WO2003106854A1 - Embrayage a friction - Google Patents

Embrayage a friction Download PDF

Info

Publication number
WO2003106854A1
WO2003106854A1 PCT/EP2003/005838 EP0305838W WO03106854A1 WO 2003106854 A1 WO2003106854 A1 WO 2003106854A1 EP 0305838 W EP0305838 W EP 0305838W WO 03106854 A1 WO03106854 A1 WO 03106854A1
Authority
WO
WIPO (PCT)
Prior art keywords
arrangement
flywheel
friction clutch
wear compensation
clutch according
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.)
Ceased
Application number
PCT/EP2003/005838
Other languages
German (de)
English (en)
Inventor
Klaus-Peter Oberle
Jörg Pankoke
Arnold Huisjes
Klaus Fischer
Horst Friedrich
Werner Selzam
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.)
ZF Race Engineering GmbH
Original Assignee
Sachs Race Engineering 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
Application filed by Sachs Race Engineering GmbH filed Critical Sachs Race Engineering GmbH
Priority to AU2003246399A priority Critical patent/AU2003246399A1/en
Publication of WO2003106854A1 publication Critical patent/WO2003106854A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • 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
    • F16D13/75—Features relating to adjustment, e.g. slack adjusters
    • F16D13/757—Features relating to adjustment, e.g. slack adjusters the adjusting device being located on or inside the clutch cover, e.g. acting on the diaphragm or on the pressure plate

Definitions

  • the present invention relates to a friction clutch, comprising a flywheel arrangement for attaching the friction clutch to a drive member, a housing arrangement which is connected to the flywheel arrangement for common rotation about an axis of rotation, a pressure plate arrangement which is connected to the housing arrangement for common rotation about the axis of rotation and with respect to the Housing arrangement is coupled displaceably in the direction of the axis of rotation, a force accumulator to be applied to the pressure plate arrangement in the direction of the flywheel mass arrangement, and a clutch disc arrangement which is connected to a
  • Clutch disk friction surface arrangement can be clamped between the pressure plate arrangement and the flywheel arrangement.
  • a friction clutch comprising: a flywheel arrangement for attaching the friction clutch to a drive member, a housing arrangement which is connected to the flywheel arrangement for common rotation about an axis of rotation, a pressure plate arrangement which is connected to the housing arrangement for common rotation around the axis of rotation and with respect to the housing arrangement in the direction of the axis of rotation is coupled, a force accumulator to be applied to the pressure plate arrangement in the direction of the flywheel mass arrangement, a clutch disc arrangement which can be clamped with a clutch disc friction surface arrangement between the pressure plate arrangement and the flywheel mass arrangement, a wear compensation arrangement which the
  • Flywheel arrangement comprises a wear compensation element that can be displaced in the direction of the axis of rotation for wear compensation.
  • the wear compensation is carried out in the area of the flywheel arrangement. This is an area that is particularly useful for performing manually
  • the flywheel arrangement comprises a flywheel base body, on which the wear compensation element is supported such that it can be displaced in the direction of the axis of rotation.
  • the housing arrangement can be connected to the flywheel base body in a radially outer region.
  • the wear compensation element be supported by an inclined surface arrangement with respect to the flywheel main body.
  • the inclined surface arrangement can comprise threaded areas that are in engagement with one another.
  • An embodiment which is very advantageous due to the small number of components required can provide that the wear compensation element is in threaded engagement with the flywheel mass body and can be displaced in the direction of the axis of rotation by rotating with respect to the flywheel mass body.
  • the wear compensation element it is possible for the wear compensation element to be supported with respect to the flywheel mass body and to be displaceable in the direction of the axis of rotation by means of support elements which are threadedly engaged with this and / or the flywheel main body.
  • the inclined surface arrangement can comprise a wedge or ramp surface arrangement, so that a relative axial displacement of the components opposite one another with corresponding surfaces is also achieved.
  • the A flywheel base body is provided with a movement blocking arrangement that blocks the wear compensation element against movement and can be brought into a release state for carrying out wear compensation processes.
  • the movement blocking arrangement comprises at least one blocking element which is pretensioned in a blocking position and engages in a blocking recess of the wear compensation element in the blocking position.
  • a plurality of blocking recesses which follow one another in the circumferential direction are provided on the wear compensation element.
  • the movement blocking arrangement comprises a plurality of, preferably two, blocking elements.
  • an adjustment tool engagement formation be provided on the wear compensation element. Blocking recesses can simultaneously form at least part of the adjustment tool attack formation.
  • the friction clutch according to the invention can be constructed in such a way that the clutch disc arrangement has a plurality of friction elements, a counter-friction element which is connected in a rotationally fixed manner to the housing arrangement being arranged between each two friction elements of the clutch disc arrangement.
  • This design constructed in the manner of so-called multi-plate clutches, has a comparatively compact size and a relatively large surface that becomes frictionally effective, so that very large torques can also be transmitted, which is particularly important in the racing field.
  • a counter-friction element which is connected in a rotationally fixed manner to the housing arrangement or the flywheel mass arrangement and can be brought into frictional interaction with a friction element of the clutch disc arrangement, is supported.
  • the present invention further relates to a flywheel arrangement for a friction clutch, comprising a flywheel base body provided for coupling to a drive element and a wear compensation element which is supported on the flywheel base body such that it can be displaced in the direction of an axis of rotation.
  • Figure 1 is a longitudinal sectional view of a friction clutch according to the invention.
  • Fig. 2 is a perspective view of a housing shown in Fig. 1
  • Fig. 3 is a longitudinal sectional view of the housing shown in Fig. 2;
  • FIG. 4 is a perspective view of a flywheel base body of the friction clutch shown in FIG. 1;
  • FIG. 5 shows a longitudinal sectional view of the flywheel body shown in FIG. 4;
  • FIG. 6 is an axial view of a wear compensation element of the friction clutch shown in FIG. 1;
  • FIG. 7 is a longitudinal sectional view of the wear compensation element shown in FIG. 6;
  • FIG. 8 is a perspective view of the friction clutch shown in FIG.
  • Fig. 9 is a longitudinal sectional view of the assembly shown in Fig. 8.
  • FIG. 10 is a view of an adjusting tool to be used to carry out wear compensation processes
  • Fig. 1 1 is a perspective view of a for deactivating a
  • This friction clutch 10 comprises a flywheel arrangement, generally designated 12, which in turn comprises a flywheel base body 14 designed for connection to a crankshaft or another drive shaft. On its side facing the drive unit, the latter has a projection arrangement 16 which is arranged around an axis of rotation A and which can serve as an incremental encoder for a magnetic sensor.
  • a plurality of connecting webs 22 extend from this ring-like region 20 in the axial direction and extend axially onto the flywheel base body 14.
  • a passage opening 24 is provided in each of these connecting webs 22 for a screw bolt 26 which can also be seen in FIG. 1.
  • a starter ring gear 30 can be fixed to the housing 18 by a plurality of screw bolts 28.
  • a pressure plate 32 is provided in the volume area generally surrounded by the housing 18 and the flywheel base body 14. This has radial projections 34 on different circumferential areas, each of which engages between two connecting webs 22 of the housing 18, so that the pressure plate 32 is held in a rotationally fixed manner with the housing 18, but is movable in the direction of the axis of rotation A.
  • a force accumulator 36 for example in the form of a diaphragm spring, is supported in its radially outer region via a support ring 38 on the housing 18 and acts on the pressure plate 32 radially further inward, so that it is pressed in the direction of the flywheel arrangement 12.
  • the Support ring 38 partially received in a groove-like recess 40 of the housing 18.
  • a plurality of outer plates 42 are also coupled in a rotationally fixed manner to the housing 18. These outer disks 42 also have radial projections 44 on a plurality of circumferential areas, each of which engages between two connecting webs 22 of the housing 18, so that the outer disks 42 are non-rotatably coupled to the housing 18, but can be displaced in the direction of the axis of rotation A with respect thereto.
  • a clutch disk, generally designated 46 has a hub 48 which is formed in the radially inner region with teeth 50 provided for rotationally fixed coupling to a transmission input shaft. In its radially outer region, this hub 48 is in non-rotatable engagement with a plurality of inner disks 52, the inner disks 52 also being coupled to the hub 48 so as to be axially movable.
  • the outer fins 42 and the inner fins 52 are made of a material that can meet the requirements that arise during operation.
  • the inner fins 42 can be designed as so-called carbon discs or carbon-containing discs, while the outer fins can be constructed from sintered material for improved heat dissipation from the area of the surfaces that become frictionally effective.
  • an outer plate 42 is positioned axially immediately adjacent to the flywheel arrangement 12, that is to say a compensation ring 54 described in more detail below, and axially adjacent to the pressure plate 32, so that in the transition region from the flywheel arrangement 12 to the various plates and in Transition area from the pressure plate 32 to the various slats no friction will occur.
  • the flywheel arrangement 12 and the pressure plate 32 can thus be kept essentially free from wear.
  • outer disks 42 or inner disks 52 will wear to a greater or lesser extent, which basically has the consequence that their axial thickness decreases.
  • An axial decrease in the thickness of the various plates 42 or / and 52 would, however, result in the pressure plate 32 moving closer to the flywheel arrangement 14 in the engaged state of the friction clutch 10 and thus the energy accumulator 36 changing its installation position.
  • the friction clutch 10 has a wear compensation arrangement, generally designated 56.
  • This essentially comprises the compensation ring 54 already mentioned above, which provides a flywheel contact surface 58 for engaging the disk pack 42, 52, which, however, as already explained above, does not have a frictional effect.
  • the pressure plate 32 provides a pressure plate contact surface 60 that does not become frictionally effective.
  • the flywheel base body 14 has an internal thread 62 into which an external thread 66 provided on an axial, ring-like projection 64 of the compensation ring 54 is screwed.
  • the two threads 62, 66 which are in engagement with one another are designed as fine threads, that is to say as threads with a small pitch, to enable very finely metered wear compensation.
  • an adjustment groove 68 which preferably encircles the entire circumference, is provided on the housing 18 in the region of the connecting webs 22, which represents the position of the pressure plate 32 in the unsealed state.
  • two circumferentially adjacent openings 70 are formed on the flywheel main body 14. These are of stepped design and have a larger cross-sectional dimension on their side facing the housing 18 than on their side facing away from the housing 18.
  • a blocking pin 74 with a close fit is passed through the opening area 72 with a smaller diameter. This is achieved in that both the opening 70 and the bolt 74 are manufactured with a high degree of accuracy.
  • a pot-like sleeve 78 is accommodated in the opening section 76 with a larger diameter, which is also manufactured with high precision, so that it can basically be moved in the axial direction with only very little radial movement play.
  • the locking bolt 74 passes through an opening 82 in the bottom region of the sleeve 78 with an end section 80 with a smaller diameter and is fixed to the sleeve 78 by a snap ring or locking ring 84.
  • a helical compression spring 86 is held under pre-tension, so that in principle the composite consisting of the blocking bolt 74 and the sleeve 78 is directed out of the opening 70 and onto the housing 18 or the compensation ring 54 is too biased.
  • the compensation ring 54 covers the opening 70, see above that the sleeve 78 is held in the opening 70 or in the section 76 thereof.
  • the recesses 88 have a mutual circumferential spacing which also corresponds to the circumferential spacing of the two openings 70 which can be seen in FIG. 4, for example, and thus the two blocking bolts 74 accommodated in these openings 70.
  • two blocking bolts 74 always protrude with their areas 81 into two of the cutouts 88.
  • a rotation of the compensation ring 54 with respect to the flywheel base body 14 is not possible if the blocking bolts 74 are in their blocking position which can be seen in FIG. 9.
  • balancing openings 90 are provided on the side of the centrifugal mass base body 14 opposite in the circumferential direction of the positioning of the blocking bolts 74, which serve to accommodate balancing masses.
  • the assembly shown in FIG. 9 can thus be balanced on its own and can thus be provided essentially without any imbalance.
  • the housing 18 In association with the two blocking bolts 74, the housing 18 has circumferential and facing one another in the region of two connecting webs 22
  • Recesses 92 which allow axial movement of the blocking bolts 74 or of the sleeves 78 firmly coupled to them. Furthermore, preferably all
  • connecting webs 22 In their axial end region, connecting webs 22 have a stop shoulder 94, which forms a maximum movement stop for the compensation ring 54. That is, with the flywheel arrangement 12 assembled with the housing 18, the compensation ring 54 can only be rotated until it is in its
  • Thread engagement of the compensation ring 54 is connected to the flywheel base body 14 in a defined manner, but further wear compensation is then no longer possible.
  • a release tool 100 shown in FIG. 11 is used. This has a fork-like end tapering wedge-like in its longitudinal direction with two notches 102, 104.
  • the tool 100 is brought to the friction clutch 10 from the radially outside, in the area in which the two connecting webs 22 bearing the markings 96 lie.
  • the tool 100, with its wedge-like end region 106, is inserted between the flywheel main body 14 and the enlarged head regions 108 of the bolts 74, each bolt 74 entering one of the notches 102, 104.
  • the bolts 74 are pulled to the left in the illustration in FIG. 9, ie the sections 80 emerge from the recesses 88 of the compensation ring 54 which initially still receive them.
  • the locking bolts 74 are then in a release position which no longer blocks the rotation of the adjusting ring 54. Due to the precise manufacture of the locking bolts 74, the sleeves 78 and the openings 70 receiving them, as already mentioned, precise guidance is provided, so that even after the locking bolts 74 are released, they can again move axially towards their locking position in a reliable manner , To here the To avoid the occurrence of the smallest canting, the components that can be moved relative to one another can be slightly chamfered in the respective edge areas. This also applies to tool 100.
  • the compensation ring 54 is rotated from the outside with a further tool 110.
  • the tool 110 has an engagement projection 112, which is inserted between two connecting webs 22 into one of the radially outwardly open recesses 88 and is then tilted in the circumferential direction, for example with support on one of the connecting webs 22, so that the compensation ring is generated on the basis of the lever action then generated 54 is rotated.
  • the flywheel base body 14 has a circumferential recess 116 in a ring-like extension 114 provided in the outer circumferential region thereof, through which the tool 110 with its projection 112 can then be guided and positioned engaging in a recesses 88.
  • This adjustment process can be repeated successively until, under observation of the position of the pressure plate 32, it assumes the desired relative position with respect to the adjustment groove 68 already mentioned above.
  • the tool 100 is withdrawn radially outward, so that the blocking bolts 74 are basically released again to return to their blocking position.
  • the blocking bolts 74 initially remain in an inactive position, in which they with their sections 80 cover the compensation ring 54 in areas between two of each Apply recesses 88.
  • a further rotation of the compensation ring 54 is then induced with the tool 110 until two of the cutouts 88 come into alignment with the sections 80 of the blocking bolts 74 and these blocking bolts 74 then with the regions 81 of sections 80 snap axially into these recesses 88.
  • the friction clutch constructed according to the invention makes it possible to carry out a wear compensation process manually in a simple manner, so that, for example, friction clutches can also be used for longer in racing, i.e. the axial thickness of the fins that rub off during operation can be better used. It is of particular importance here that wear compensation arrangements that work automatically due to the carbon material used can be added, especially when used in racing, due to the dust generated during abrasion, so that their functionality is not guaranteed. It is also important that racing is done at high speeds and when strong vibrations occur, which further increases the susceptibility to failure of automated wear compensation arrangements.
  • the wear compensation arrangement according to the invention is functionally reliable even under difficult conditions, since no components have to be displaced with respect to one another, particularly in rotary operation, in order to achieve wear compensation.
  • Another advantage of the friction clutch designed according to the invention is that the measures required to carry out the compensation process are to be carried out on the side of the friction clutch 10 which is closer to the drive unit. This is advantageous since this area is generally more easily accessible than the other axial end area of the friction clutch 10, in which, for example, a starter also makes free access difficult.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un embrayage à friction qui comprend un système de masse d'inertie (12) servant à monter l'embrayage à friction (10) sur un organe d'entraînement, un système de carter (18) qui est relié au système de masse d'inertie (12) pour la rotation commune autour d'un axe de rotation (A), un système de plaque de pression (32) qui est accouplé au système de carter (18) pour la rotation commune autour de l'axe de rotation (A) et peut être déplacé par rapport au système de carter (18) dans le sens de l'axe de rotation (A), un accumulateur d'énergie (36) sollicitant le système de plaque de pression (32) en direction du système de masse d'inertie (12), un système de disque d'embrayage (46) pouvant être monté entre le système de plaque de pression (32) et le système de masse d'inertie (12) à l'aide d'un système de surface de friction de disque d'embrayage (52), ainsi qu'un système de compensation d'usure (56) qui comprend, sur le système de masse d'inertie (12), un élément de compensation d'usure (54) pouvant être déplacé en direction de l'axe de rotation (A) pour compenser l'usure.
PCT/EP2003/005838 2002-06-12 2003-06-04 Embrayage a friction Ceased WO2003106854A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2003246399A AU2003246399A1 (en) 2002-06-12 2003-06-04 Friction clutch

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10225991.7 2002-06-12
DE2002125991 DE10225991A1 (de) 2002-06-12 2002-06-12 Reibungskupplung

Publications (1)

Publication Number Publication Date
WO2003106854A1 true WO2003106854A1 (fr) 2003-12-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/005838 Ceased WO2003106854A1 (fr) 2002-06-12 2003-06-04 Embrayage a friction

Country Status (3)

Country Link
AU (1) AU2003246399A1 (fr)
DE (1) DE10225991A1 (fr)
WO (1) WO2003106854A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8167108B2 (en) 2007-08-20 2012-05-01 Yamaha Hatsudoki Kabushiki Kaisha Clutch, continuously variable transmission, engine unit including them, and straddle-type vehicle including them

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993007400A1 (fr) * 1991-10-04 1993-04-15 Automotive Products Plc Embrayage a friction
US5404979A (en) * 1994-05-27 1995-04-11 Chrysler Corporation Motor vehicle manual transmission modular clutch assembly
US5494143A (en) * 1992-11-27 1996-02-27 Automotive Products, Plc Multiplate clutch
US6053296A (en) * 1997-03-25 2000-04-25 Valeo Friction clutch with wear take-up device, especially for motor vehicles

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993007400A1 (fr) * 1991-10-04 1993-04-15 Automotive Products Plc Embrayage a friction
US5494143A (en) * 1992-11-27 1996-02-27 Automotive Products, Plc Multiplate clutch
US5404979A (en) * 1994-05-27 1995-04-11 Chrysler Corporation Motor vehicle manual transmission modular clutch assembly
US6053296A (en) * 1997-03-25 2000-04-25 Valeo Friction clutch with wear take-up device, especially for motor vehicles

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8167108B2 (en) 2007-08-20 2012-05-01 Yamaha Hatsudoki Kabushiki Kaisha Clutch, continuously variable transmission, engine unit including them, and straddle-type vehicle including them

Also Published As

Publication number Publication date
AU2003246399A1 (en) 2003-12-31
DE10225991A1 (de) 2003-12-24

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