WO2021013292A1 - Piston annulaire en plusieurs parties pour un cylindre récepteur, permettant l'actionnement hydraulique d'un embrayage ou d'un frein - Google Patents

Piston annulaire en plusieurs parties pour un cylindre récepteur, permettant l'actionnement hydraulique d'un embrayage ou d'un frein Download PDF

Info

Publication number
WO2021013292A1
WO2021013292A1 PCT/DE2020/100565 DE2020100565W WO2021013292A1 WO 2021013292 A1 WO2021013292 A1 WO 2021013292A1 DE 2020100565 W DE2020100565 W DE 2020100565W WO 2021013292 A1 WO2021013292 A1 WO 2021013292A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
piston body
fluid pressure
actuation system
fluidic actuation
Prior art date
Application number
PCT/DE2020/100565
Other languages
German (de)
English (en)
Inventor
Paul Gehrke
Michel Jacky
Fadil Mahracha
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 WO2021013292A1 publication Critical patent/WO2021013292A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/083—Actuators therefor
    • 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
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/46—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings
    • F16J15/48—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings influenced by the pressure within the member to be sealed
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84

Definitions

  • the invention relates to a fluidic actuation system for fluidically actuating at least one clutch and / or braking device, with an annular piston which delimits a fluid pressure space in an annular space.
  • a concentric slave cylinder which has a spring cup and a pressure divider, which is characterized by a plurality of compression springs arranged on the outer circumference of the slave cylinder for applying a preload to a release bearing that can be actuated by the slave cylinder are.
  • a slave cylinder (CSC) is known, in particular for a hydraulic release system of a friction clutch of a motor vehicle, with a substantially concentric slave cylinder housing with a longitudinal axis, wel ches has an annular space to form an annular pressure chamber , in which an annular piston, which is provided with a seal on the pressure chamber side, is guided axially displaceably, the annular piston acting on a release bearing and at least one elastic and / or resilient element is arranged on the slave cylinder housing in the direction of the release bearing, which compensates for tolerances Nem stop of the slave cylinder housing for the release bearing in a rear end position (minimum extension) of the annular piston.
  • a hybrid module for a drive train of a motor vehicle is known from the German Offenle application DE 10 2017 127 102 A1.
  • the object of the invention is to simplify the production of a fluidic actuation system for the fluidic actuation of at least one clutch and / or brake device, with an annular piston which delimits a fluid pressure space in an annular space.
  • the object is achieved in a fluidic actuation system for fluidic actuation of at least one clutch and / or brake device, with an annular piston that delimits a fluid pressure chamber in an annular space, in that the annular piston comprises at least one first piston body and a second piston body, which is its The position relative to the first piston body is changed when fluid pressure is applied to the fluid pressure space so that a sealing gap between the second piston body and a housing surface is minimized.
  • the annular piston is preferably a slave piston in a concentric slave cylinder.
  • the annular piston in the claimed concentric actuation system preferably has a relatively large diameter, which is in particular fifty to one hundred millimeters in size.
  • the preferably two-part design of the annular piston with a first piston body and a second piston body has proven to be particularly advantageous.
  • a relatively large gap between the annular piston and the housing surface that results from an undesired gap extrusion can be minimized. This advantageously prevents an undesired failure of a seal associated with the annular piston.
  • a preferred exemplary embodiment of the fluidic actuation system is characterized in that the first piston body is designed as a radially inner ring body and the second piston body is designed as a radially outer ring body.
  • the two Kol benk analyses are preferably designed as a closed ring body.
  • piston bodies have sliding surfaces with which the piston bodies bear against one another and with which the piston bodies slide against one another when fluid pressure is applied to the fluid pressure chamber. It is particularly advantageous for only the second piston body to slide relative to the first piston body. As a result of this desired sliding movement under the application of fluid pressure, one of the piston bodies, in particular the radially outer ring body, which represents the second piston body, so that the sealing gap between the second piston body and the housing surface is minimized.
  • Another preferred embodiment of the fluidic actuation system is characterized in that the sliding surfaces, viewed in a cross section through the piston bodies, are arranged at an angle obliquely to a longitudinal axis, parallel to which the annular piston can be moved back and forth.
  • the longitudinal axis defines an axial direction of movement of the annular piston when the fluidic actuation system is in operation.
  • Axial means in the direction of or parallel to the longitudinal axis of the annular piston.
  • Analog means radially transverse to the longitudinal axis.
  • the angle between the sliding surfaces and the longitudinal axis is forty-five degrees, for example. Depending on the design, the angle can be larger or smaller than forty-five degrees to set a desired expansion behavior of one of the piston bodies, in particular the second piston body, which is designed as a radially outer ring body, in terms of size and / or strength.
  • the second piston body is formed from an elastic mate rial that enables a desired deformation when the second piston body changes its position relative to the first piston body when fluid pressure is applied to the fluid pressure chamber.
  • the elastic material makes it possible for the second piston body to expand sufficiently relative to the first piston body to minimize the sealing gap.
  • the second piston body is advantageously formed from a plastic material.
  • Both piston bodies can be formed from a plastic material at a particularly low cost.
  • the piston bodies are manufactured from the plastic material, for example, in large numbers at low cost using an injection molding process.
  • the two piston bodies are preferably not made of the same material.
  • the first piston body is made of a plastic material reinforced with glass fibers, for example.
  • the second piston body is preferably formed from an unreinforced Kunststoffma material in order to enable the desired elastic deformation of the second piston body during operation.
  • Another preferred exemplary embodiment of the fluidic actuation system is characterized in that the two piston bodies jointly delimit a receiving space for a seal.
  • the seal is used in a manner known per se to seal the fluid pressure chamber.
  • a further preferred exemplary embodiment of the fluidic actuation system is characterized in that the receiving space for captively receiving the seal is designed in the manner of a dovetail.
  • the dovetail-like Ausulate tion serves to illustrate an advantageous embodiment of a form-locking connection between the seal and the annular piston.
  • Another preferred exemplary embodiment of the fluidic actuation system is characterized in that the first piston body has a circumferential shoulder for mounting the annular piston on an actuation bearing.
  • the circumferential shoulder advantageously prevents the annular piston from dipping too deep into the fluid pressure chamber.
  • the second piston body has a potential contact surface facing the housing surface with depressions radially on the outside, in order to reduce the size of the potential contact surface.
  • the depressions are designed, for example, as annular groove-like depressions.
  • contact between the second piston body and the housing surface during operation of the fluidic actuation system is undesirable due to the associated friction.
  • the effects of the friction between the second piston body and the housing surface can be kept low by reducing the potential contact surface.
  • the invention also relates to an annular piston, a piston body and / or a seal for a previously described fluidic actuation system. The parts mentioned can be traded separately or together in an assembly unit.
  • the invention optionally also relates to a method for assembling a fluidic actuation system described above. During assembly, in particular the annular piston with the two piston bodies and the seal is combined in one assembly unit.
  • the invention optionally also relates to a kit for a previously described fluidic actuation system.
  • the fluidic actuation system is used, for example, in a hybrid module for a drive train of a motor vehicle, as is described in the German patent application DE 10 2017 127 102 A1.
  • FIG. 1 shows a schematic representation of a fluidic actuation system for fluidic actuation of a clutch and / or brake device with an annular piston in longitudinal section;
  • FIG. 2 shows the enlarged illustration of a section II from FIG. 1;
  • FIG. 3 shows a representation similar to that in FIG. 2 before the application of a
  • FIG. 4 shows the same representation as in FIG. 3 after the application of the
  • a fluidic actuation system 1 for fluidic actuation of a clutch and / or brake device 2 is shown in a simplified manner.
  • the fluidic actuation system 1 is preferably operated with a hydraulic medium and can therefore also be referred to as a hydraulic actuation system 1.
  • a coupling and / or braking device 2 indicated by a rectangle is preferably arranged in a drive train of a motor vehicle.
  • the fluidic actuation system 1 comprises a ring cylinder 3, in which a ring piston 4 with a longitudinal axis 17 is axially movable back and forth.
  • the term axial refers to the longitudinal axis 17 of the annular piston 4, which is preferably rotationally symmetrical.
  • Axial means in the direction of or parallel to the longitudinal axis 17.
  • Analog means radially transversely to the longitudinal axis 17.
  • the annular piston 4 is coupled to the clutch and / or braking device 2 via an actuation bearing 5, which is likewise only indicated.
  • actuation bearing 5 On its side facing away from the actuating bearing 5, a seal 6 is assigned to the annular piston 4 in a manner known per se.
  • the seal 6 delimits a fluid pressure chamber 7 with the annular piston 4 in an annular space 8 of the annular cylinder 3.
  • the annular cylinder 3, the annular piston 4 and the actuating bearing 5 together include a central through hole 9. Through the central through hole 9 extends, for example, at least one shaft which is used in the drive train of the motor vehicle to transmit rotation.
  • the ring cylinder 3 with the ring piston 4 is also referred to as the 10 concentric slave cylinder.
  • a sealing gap 13 results radially on the outside between the annular piston 4 and the annular cylinder 3 due to the design.
  • the annular piston 4 is designed in two parts with a first piston body 11 and a second piston body 12.
  • the geometry of the two piston bodies 11 and 12 is designed in such a way that when the fluid pressure chamber 7 is pressurized, the second piston body 12 is pressed outwards in a radial direction and closes the sealing gap 13, as can be seen from a synopsis of FIGS. 3 and 4 .
  • the first piston body 11 is designed as a radially inner ring body 11.
  • the radially inner annular body 11 comprises a circumferential shoulder 19 which, as can be seen in FIG. 2, serves to mount the annular piston 4 on the actuating bearing 5.
  • the umlau Fende paragraph 19 is formed radially on the outside of the first piston body 11.
  • Radially inwardly, the first piston body 11 has a circumferential shoulder 26 through which the annular piston 4 is axially movable back and forth in or on the annular cylinder 3.
  • the circumferential shoulder 26 advantageously prevents the annular piston 4 from dipping too deep into the fluid pressure chamber 7.
  • the second piston body 12 is designed as a radially outer ring body.
  • the two piston bodies 11 and 12 designed as ring bodies have sliding surfaces 15, 16 facing one another.
  • the two piston bodies 1 1, 12 are with their sliding surfaces 15, 16 in sliding contact.
  • the sliding surfaces 15, 16 run at an angle obliquely upwards.
  • the angle between the sliding surfaces 15, 16 and the longitudinal axis (17 in Figure 1) has a size of forty-five degrees in the illustrated embodiment.
  • the size of the angle can advantageously be used to set how far and how lightly or strongly the second piston body 12 expands relative to the first piston body 11 when the fluid pressure space 7 is acted upon by fluid pressure.
  • the radially outer ring body, which the second piston benkMech 12 represents pressed in the radial direction outward and tet expanded.
  • FIG. 3 shows that the detail from Figure 2 is shown before the fluid pressure chamber 7 is applied.
  • the sealing gap 13 is relatively large.
  • FIG. 4 shows that the second piston body 12 has been displaced radially outward relative to the first piston body 11 by the fluid pressure in the fluid pressure chamber 7, so that the sealing gap 13 is minimized.
  • the two-part design of the annular piston 4 particularly advantageously enables the use of plastic materials for positioning the annular piston 4, specifically particularly advantageously even with large piston diameters, for example fifty to one hundred millimeters.
  • a plastic injection molding process can advantageously be used to position the annular piston 4, in particular the piston body 11 and / or 12. Filigree seal rings, as used in conventional annular pistons, can be omitted.
  • FIG 2 it can be seen that the two piston bodies 1 1 and 12 together define a receiving space 18 for the seal 6.
  • the receiving space 18 is designed to lose the seal 6 dovetail-like. The resulting form fit prevents the preassembled seal 6 from coming loose before or during the assembly of the annular piston 4.
  • the seal 6 in the receiving space 18 prevents fluid from escaping from the fluid pressure space 7 between the sliding surfaces 15, 16.
  • a potential contact surface 20 of the second piston body 12, which faces the housing surface 14, is equipped with annular groove-like depressions 21 to 24.
  • the groove-like depressions 21 to 24 serve to reduce the potential contact surface 20. This minimizes any friction that may occur when the second piston body 12 comes into contact with the housing surface 14 with its potential contact surface 20.
  • the two piston bodies 11, 12 are advantageously pre-assembled with the seal 6 in an assembly unit 25. This assembly unit 25 is then assembled in the ring cylinder 3 during assembly of the fluid actuation system 1.

Abstract

L'invention concerne un système d'actionnement fluidique permettant l'actionnement fluidique d'au moins un dispositif d'embrayage et/ou de freinage, le système étant pourvu d'un piston annulaire qui délimite une chambre de pression de fluide dans un espace annulaire. L'objet de l'invention est de simplifier la fabrication du système d'actionnement fluidique. À cet effet, le piston annulaire comprend au moins un premier corps (11) de piston et un deuxième corps (12) de piston qui modifie sa position par rapport au premier corps (11) de piston lorsque la chambre de pression de fluide (7) est soumise à l'effet d'une pression de fluide, de sorte qu'une fente d'étanchéité (13) entre le deuxième corps (12) de piston et une surface de carter (14) est réduite au minimum.
PCT/DE2020/100565 2019-07-25 2020-06-30 Piston annulaire en plusieurs parties pour un cylindre récepteur, permettant l'actionnement hydraulique d'un embrayage ou d'un frein WO2021013292A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019120072.5 2019-07-25
DE102019120072.5A DE102019120072A1 (de) 2019-07-25 2019-07-25 Fluidisches Betätigungssystem

Publications (1)

Publication Number Publication Date
WO2021013292A1 true WO2021013292A1 (fr) 2021-01-28

Family

ID=71614660

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2020/100565 WO2021013292A1 (fr) 2019-07-25 2020-06-30 Piston annulaire en plusieurs parties pour un cylindre récepteur, permettant l'actionnement hydraulique d'un embrayage ou d'un frein

Country Status (2)

Country Link
DE (1) DE102019120072A1 (fr)
WO (1) WO2021013292A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022113925A1 (de) 2022-06-02 2023-12-07 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit zweiteiligen Ringkolben für ein hydraulisches Ausrücksystem sowie Kupplungs- oder Bremsanordnung mit dem Nehmerzylinder

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4129370A1 (de) * 1991-09-04 1993-03-11 Fichtel & Sachs Ag Hydraulisch betaetigbarer ausruecker mit stuetzring und stuetzschulter
DE19614385A1 (de) * 1996-03-04 1997-09-11 Schaeffler Waelzlager Kg Dichtung für einen Ringkolben einer hydraulischen Kupplungs-Ausrückvorrichtung
FR2772443A1 (fr) * 1997-12-11 1999-06-18 Valeo Recepteur hydraulique de commande d'embrayage notamment pour vehicule automobile
FR2780122A1 (fr) * 1998-06-19 1999-12-24 Valeo Dispositif de debrayage a commande hydraulique
DE102011009022A1 (de) 2010-01-27 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Konzentrischer Nehmerzylinder (CSC)
DE102012212296A1 (de) * 2011-08-05 2013-02-07 Schaeffler Technologies AG & Co. KG Nehmerzylinder
DE102011081298A1 (de) 2011-08-22 2013-02-28 Schaeffler Technologies AG & Co. KG Nehmerzylinder (CSC)
EP2905495A1 (fr) * 2014-02-06 2015-08-12 Schaeffler Technologies AG & Co. KG Agencement d'étanchéification
DE102017127102A1 (de) 2017-06-16 2018-12-20 Schaeffler Technologies AG & Co. KG Hybridmodul für einen Antriebsstrang eines Kraftfahrzeugs, Hybrid-Einheit und Verfahren zur Montage eines Hybridmoduls
DE102017121807A1 (de) * 2017-06-27 2018-12-27 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit Taumelausgleich im Dichtungsträger
DE102018111760A1 (de) * 2018-05-16 2019-11-21 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit geteiltem Dichtringträger
DE102018129126A1 (de) * 2018-11-20 2020-05-20 Schaeffler Technologies AG & Co. KG Ausrücklageranordnung

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4129370A1 (de) * 1991-09-04 1993-03-11 Fichtel & Sachs Ag Hydraulisch betaetigbarer ausruecker mit stuetzring und stuetzschulter
DE19614385A1 (de) * 1996-03-04 1997-09-11 Schaeffler Waelzlager Kg Dichtung für einen Ringkolben einer hydraulischen Kupplungs-Ausrückvorrichtung
FR2772443A1 (fr) * 1997-12-11 1999-06-18 Valeo Recepteur hydraulique de commande d'embrayage notamment pour vehicule automobile
FR2780122A1 (fr) * 1998-06-19 1999-12-24 Valeo Dispositif de debrayage a commande hydraulique
DE102011009022A1 (de) 2010-01-27 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Konzentrischer Nehmerzylinder (CSC)
DE102012212296A1 (de) * 2011-08-05 2013-02-07 Schaeffler Technologies AG & Co. KG Nehmerzylinder
DE102011081298A1 (de) 2011-08-22 2013-02-28 Schaeffler Technologies AG & Co. KG Nehmerzylinder (CSC)
EP2905495A1 (fr) * 2014-02-06 2015-08-12 Schaeffler Technologies AG & Co. KG Agencement d'étanchéification
DE102017127102A1 (de) 2017-06-16 2018-12-20 Schaeffler Technologies AG & Co. KG Hybridmodul für einen Antriebsstrang eines Kraftfahrzeugs, Hybrid-Einheit und Verfahren zur Montage eines Hybridmoduls
DE102017121807A1 (de) * 2017-06-27 2018-12-27 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit Taumelausgleich im Dichtungsträger
DE102018111760A1 (de) * 2018-05-16 2019-11-21 Schaeffler Technologies AG & Co. KG Nehmerzylinder mit geteiltem Dichtringträger
DE102018129126A1 (de) * 2018-11-20 2020-05-20 Schaeffler Technologies AG & Co. KG Ausrücklageranordnung

Also Published As

Publication number Publication date
DE102019120072A1 (de) 2021-01-28

Similar Documents

Publication Publication Date Title
DE10205177B4 (de) Hydraulisches System
EP2193282B1 (fr) Elément hydraulique
DE4339652C2 (de) Hydraulisch betätigbare Ausrücker-Nehmerzylinder für eine Kraftfahrzeug-Reibungskupplung
DE102007028490A1 (de) Koppler zur Hubübertragung mittels Scherkraft, Injektor, sowie Verfahren zur Hubübertragung
DE10327437A1 (de) Hydraulisches System
DE19716473C2 (de) Zentralausrücker für eine hydraulische Kupplungsbetätigung
WO2018001554A1 (fr) Cylindre émetteur, en particulier pour un dispositif hydraulique d'actionnement d'embrayage dans des véhicules
DE102015220819A1 (de) Kolben-Zylinder-Einheit
DE3816608A1 (de) Hydraulikzylinder
DE102019208445A1 (de) Kraftstoff-Hochdruckpumpe
WO2021013292A1 (fr) Piston annulaire en plusieurs parties pour un cylindre récepteur, permettant l'actionnement hydraulique d'un embrayage ou d'un frein
DE102015217664A1 (de) Kolben-Ausrücker
EP3177844B1 (fr) Maître-cylindre comprenant une douille de guidage pour une lèvre d'étanchéité du système de dilatation
DE102008024163A1 (de) Verbundkolben für ein Kraftfahrzeuggetriebe
DE102011087103A1 (de) Geberzylinder
DE102017121807A1 (de) Nehmerzylinder mit Taumelausgleich im Dichtungsträger
DE10193440B3 (de) Vorrichtung zur Verbindung eines Hebels mit dem Kolben eines Schaltzylinders
DE102013221845A1 (de) Kolben-Zylinder-Einheit
DE102014217648A1 (de) Nehmerzylinder
WO2017174064A1 (fr) Garniture d'étanchéité pour ensemble cylindre-piston
DE102017106105A1 (de) Dichtung für eine Kolben-Zylinder-Anordnung für eine Kupplung
EP1857699B1 (fr) Cylindre recépteur
DE102011016985A1 (de) Zentralausrücker zur Betätigung einer Reibungskupplung
DE102014216619A1 (de) Nehmerzylinder zur Betätigung einer Kupplung, Kupplung für ein Kraftfahrzeug und Kraftfahrzeug mit entsprechender Kupplung
DE102015215958A1 (de) Geberzylinder mit zwei Kolben mit stirnseitigen Dichtungen

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 20740228

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 20740228

Country of ref document: EP

Kind code of ref document: A1