WO2014095630A1 - Mécanisme de couplage - Google Patents

Mécanisme de couplage Download PDF

Info

Publication number
WO2014095630A1
WO2014095630A1 PCT/EP2013/076540 EP2013076540W WO2014095630A1 WO 2014095630 A1 WO2014095630 A1 WO 2014095630A1 EP 2013076540 W EP2013076540 W EP 2013076540W WO 2014095630 A1 WO2014095630 A1 WO 2014095630A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
clutch mechanism
disc
actuating member
rotatable
Prior art date
Application number
PCT/EP2013/076540
Other languages
English (en)
Inventor
Martin Brenninger
Richard Heindl
Original Assignee
Agco International Gmbh
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
Priority claimed from GB201223543A external-priority patent/GB201223543D0/en
Priority claimed from GB201223542A external-priority patent/GB201223542D0/en
Application filed by Agco International Gmbh filed Critical Agco International Gmbh
Publication of WO2014095630A1 publication Critical patent/WO2014095630A1/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
    • F16D25/06—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
    • F16D25/0638—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 with more than two discs, e.g. multiple lamellae
    • 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
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
    • F16D2048/0254—Double actuation, i.e. two actuation means can produce independently an engagement or disengagement of the clutch

Definitions

  • the present invention relates to clutch mechanisms for utility vehicles and
  • Standard drivelines for All Wheel Drive (AWD) utility vehicles especially for tractors, comprise an AWD clutch between front and rear axles providing an engaged and disengaged position.
  • AWD is disengaged when the vehicle is passing a curve and the inner wheel and outer wheel rotate at different speeds.
  • AWD is also disengaged, so that only the rear wheels transmit brake forces to ground.
  • the engaged position is chosen for high traction work, typically on the field.
  • torque- vectoring may be realized in AWD-cars with, for example, a Haldex coupling between front and rear axles.
  • the parking brake function is different compared to other vehicle types.
  • the parking brake function is realised by a parallel brake system to the service brake which mainly acts on one axle only, generally the rear axle.
  • the service brake which mainly acts on one axle only, generally the rear axle.
  • this function is suitable.
  • a tractor is often used with a trailer with no brakes.
  • the rear wheels have to bear the load of about 40 tonnes. This may result in unplanned movement of the tractor when the rear wheels alone are not capable to handle the load.
  • a clutch mechanism for a utility vehicle comprising: a rotatable first body, a second rotatable body rotatable relative to the first body, at least one first clutch disc which is non-rotatable relative to the first body, at least one second rotating clutch disc which is fixed for rotation with the second rotatable body, an actuating member which can press the first clutch disc and the second clutch disc against each other to close the clutch, a spring means which exerts an closing force on the actuating member via an intermediate part to press the first clutch disc and the second clutch disc against each other to close the clutch, a clutch release means which can exert a clutch release force which counteracts the closing force of the spring so that the actuating member no longer presses the first clutch disc and the second clutch disc against each other, and a clutch
  • the mechanism provides a fail-safe arrangement whereby the spring means forces engagement of the clutch plates unless forcibly counteracted by the clutch release means. Variable engagement is provided by operation of both the clutch release means and clutch applying means.
  • the invention further provides a continuously variable transmission arrangement and an AWD utility vehicle utilising such a clutch mechanism as a coupling mechanism between front and rear driven axles. Further optional features of the invention are recited in the attached sub-claims to which reference should now be made and which are incorporated herein by reference.
  • Figure 1 shows a drivetrain arrangement for an AWD vehicle suitable to incorporate a clutch mechanism according to the invention
  • Figure 2 is a sectional view of a first embodiment of clutch mechanism
  • Figure 3 is a sectional view of a second embodiment of clutch mechanism.
  • Figure 4 shows a further drivetrain arrangement incorporating the clutch mechanism.
  • Figure 1 schematically shows a drivetrain arrangement for a utility vehicle, in this case a tractor, comprising:
  • ASD All Wheel Drive
  • PTO power take-off
  • a first embodiment of a clutch arrangement according the present invention used suitably for the clutch 5 in Figure 1 is shown in sectional view in Figure 2.
  • the clutch arrangement 50 shown in Figure 2 has a first body (input element 51 ) and a second body (output element 52), both pivotably mounted and axially fixed via bearings 53 in a housing 54, which is only shown schematically for better clarity.
  • the housing 54 may be a front wheel driveline housing.
  • a further bearing 55 is provided between input element 51 and output element 52.
  • First clutch discs 56a are pivotably fixed but axially movable attached to the input element 51 via engaging toothing.
  • second clutch discs 56b (in between first clutch discs 56a) are pivotably fixed but axially movable attached to the output element 52 via engaging toothing.
  • the clutch discs 56a, 56b are brought into contact by first annular piston 57 moving in the direction shown by arrow A.
  • the clutch discs 56a, 56b are of wet-type operating under oil supply.
  • a first actuation (clutch applying) means for Variable Adjustment mode is provided by a first actuation chamber 60 which can be pressurized with hydraulic fluid to move a first actuating member (annular piston 57) in direction A.
  • the first actuation chamber 60 is connected to a hydraulic supply system via ducts 52a in output element 52, a rotary feedthrough arrangement 62 (including seals 62a) and a duct 54a in housing 54. If the first actuation chamber 60 is not pressurized, the first annular piston 57 is moved in the opposite direction to A by reset behaviour (caused by friction and oil adulteration) of the clutch discs 56a, 56b.
  • a second actuation means for ON/OFF mode, comprises Belleville spring washer 70 which applies a force in direction A on a second annular piston 71 which is
  • Second annular piston 71 can be moved in an opposite direction to A by pressurizing second actuation chamber 73, with the piston 71 and chamber 73 providing a clutch release means.
  • the second actuation chamber 73 is connected to a hydraulic supply system via ducts 52b in output element 52, a rotary feedthrough arrangement 62 (including seals 62a) and a duct 54b in housing 54. Due to the Belleville spring washer 70, the second actuation means is always closed when the second actuation chamber 73 is disconnected from the oil supply.
  • Belleville spring washers friction forces between the washers result in a certain hysteresis. This hysteresis makes it difficult to realise a fine adjustment of the clutch engagement but, on the other hand, Belleville springs allow high forces in a very compact installation space.
  • first piston 57 can only disengage the clutch discs if the second piston 71 is in the left position (in the orientation of the Figure) from piston chamber 73 being pressurized.
  • intermediate part 72 is not fixed to first piston 57, movement of the second piston 71 does not automatically move first piston 57 in the direction opposite to A.
  • the clutch arrangement 50 would be connected coaxially to the driveline via toothing on the shaft end 51 a of input element 51 and via toothing on the shaft end 52c of output element 52.
  • input element 51 and/or output element 52 could be equipped with toothing on circumferential surfaces shown in dashed lines at 51 b and 52d, which toothing then engages a
  • the clutch 7 in the PTO driveline may also comprise a clutch mechanism according to the invention.
  • Figure 3 shows another embodiment of the coupling arrangement clutch mechanism 500 whereby input element 510 is designed for a non-coaxial connection via circumferential toothing 510a.
  • output element 520 offers a shaft end 520a for coaxial connection and a
  • the driveline comprises
  • the transmission arrangement shown in Figure 4 is of a hydrostatic-mechanical power split type with a mechanical branch and a hydrostatic branch 100 comprising:
  • the first hydraulic motor 102 is connected to the rear axle 2 and can be connected via clutch 500 to the front axle 3. If the clutch 500 is disengaged, motor 102 is not connected to front axle 3 and only drives the rear axle (e.g. for transport on the road).
  • the second hydraulic motor 103 is connected via clutch 300 to the front axle 3. This clutch is a standard On/Off clutch similar to a standard AWD clutch.
  • Clutch 500 also serves as a means to sum up the torque delivered by motor 102 (connected to shaft end 51 a of first body (input element) 51 as shown in Figure 2) and the torque supplied by motor 103 (connected to shaft end 52c of second body (output element) 52 as shown in Figure 2) for connection with the front axle 3 via circumferential toothed portion 52d (as shown in Figure 2) resulting in there being three elements for torque input/output.
  • motor 102 connected to shaft end 51 a of first body (input element) 51 as shown in Figure 2
  • motor 103 connected to shaft end 52c of second body (output element) 52 as shown in Figure 2
  • the clutch mechanism embodiment of Figure 3 could also be used in the driveline of Figure 4.
  • both motors 102, 103 could be connected to the circumferential toothing 510a, 520b (51 b, 52d) for torque input while torque output could be provided at shaft ends 51 a, 52c, 520a.
  • a clutch mechanism for a utility vehicle which comprises a rotatable first body 51 , a second rotatable body 52 rotatable relative to the first body 51 , at least one first clutch disc 56a which is non-rotatable relative to the first body 51 , and at least one second rotating clutch disc 56b which is fixed for rotation with the second rotatable body 52.
  • An actuating member 57 is operable to press the first clutch disc 56a and the second clutch disc 56b against each other to close the clutch.
  • a spring 70 which exerts a closing force on the actuating member 57 via intermediate part 72, presses the first and second clutch discs 56a, 56b against each other to close the clutch.
  • a clutch release means 71 ,73 is operable to exert a clutch release force which counteracts the closing force of the spring so that the actuating member 57 no longer presses the first and second clutch discs 56a, 56b against each other.
  • a clutch applying means 60 exerts a pushing force on the actuating member 57 in the same direction as the closing force to press the first clutch disc 56a and the second clutch disc 56b against each other to close the clutch.

Landscapes

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

Abstract

La présente invention concerne un mécanisme d'embrayage pour véhicule utilitaire, comprenant : un premier corps rotatif (51) ; un second corps rotatif (52) pouvant tourner par rapport au premier corps (51) ; au moins un premier disque d'embrayage (56a) qui ne peut pas tourner par rapport au premier corps (51) ; et au moins un second disque d'embrayage tournant (56b) qui est fixé pour pouvoir tourner avec le second corps rotatif (52). Un élément d'actionnement (57) peut servir à presser le premier disque d'embrayage (56a) et le second disque d'embrayage (56b) l'un contre l'autre pour fermer l'embrayage. Un ressort (70) qui exerce une force de fermeture sur l'élément d'actionnement (57) via une partie intermédiaire (72) presse le premier et le second disque d'embrayage (56a, 56b) l'un contre l'autre pour fermer l'embrayage. Un moyen de débrayage d'embrayage (71, 73) peut servir à exercer une force de débrayage d'embrayage qui agit contre la force de fermeture du ressort de façon à ce que l'élément d'actionnement (57) ne presse plus le premier et le second disque d'embrayage (56a, 56b) l'un contre l'autre. Un moyen d'application d'embrayage (60) exerce une force de poussée sur l'élément d'actionnement (57) dans la même direction que la force de fermeture pour presser le premier disque d'embrayage (56a) et le second disque d'embrayage (56b) l'un contre l'autre pour fermer l'embrayage.
PCT/EP2013/076540 2012-12-21 2013-12-13 Mécanisme de couplage WO2014095630A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB1223543.8 2012-12-21
GB201223543A GB201223543D0 (en) 2012-12-21 2012-12-21 Coupling mechanism
GB201223542A GB201223542D0 (en) 2012-12-21 2012-12-21 Coupling mechanism
GB1223542.0 2012-12-21

Publications (1)

Publication Number Publication Date
WO2014095630A1 true WO2014095630A1 (fr) 2014-06-26

Family

ID=49766086

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/076540 WO2014095630A1 (fr) 2012-12-21 2013-12-13 Mécanisme de couplage

Country Status (1)

Country Link
WO (1) WO2014095630A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016193347A1 (fr) * 2015-06-03 2016-12-08 Borgwarner Torqtransfer Systems Ab Embrayage hydraulique

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH259546A (fr) * 1941-02-18 1949-01-31 Cattaneo Giustino Dispositif de commande pour accouplement à friction destiné à la transmission du mouvement entre deux éléments tournants.
DE202006019190U1 (de) * 2006-12-15 2008-04-24 Kwd Kupplungswerk Dresden Gmbh Federdruck-Lamellenkupplung für Kompressoren
US20090045028A1 (en) * 2007-08-16 2009-02-19 Gm Global Technology Operations, Inc. Clutch Actuation System with Locking Mechanism and Method of Controlling Engagement of a Clutch
DE102008019951A1 (de) * 2008-04-21 2009-10-22 Robert Rieder Vorrichtung zur Servobetätigung und definierten Schlupferzeugung von/an Motorradkupplungen

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH259546A (fr) * 1941-02-18 1949-01-31 Cattaneo Giustino Dispositif de commande pour accouplement à friction destiné à la transmission du mouvement entre deux éléments tournants.
DE202006019190U1 (de) * 2006-12-15 2008-04-24 Kwd Kupplungswerk Dresden Gmbh Federdruck-Lamellenkupplung für Kompressoren
US20090045028A1 (en) * 2007-08-16 2009-02-19 Gm Global Technology Operations, Inc. Clutch Actuation System with Locking Mechanism and Method of Controlling Engagement of a Clutch
DE102008019951A1 (de) * 2008-04-21 2009-10-22 Robert Rieder Vorrichtung zur Servobetätigung und definierten Schlupferzeugung von/an Motorradkupplungen

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016193347A1 (fr) * 2015-06-03 2016-12-08 Borgwarner Torqtransfer Systems Ab Embrayage hydraulique
CN107667231A (zh) * 2015-06-03 2018-02-06 博格华纳瑞典公司 液压耦合器
CN107667231B (zh) * 2015-06-03 2019-11-22 博格华纳瑞典公司 液压耦合器
US10711846B2 (en) 2015-06-03 2020-07-14 Borgwarner Sweden Ab Hydraulic coupling

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