstreckt sich von dem Ventilsitz 17 aus zum Hülsenmantel des Ventil gehäuses 2. Der Ringkanal 13 ist an der spaltförmigen Durchgangsöffnung 12 offen und an- sonsten umlaufend geschlossen. Figure 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. In the closed position I of the piston 3, 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. In the closed position I is 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.
In der Schließstellung I ist die durch den Druck eines Strömungsmittels im ersten Kanal 36 auf die Fläche 31 des Kolbenbodens ausgeübte Kraft kleiner oder gleich einer im Inneren des Druckausgleichsventils 1 auf die Rückseite des Kolbenbodens 7 wirkenden Gegenkraft. Die Gegenkraft ist ein Ergebnis der durch einen Gegendruck im Inneren des Druckausgleichsven tils 1 erzeugten Kraft an der Rückseite des Kolbenbodens 7 und vornehmlich der auf die Rückseite des Kolbenbodens 7 ausgeübten Federkraft der zwischen dem Kolbenboden 7 und dem Stützelement 4 eingespannten Feder 5. Figur 4 - Wenn der Druck im ersten Kanal 36 soweit ansteigt, dass die dadurch auf die Flä che 31 des Kolbenbodens 7 die Gegenkraft übersteigt, bewegt sich der Kolben 3 axial in Rich tung des Stützelements 4 in die Öffnungsstellung II und gibt den Ventilsitz 17 frei. Zugleich wird rückseitig des Kolbenbodens 7 befindliches Strömungsmittel über die Drosselöffnungen 33 aus dem Inneren des Druckausgleichsventils 1 verdrängt und werden die axiale Bewegung bzw. eventuelle axiale Schwingbewegungen des Kolbens 3 gedämpft. Das Strömungsmittel strömt durch einen so frei gegebenen Durchlass 18 über die erste Öffnung 8 durchs Innere des Druckausgleichsventils 1 über die zweite Öffnung 10 in den zweiten Kanal 37. In the closed position I, 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. At the same time, 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.
Bezuqszeichenliste Reference list
Figure imgf000010_0001
Figure imgf000010_0001

Claims

Patentansprüche Claims
1. Ventil (20) mit einem Ventilgehäuse (2), wenigstens einem Kolben (3), mindestens ei nem Stützelement (4) und zumindest einer Feder (5), mit den Merkmalen: 1. Valve (20) with a valve housing (2), at least one piston (3), at least one support element (4) and at least one spring (5), with the features:
der Kolben (3) und das Ventilgehäuse (2) sind zueinander koaxial auf einer ge dachten Ventilachse (6) angeordnet, wobei die Ventilachse (6) in eine erste axiale Richtung sowie in eine zur ersten axialen Richtung entgegengesetzte zweite axiale Richtung axial ausgerichtet ist, the piston (3) and the valve housing (2) are arranged coaxially with one another on a ge-intended valve axis (6), the valve axis (6) being axially aligned in a first axial direction and in a second axial direction opposite to the first axial direction,
der Kolben (3) ist gegen Federkräfte der Feder (5) axial beweglich in dem Ventil gehäuse (2) aufgenommen, wobei die Feder (5) zumindest in die erste axiale Rich tung an dem Stützelement (4) und in die zweite axiale Richtung an dem Kolben (3) abgestützt ist, The piston (3) is axially movable in the valve housing (2) against spring forces of the spring (5), the spring (5) at least in the first axial direction on the support element (4) and in the second axial direction the piston (3) is supported,
das Stützelement (4) ist an dem Ventilgehäuse (2) abgestützt, the support element (4) is supported on the valve housing (2),
der Kolben (3) weist einen Kolbenboden (7) und einen Kolbenmantel (9) auf, das Ventilgehäuse (2) ist mit einer strömungsmitteldurchlässigen ersten Öffnung (8) versehen, welche durch den Kolbenboden (7) verschließbar ist, the piston (3) has a piston crown (7) and a piston skirt (9), the valve housing (2) is provided with a fluid-permeable first opening (8) which can be closed by the piston crown (7),
der Kolben (3) ist über den Kolbenmantel (9) in dem Ventilgehäuse (2) geführt da bei axial gegen die Feder (5) in Richtung des Stützelementes (4) verschiebbar, wobei das Ventilgehäuse (2) an einem axial von der ersten Öffnung (8) entfernten En de (19) wenigstens eine für die Strömungsmittel durchlässige Drosselöffnung (33) aufweist, welche durch eine Drosselscheibe (32) begrenzt ist und wobei die Drossel scheibe (32) als separates Bauteil zwischen dem Kolben (3) und dem Stützelement (4) angeordnet ist. the piston (3) is guided over the piston skirt (9) in the valve housing (2) since it is axially displaceable against the spring (5) in the direction of the support element (4), the valve housing (2) being axially at the first opening (8) removed En de (19) has at least one throttle opening (33) which is permeable to the fluid and which is delimited by a throttle disc (32) and wherein the throttle disc (32) as a separate component between the piston (3) and the support element (4) is arranged.
2. Ventil nach Anspruch 1 , in dem die Drosselöffnung (33) als wenigstens ein zwischen dem Ventilgehäuse (2) und der Drosselscheibe (32) für die Strömungsmittel durchläs siger Drosselspalt ausgebildet ist. 2. Valve according to claim 1, in which the throttle opening (33) is designed as at least one between the valve housing (2) and the throttle disc (32) for the fluid permeable throttle gap.
3. Ventil nach Anspruch 1 oder 2, in dem die Drosselöffnung (33) in Umfangsrichtung um die Ventilachse (6) gesehen durch Vorsprünge (28) des Stützelements (4) begrenzt ist, wobei das Stützelement (4) über die Vorsprünge (28) an dem Ventilgehäuse (2) abge stützt ist und wobei zwischen den Vorsprüngen (28) in Umfangsrichtung um die Ven tilachse (6) Lücken (16) ausgebildet sind. 3. Valve according to claim 1 or 2, in which the throttle opening (33) in the circumferential direction around the valve axis (6) is limited by projections (28) of the support element (4), the support element (4) via the projections (28) on the valve housing (2) is supported abge and gaps (16) are formed between the projections (28) in the circumferential direction around the Ven tilachse (6).
4. Ventil nach Anspruch nach Anspruch 1 , in dem die Drosselscheibe (32) an dem Stüt zelement (4) befestigt ist. 4. Valve according to claim 1, in which the throttle disc (32) on the support zelement (4) is fixed.
5. Ventil nach Anspruch 1 , 2, 3 oder 4, in dem das Stützelement (4) an dem Ventilgehäu se (2) befestigt ist, wobei das Stützelement (4) mit wenigstens einem Durchgangsloch (22) versehen ist, und wobei die Drosselscheibe (32) formschlüssig in das Durch gangsloch (22) eingreift. 5. Valve according to claim 1, 2, 3 or 4, in which the support element (4) on the Ventilgehäu se (2) is fixed, wherein the support element (4) is provided with at least one through hole (22), and wherein the throttle disc (32) positively engages in the through hole (22).
6. Ventil nach Anspruch 1 , 2, 3 oder 4, in dem die Feder (5) axial an der Drosselscheibe (32) anliegt sowie über die Drosselscheibe (32) radial in dem Ventilgehäuse (2) geführt und zentriert ist. 6. Valve according to claim 1, 2, 3 or 4, in which the spring (5) rests axially on the throttle disk (32) and is guided and centered radially in the valve housing (2) via the throttle disk (32).
7. Ventil nach Anspruch 1 , in dem das Stützelement (4) radial außen in Umfangsrichtung wenigstens zwei Vorsprünge (28) aufweist, welche in einer Umfangsnut (21) des Ven tilgehäuses (2) formschlüssig verrastet sind, wobei zwischen den Vorsprüngen (28) in Umfangsrichtung um die Ventilachse (6) Lücken (16) ausgebildet sind, welche durch die Drosselscheibe (32) zumindest teilweise axial bedeckt sind. 7. Valve according to claim 1, in which the support element (4) has radially outside in the circumferential direction at least two projections (28) which are positively locked in a circumferential groove (21) of the Ven tilgehäuses (2), between the projections (28) gaps (16) are formed in the circumferential direction around the valve axis (6) and are at least partially axially covered by the throttle disc (32).
8. Ventil nach Anspruch 7, in dem die Lücken (16) durch die Drosselscheibe (32) nur so teilweise bedeckt sind, dass jeweils zwischen zwei Vorsprüngen (28) eine für Strö mungsmittel durchlässige Drosselöffnung (33) verbleibt. 8. Valve according to claim 7, in which the gaps (16) are only partially covered by the throttle disc (32) in such a way that between two projections (28) a flow opening (33) which is permeable to flow medium remains.
9. Vorrichtung (30) zur Regelung von Drücken eines Strömungsmittels in einem Fahr zeuggetriebe, wobei die Vorrichtung (30) aus einem Abschnitt eines Getriebebauteils (35), aus zumindest einem ersten Kanal (36) und einem zweiten Kanal (37) sowie aus dem als ein Druckausgleichsventil (1) ausgebildeten Ventil (20) nach einem der vor hergehenden Ansprüche gebildet ist, wobei der erste Kanal (36) in dem Abschnitt des Getriebebauteils (35) zu der ersten Öffnung (8) führt und eine für Strömungsmittel durchlässige zweite Öffnung (10) des Ventilgehäuses (2) in den zweiten Kanal (37) mündet, wobei die zweite Öffnung (10) quer zu den axialen Richtungen ausgerichtet und von dem Kolbenmantel (9) verschließbar ist. 9. Device (30) for regulating pressures of a fluid in a driving gearbox, the device (30) comprising a section of a gearbox component (35), at least a first channel (36) and a second channel (37) and from the formed as a pressure compensation valve (1) according to any one of the preceding claims, wherein the first channel (36) in the section of the transmission component (35) leads to the first opening (8) and a second opening permeable to fluid (10) of the valve housing (2) opens into the second channel (37), the second opening (10) being aligned transversely to the axial directions and being closable by the piston skirt (9).
10. Vorrichtung (30) zur Regelung von Drücken nach Anspruch 9, in welchem der Kolben (3) gegen die Federkräfte der Feder (5) aus einer Schließstellung (I) in eine axial von der Schließstellung (I) entfernte Öffnungsstellung (II) axial beweglich in dem Ventilge häuse (2) geführt ist, wobei in der Schließstellung (I) des Kolbens (3) die erste Öffnung (8) mittels des Kolbens (3) verschlossen ist, und wobei die erste Öffnung (8) in der Öffnungsstellung (II) des Kolbenbodens (7) durch den Kolben (3) durchlässig freigege ben ist, wobei in der Öffnungsstellung (II) über die erste Öffnung (8) und die zweite Öffnung (10) ein für die Strömungsmittel freier Durchlass (18) von dem ersten Kanal (36) durch das Ventilgehäuse (2) zu dem zweiten Kanal (37) gebildet ist. 10. The device (30) for controlling pressures according to claim 9, in which the piston (3) against the spring forces of the spring (5) from a closed position (I) in an axially from the closed position (I) distant open position (II) axially is movably guided in the Ventilge housing (2), wherein in the closed position (I) of the piston (3) the first opening (8) is closed by means of the piston (3), and wherein the first opening (8) in the The open position (II) of the piston crown (7) is permeable ben by the piston (3), in the open position (II) via the first opening (8) and the second opening (10) a passage (18) free for the fluid from the first channel (36) through the valve housing (2) to the second channel (37).
PCT/DE2019/101045 2018-12-06 2019-12-05 Valve and device for the control of pressures of a flow medium in a vehicle transmission with a valve WO2020114560A1 (en)

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DE102018131098.6A DE102018131098A1 (en) 2018-12-06 2018-12-06 Valve and device for regulating pressures of a fluid in a vehicle transmission with a valve
DE102018131098.6 2018-12-06

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DE102019120225A1 (en) * 2019-07-26 2021-01-28 Schaeffler Technologies AG & Co. KG Valve and device for regulating pressures of a fluid with the valve and device for securing the valve in the transmission component
DE102021107639A1 (en) 2021-03-26 2022-09-29 Mann+Hummel Gmbh Water separator with a throttling element, use of a water separator and fuel cell system with a water separator

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Publication number Priority date Publication date Assignee Title
DE1810550A1 (en) * 1968-11-23 1970-06-04 Ernst Heinkel Ag Cone seat valve
DE3120606A1 (en) * 1981-05-23 1983-07-28 Bayerische Motoren Werke AG, 8000 München Valve for pressure limitation in hydraulic systems
DE19505129A1 (en) * 1995-02-16 1996-08-22 Rexroth Mannesmann Gmbh Servo=assisted pressure limitation valve
FR2817014A1 (en) * 2000-11-17 2002-05-24 Montage Auto Camions Soc D Automobile de-gassing valve mounted on gaseous mixture conduit comprises body with bore in which piston slides between positions which obstruct and free body openings connecting bore to outside
EP1382893A1 (en) 2002-07-12 2004-01-21 TRW Automotive Pumps S.r.l. Ball valve for hydraulic circuits
DE102008057393A1 (en) * 2008-11-14 2010-05-20 Schaeffler Kg Check valve in cartridge design
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ITRE20110027A1 (en) * 2011-04-19 2012-10-20 Renato Besacchi NON-RETURN VALVE FOR OILS AND FLUIDS IN GENERAL.
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DE102014213751A1 (en) * 2014-05-23 2015-11-26 Continental Teves Ag & Co. Ohg valve assembly
CN204153230U (en) * 2014-08-12 2015-02-11 常州福磊石材有限公司 Anti-plugging one-way throttle valve

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