EP2630383A1 - Embrayage ou frein à friction actionné par un fluide sous pression - Google Patents

Embrayage ou frein à friction actionné par un fluide sous pression

Info

Publication number
EP2630383A1
EP2630383A1 EP11770801.6A EP11770801A EP2630383A1 EP 2630383 A1 EP2630383 A1 EP 2630383A1 EP 11770801 A EP11770801 A EP 11770801A EP 2630383 A1 EP2630383 A1 EP 2630383A1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
friction clutch
brake according
clutch
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP11770801.6A
Other languages
German (de)
English (en)
Inventor
Matthias Glomm
Rainer Bittermann
Thomas HÄSEKER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Stromag GmbH
Original Assignee
GKN Stromag AG
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 GKN Stromag AG filed Critical GKN Stromag AG
Publication of EP2630383A1 publication Critical patent/EP2630383A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/583—Diaphragm-springs, e.g. Belleville
    • 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
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs

Definitions

  • the invention relates to a fluid-actuated friction clutch or brake with an axially movable pressure piston assembly and at least one acted upon by the pressure piston assembly friction disc.
  • Such a friction clutch is known from the KHM 800/4 Stromag AG.
  • the known friction clutch has, as a pressure piston arrangement, a pressure piston which acts on two friction disks of an output-side clutch hub.
  • the friction clutch is hydraulically operated.
  • the pressure piston is associated with a pressure chamber within a coupling housing, which is acted upon by hydraulic oil. Hydraulic loading leads to axial movement of the pressure piston and consequently to a frictional engagement with the friction plates, whereby the desired torque transmission is achieved.
  • the object of the invention is to provide a friction clutch or brake of the type mentioned, which allows a smooth switching operation.
  • the pressure piston arrangement has at least two pistons, which are the pressure-dependent stepped at least one friction disc deliverable successively.
  • the pistons of the pressure piston arrangement are therefore connected in series, by first of all the one piston acting on the at least one friction disc and then the at least one second piston is switched on to the complementary effect on the at least one friction disc. This makes it possible to realize a smooth switching operation for the clutch or brake. Because with the connection of the first piston is a switching on of the clutch or brake with a relatively low torque. The connection of the second piston then causes a stepped torque increase.
  • the solution according to the invention is particularly suitable for the soft connection of drives in machines for industry or for agriculture.
  • the solution according to the invention for connecting a main drive in a combine harvester is particularly suitable.
  • the soft connection ensures that a diesel engine supplying the main drive is at most slightly pressed in its speed. A stalling of the diesel engine in a clutch switching operation is reliably avoided. A relatively fast connection of the drive is made possible.
  • Mechanical means are particularly advantageously provided in order to achieve the multi-stage switching characteristic for the clutch or brake.
  • the piston is associated with a common pressure chamber for pressure medium, and at least one piston is associated with a counterforce applying retaining means which defines a higher pressure level for axial movement of the piston than for the at least one other piston.
  • the at least two pistons are preferably arranged coaxially with one another. Since the pistons have a common pressure chamber for pressurizing agent, they define a common piston end face, which is decisive for the pressure calculation.
  • at least one mechanical spring arrangement acting on the piston is provided as holding means. The spring arrangement acts as a counterforce when pressure is applied to the piston, so that the pressure acting on the piston must exceed the counterforce of the spring arrangement in order to be able to displace the piston.
  • the holding means comprises a piston bearing with respect to a storage for the at least one other piston increased coefficient of friction.
  • the increased coefficient of friction of the bearing acts as a counterforce with the same result as in the previously described embodiment. Because the piston is displaced only after overcoming the increased frictional force.
  • the spring arrangement comprises a plurality of distributed over a clutch or brake circumference arranged helical compression springs, which engage on a clutch or brake housing on the one hand and on a pressure chamber opposite the piston face on the other hand.
  • helical compression springs Depending on the available space, it is possible to arrange different helical compression springs radially and circumferentially offset from each other.
  • the piston assembly is formed by a pair of pistons with an inner piston and a radially surrounding the inner piston, annular outer piston, wherein the inner piston is slidably mounted in the outer piston.
  • a double piston is formed, wherein at a low pressure level initially one of the two pistons is displaceable. When the pressure level is increased, the second piston is also displaced.
  • the switch-on behavior according to the invention results in a substantial insensitivity to pressure fluctuations within an associated hydraulic system.
  • the stepped connection process is independent of a viscosity of the pressure medium and thus of the switching medium.
  • a sliding bearing between outer piston and inner piston which comprises a non-metallic slip ring band.
  • the slip ring band made of PTFE (polytetrafluoroethylene).
  • the additional slip ring band allows a non-metallic mounting of the inner piston in the outer bulb and consequently an improved linear guide for the inner piston.
  • the helical compression springs are supported on the outer bulb.
  • the inner piston thus causes the first switching stage with low torque and flat pressure characteristic, before then the additional connection of the outer bulb takes place at a higher pressure level.
  • Fig. 1 shows a sectional view of an embodiment of a
  • Fig. 2 shows an embodiment of a friction clutch according to the invention
  • FIG. 3 is a graph of a pressure / torque behavior of the friction clutch of FIG. 1 on the one hand and the friction clutch according to the invention of FIG. 2 on the other.
  • a hydraulically operated friction clutch 1 according to the invention according to FIG. 2 is intended to connect a main drive of a combine harvester. The main drive is illustrated by a dash-dotted drive shaft 7.
  • the friction clutch 1 according to the invention is described below in comparison to a friction clutch 1a according to FIG. 1, as is known from the prior art.
  • Identical components in the friction clutch 1 of FIG. 2 and in the prior art coupling 1 a of FIG. 1 are provided with identical reference numerals. Functional parts and sections, but different in their structural design, are provided with the same reference numerals with the addition of the letter a for the coupling of FIG. 1 of the prior art.
  • the known friction clutch 1 a of FIG. 1 will be explained first.
  • a pressure piston assembly 10a is arranged, which is hydraulically pressurized via a sealed pressure chamber 14a.
  • the pressure piston assembly 10a is axially movable displaceable relative to the clutch housing 2a, 3, 4 along a coupling axis of rotation K.
  • an elastic disc membrane 1 1 which is radially on the inside of the pressure piston assembly 10a and radially outside between the housing parts 2a and 3 is attached.
  • a pressure surface of the pressure piston assembly 10a acts on a first friction disc 5, which is axially movable, but non-rotatably connected to the drive hub 7.
  • a further friction disc 6 is arranged, which is also mounted axially movable and rotationally fixed on the drive hub 7.
  • a pressure plate 8 is arranged, which in a housing part 4 of the clutch housing 2a, 3, 4 rotatably, but is arranged axially movable.
  • the distance Disc 8 is associated with a return spring assembly 9, which presses the pressure plate 8 in the unloaded starting position against a housing stop of the housing part 3.
  • the pressure piston arrangement 10a also acts on a return spring arrangement 12, which presses a piston section of the pressure piston arrangement 10a carrying the piston pressure surface against the housing section 2a of the clutch housing and thus against the outer clamping of the disk membrane 11 in an unloaded starting position.
  • a return spring arrangement 12 presses a piston section of the pressure piston arrangement 10a carrying the piston pressure surface against the housing section 2a of the clutch housing and thus against the outer clamping of the disk membrane 11 in an unloaded starting position.
  • both friction plates 5 and 6 are released, since both the pressure piston assembly 10a through the disc diaphragm 1 1 and the return spring assembly 12 and the pressure plate 8 are held pressed by the compression spring assembly 9 in its left in Fig. 1 starting position.
  • the friction clutch 1 according to the invention is provided, which is identical with respect to the second clutch side, which is associated with the drive shaft 7 as the known friction clutch 1 a. To avoid repetition, reference is therefore made to the disclosure of the friction clutch 1a according to FIG.
  • the essential difference of the friction clutch 1 according to the invention according to FIG. 2 is that the coupling side on the left side of the coupling, namely the first coupling side, has a different construction.
  • the pressure piston assembly 10a is designed as a double piston by comprising an inner piston 10 and an outer piston 15.
  • the inner piston 10 is analogous to the pressure piston assembly 10a of FIG.
  • the second clutch side facing annular disc 6 is supported axially on a coupling portion 21 of the main drive.
  • annular outer piston 15 which is mounted coaxially with the inner piston 10 in the housing part 2 of the clutch housing.
  • the active piston portion of the inner piston 10 is axially movably mounted in the outer piston 15.
  • the outer piston 15 has a radially inwardly projecting annular shoulder 22, which forms an axial stop relative to the active piston portion of the inner piston 10.
  • the inner piston 10 is sealed relative to the outer piston 15 by means of a sealing arrangement 16.
  • a sliding ring belt 17 is provided as a sliding bearing between the inner piston 10 and the outer piston 15 that serves as a guide band for the Axialbeweglich- speed of the inner piston 10 relative to the outer piston 15 is used.
  • the slip ring band 17 is inserted into a corresponding radially inwardly open annular groove of the outer bulb 15 and prevents metallic contact between the outer bulb 15 made of steel and the existing inner steel piston 10.
  • the Gleitringband 17 is made in the illustrated embodiment of PTFE.
  • the outer piston 15 is sealed by means of a sealing arrangement unspecified axially movable axially mounted in the housing part 2 of the clutch housing.
  • the intermediate housing part 18 protrudes radially between the outer bulb 15 and the disc membrane 1 1, as shown in FIG. 2 can be removed.
  • a helical compression spring arrangement 19, 20 is arranged, which is composed of a plurality of distributed over the circumference of the intermediate housing part 18 arranged helical compression springs.
  • smaller helical compression springs 20 and larger helical compression springs 19 are provided, which are arranged radially and circumferentially offset from one another in the intermediate housing part 18.
  • the helical compression springs 19, 20 are arranged in axial recesses of the intermediate housing part 18, which are open axially to the outer bulb 15.
  • the helical compression springs 19, 20 are supported on the one hand at a bottom of the respective axial recess of the intermediate housing part 18 and on the other at an end face of the outer bulb 15 opposite the pressure chamber 14.
  • the helical compression springs 19, 20 exert an axial counterforce on the outer piston 15, which keep the outer bulb 15 pressed against the housing part 2 in the unloaded initial position of the outer bulb 15.
  • the outer piston 15 has an effective piston surface within the pressure chamber 14, which ends radially inward in the region of the annular shoulder 22.
  • the inner piston 10 has a radially inwardly on the piston surface of the outer piston 15 subsequent, effective piston surface.
  • the entire effective piston area of the pressure chamber 14 is therefore jointly by the inner piston 10th and the outer bulb 15 is formed.
  • the effective piston surfaces of the outer piston 15 and the inner piston 10 are matched to the opposing forces exerted by the pressure spring assemblies 12 and 19, 20 that at the beginning of hydraulic pressurization within the pressure chamber 14, first, the inner piston 10 is moved axially. Only when the pressure increases further does the outer piston 15 also overcome the opposing forces caused by the compression spring arrangements 19, 20 and is moved axially.
  • About the annular shoulder 22 of the outer piston 15 transmits the corresponding pressure forces on the inner piston 10, which in turn acts on the friction plates 5 and 6.
  • the supplementary pressure force of the outer bulb 15 is defined by its effective piston area in the pressure chamber 14. The power transmission takes place via the annular shoulder 22 on the inner piston 10th
  • the friction clutch 1 according to Fig. 2 corresponds - as already stated - with respect to the right half of the drawing coupling half of the friction clutch 1 a of FIG. 1.
  • the left in the drawing of FIG. 2 coupling half is formed by separate components that are detachable to each other or connected to the other coupling parts.
  • the opposite the friction clutch 1 a of FIG. 1 different coupling parts are the intermediate housing part 18, the coil springs 19, 20, the inner piston 10, the outer bulb 15, the guide belt 17 and the additional seal assembly 16 as well as correspondingly longer screw 13. All these coupling parts releasably attached to the opposite of the friction clutch 1 a of FIG. 1 remaining common parts attachable and by means of correspondingly releasable fastening means.
  • FIG. 3 how the friction clutch 1 a according to FIG. 1 and the friction clutch 1 according to the invention according to FIG. 2 have a different pressure / torque behavior during operation.
  • the torque M is shown on the ordinate and the pressure p on the abscissa.
  • the pressure / torque characteristic of the friction clutch 1 a of FIG. 1 is shown in phantom.
  • the pressure / torque characteristic of the friction clutch 1 according to the invention of FIG. 2 is shown by a solid line.
  • a two-stage connection takes place in the friction clutch 1.
  • a first stage in which the pressure forces of the helical compression springs 19, 20 still hold the outer bulb 15 in its initial position, a slight increase in the torque takes place with a corresponding increase in pressure. Only when the resulting total piston effective area of both pistons of the double piston becomes effective does the same torque increase take place relative to the pressure increase, as is the case in the friction clutch 1 according to FIG. 1 from the beginning.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

On connaît déjà ce type d'embrayage ou de frein à friction comportant un système de pistons de compression mobiles axialement ainsi qu'au moins un épaulement annulaire soumis à l'action du système de pistons de compression. Selon l'invention, le système de pistons de compression présente au moins deux pistons qui peuvent être approchés de l'épaulement ou des épaulements annulaires l'un après l'autre par étages en fonction de la pression. L'objet de l'invention est destiné à des machines agricoles.
EP11770801.6A 2010-10-20 2011-10-20 Embrayage ou frein à friction actionné par un fluide sous pression Withdrawn EP2630383A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010049811A DE102010049811A1 (de) 2010-10-20 2010-10-20 Druckmittelbetätigte Reibkupplung oder -bremse
PCT/EP2011/068301 WO2012052498A1 (fr) 2010-10-20 2011-10-20 Embrayage ou frein à friction actionné par un fluide sous pression

Publications (1)

Publication Number Publication Date
EP2630383A1 true EP2630383A1 (fr) 2013-08-28

Family

ID=44992875

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11770801.6A Withdrawn EP2630383A1 (fr) 2010-10-20 2011-10-20 Embrayage ou frein à friction actionné par un fluide sous pression

Country Status (4)

Country Link
US (1) US20130206537A1 (fr)
EP (1) EP2630383A1 (fr)
DE (1) DE102010049811A1 (fr)
WO (1) WO2012052498A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015205185B3 (de) * 2015-03-23 2016-02-04 Gkn Stromag Aktiengesellschaft Druckmittelbetätigte Reibkupplung oder -bremse
DE102018126906A1 (de) * 2018-10-29 2020-04-30 Schaeffler Technologies AG & Co. KG Reibungskupplung
DE102019103775A1 (de) 2019-02-14 2020-08-20 Claas Industrietechnik Gmbh Kupplungsvorrichtung für eine landwirtschaftliche Arbeitsmaschine

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3384214A (en) * 1965-04-16 1968-05-21 Int Harvester Co Dual piston clutch
US3612237A (en) * 1968-05-16 1971-10-12 Honda Motor Co Ltd Liquid pressure-operated frictional clutch apparatus
GB1271680A (en) * 1969-07-18 1972-04-26 Borg Warner Ltd Brake and clutch actuating assembly
US3690429A (en) * 1971-07-15 1972-09-12 Honda Motor Co Ltd Clutch with dual pistons and springs
US3828894A (en) * 1972-12-27 1974-08-13 Goodyear Tire & Rubber Telescopic piston for added brake wear adjustment
US4195714A (en) * 1977-08-22 1980-04-01 The Bendix Corporation Piston and extensible cylinder therefor
IT1202756B (it) * 1978-07-10 1989-02-09 Oleodinamica Magnaghi Spa Dispositivo per il ricupero dell'usura delle guarnizioni di attrito nel gruppo idraulico di comando di freni a disco particolarmente per aerei o simili
DE4418701A1 (de) * 1994-05-28 1995-11-30 Bayerische Motoren Werke Ag Bremskolben für eine Scheibenbremse in einem Kraftfahrzeug
JP3599123B2 (ja) * 1994-06-22 2004-12-08 本田技研工業株式会社 トランスミッション用油圧ブレーキ
DE19602752C1 (de) * 1996-01-26 1997-07-17 Gkn Viscodrive Gmbh Vorrichtung zur Steuerung einer Kupplung
FR2831934B1 (fr) * 2001-11-06 2004-01-16 Eurocopter France Boite de transmission basculante avec dispositif de rattrapage de jeu selon l'axe de basculement
US6920971B2 (en) * 2003-04-17 2005-07-26 Caterpillar Inc Cushioned hydraulic clutch/brake piston
US7140481B2 (en) * 2004-06-25 2006-11-28 Freudenberg-Nok General Partnership Clutch piston amplifier assembly
US7104380B2 (en) * 2004-09-15 2006-09-12 Ford Global Technologies, Llc Dual area piston for transmission clutch and sequential control therefor
DE102007032488A1 (de) * 2006-08-09 2008-02-14 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Einrichtung zur pneumatischen Betätigung einer Fahrzeugkupplung
DE102007047852A1 (de) * 2007-11-23 2009-05-28 Zf Friedrichshafen Ag Lastschaltelement
DE102008046815B4 (de) * 2008-09-11 2013-08-14 Zf Friedrichshafen Ag Kupplungseinrichtung, insbesondere für ein Automatikgetriebe, eine hydrodynamische Kopplungseinrichtung oder eine nasslaufende Kupplung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012052498A1 *

Also Published As

Publication number Publication date
WO2012052498A1 (fr) 2012-04-26
DE102010049811A1 (de) 2012-04-26
US20130206537A1 (en) 2013-08-15

Similar Documents

Publication Publication Date Title
EP2470808B1 (fr) Système de double embrayage pour une boîte de vitesses munie de deux arbres d'entrée
DE2540191C3 (de) Druckmittelbetätigte Lamellenkupplung mit stehendem Ringzylinder
DE10064459A1 (de) Doppelkupplung, insbesondere für Kraftfahrzeuge
DE102005045322A1 (de) Doppelscheibenfeder
EP1698804B1 (fr) Embrayage à friction
DE102008043484A1 (de) Kopplungsanordnung, insbesondere zur wahlweisen Drehkopplung einer Eingangswelle eines Kompressors in einem Fahrzeug mit einem Antriebsorgan
DE102011107696A1 (de) Ausrückereinheit für eine Doppelkupplung
DE102009050346A1 (de) Kupplungsausrücksystem mit Verdrehsicherung für Nehmerzylinderkolben
DE19953091C1 (de) Anordnung zum Kuppeln einer Antriebswelle mit einer oder beiden von zwei Getriebewellen eines Zahnräderwechselgetriebes
EP2630383A1 (fr) Embrayage ou frein à friction actionné par un fluide sous pression
DE102015209611A1 (de) Kennungswandler mit Kurvenscheibe und Querkraft- minimiert positioniertem Stößel zur Betätigung einer Kupplung
DE102008046815B4 (de) Kupplungseinrichtung, insbesondere für ein Automatikgetriebe, eine hydrodynamische Kopplungseinrichtung oder eine nasslaufende Kupplung
EP2721315B1 (fr) Système de débrayage pour embrayage double
DE102006031815B4 (de) Druckölkupplung
EP0480169B1 (fr) Dispositif d'embrayage et de freinage combiné, particulièrement pour presses
DE102021126107B3 (de) Kupplungseinrichtung für ein Kraftfahrzeug und Drehmomentverteileinrichtung für ein Kraftfahrzeug
DE102022114774B3 (de) Kopplungseinheit zur reversiblen Kopplung einer Antriebsseite mit einer Abtriebsseite eines Antriebsstrangs
DE4005965A1 (de) Kupplung
DE102008044220A1 (de) Getriebe
AT513976B1 (de) Schaltbare Zahnradpumpe
EP2454501B1 (fr) Dispositif d'accouplement
DE102016204454B3 (de) Fluidbetätigte Schaltkupplung oder -bremse
DE102015205185B3 (de) Druckmittelbetätigte Reibkupplung oder -bremse
DE10342004B4 (de) Schaltkupplung
DE102018122660A1 (de) Kupplungseinrichtung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130515

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20150128