WO2011138804A1 - Embrayage centrifuge, en particulier pour des véhicules motorisés à transmission automatique à variation continue et similaires - Google Patents

Embrayage centrifuge, en particulier pour des véhicules motorisés à transmission automatique à variation continue et similaires Download PDF

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Publication number
WO2011138804A1
WO2011138804A1 PCT/IT2010/000201 IT2010000201W WO2011138804A1 WO 2011138804 A1 WO2011138804 A1 WO 2011138804A1 IT 2010000201 W IT2010000201 W IT 2010000201W WO 2011138804 A1 WO2011138804 A1 WO 2011138804A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch elements
bell
shaped element
mechanical coupling
rotating body
Prior art date
Application number
PCT/IT2010/000201
Other languages
English (en)
Inventor
Ugo Malossi
Original Assignee
Malossi Engineering S.R.L.
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 Malossi Engineering S.R.L. filed Critical Malossi Engineering S.R.L.
Priority to PCT/IT2010/000201 priority Critical patent/WO2011138804A1/fr
Publication of WO2011138804A1 publication Critical patent/WO2011138804A1/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
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction clutching members
    • 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
    • F16D2300/02—Overheat protection, i.e. means for protection against overheating
    • F16D2300/021—Cooling features not provided for in group F16D13/72 or F16D25/123, e.g. heat transfer details
    • 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
    • F16D2300/12—Mounting or assembling

Definitions

  • the present invention refers to a centrifugal type clutch mechanical coupling, particularly for motorvehicles with continuous variation automatic transmission and the like.
  • clutches which are called “of the centrifugal type” and which comprise a support element, which forms such first part and which bears a series of clutch elements, which are more commonly known by the jargon term “shoes” and which move radially with respect to its axis of rotation, and a bell-shaped element, which forms such second part and which accommodates the support element and the clutch elements.
  • the clutch elements move from a position that is radially internal with respect to the support element to a position that is radially external, thus moving away from the centre of rotation and defeating the action of elastic means that are interposed between such clutch elements and which are adapted to work against their radial movement.
  • the clutch elements come into contact with their outside surfaces with the inside surface of the bell-shaped element, gripping it and achieving the desired coupling.
  • the support element generally consists in a perforated plate, substantially circular in shape, which is fitted on the driving element of the transmission and which bears, on its periphery, a plurality of clutch elements.
  • the clutch elements consist in bodies that are substantially C-shaped and which are hinged, at one of their ends, to the support element in such a way that such support elements can rotate about their axis of hinging.
  • clutch elements are hinged to the support element at respective points that are uniformly distributed on the periphery of the support element and which can be interconnected to each other by a plurality of helical springs each of which is hooked to the free end of a clutch element and to the hinged end of the adjacent clutch element.
  • each individual clutch element is subjected to the apparent centrifugal force which tends to make it rotate outward about its axis of hinging with the support element.
  • the rotation of the clutch elements is countered by the action of the elastic means associated with the clutch elements and is impeded by them until a certain angular speed of the support element is reached, the value of which is linked to the value of the elastic modulus of the helical springs and to the value of the mass of the individual clutch elements subjected to the apparent centrifugal acceleration.
  • centrifugal type clutches are widely used in the motorcycle sector, and they are particularly common in the drivetrains of mopeds and of motorcycles of small and medium capacity where the common denominator is that a drivetrain with continuous variation automatic transmission is used.
  • such drivetrains which kinematically connect the drive shaft of the engine of the motor vehicle with its rear wheel, comprise a first drivetrain stage which is constituted by a belt drive that comprises two belt pulleys, of which one is directly fitted on the drive shaft of the engine of the motor vehicle, with a transmission that varies together with the variation of the speed of rotation of the belt, and a second drivetrain stage constituted by a gear reducer which is directly connected to the rear wheel of the motor vehicle.
  • the two drivetrain stages are kinematically connected to each other by means of a known centrifugal type clutch mechanical coupling, the support element of which is integral in rotation with the driven belt pulley of the first drivetrain stage and the bell-shaped element of which is integral in rotation with the first cogwheel of the gear reducer of the second drivetrain stage.
  • the revolutions per minute of the engine at which the mechanical coupling is activated and, therefore, the minimum value of the torque that can be transmitted to the rear wheel of the motor vehicle at the time of activation of the mechanical coupling depend exclusively on the elastic properties of the helical springs associated with the clutch elements and on the mass possessed by such clutch elements.
  • a known technique is to adjust known mechanical couplings by replacing the helical springs associated with the clutch elements with helical springs with optimal elastic properties and by adding masses to, or subtracting masses from, the clutch elements themselves.
  • the aim of the present invention is to devise a centrifugal type clutch mechanical coupling, particularly for motor vehicles with continuous variation automatic transmission and the like, that makes it possible to rapidly adjust such mechanical coupling, thus overcoming the limitations and solving the drawbacks of the known art.
  • an object of the present invention is to devise a mechanical coupling that does not need to be completely dismantled in order to permit adjustment operations.
  • Another object of the invention is to devise a mechanical coupling that is highly reliable, easy to implement and of low cost.
  • a centrifugal type clutch mechanical coupling particularly for motor vehicles with continuous variation automatic transmission and the like, comprising a support element that bears a plurality of clutch elements and which can be fixed integrally in rotation about an axis of rotation to a first rotating body, and a bell-shaped element that accommodates said clutch elements inside it at least in part and which can be fixed integrally in rotation about said axis of rotation to a second rotating body which is to be kinematically connected to said first rotating body, said clutch elements being capable of engaging with said bell-shaped element, against the action of elastic means which are removably associated with said clutch elements, to transmit the motion of said first rotating body to said second rotating body, characterised in that it comprises a plurality of apertures formed on the outside surface of said bell-shaped element for extracting and inserting at least one of said elastic means and additional masses which can be associated with said clutch elements, with said support element associated with said first rotating body and with said bell-shaped
  • Figure 1 is a partially exploded perspective view of a preferred, but not exclusive, embodiment of a centrifugal type clutch mechanical coupling, particularly for motor vehicles with continuous variation automatic transmission and the like, according to the invention
  • Figure 2 is an exploded perspective view of the support element and of the clutch elements of the mechanical coupling shown in Figure 1 ;
  • Figure 3 is a perspective view of the mechanical coupling shown in Figure 1 and installed on a motor vehicle according to the invention
  • Figure 4 is an enlarged-scale view of a detail of the mechanical coupling shown in Figure 3.
  • a centrifugal type clutch mechanical coupling particularly for motor vehicles with continuous variation automatic transmission and the like, according to the invention, generally designated by the reference numeral 1, comprises a support element 2 that bears a plurality of clutch elements 3 and which can be fixed integrally in rotation about an axis of rotation 4 to a first rotating body 5, for example the driven belt pulley of a belt drive 7 of a motor vehicle 8 with continuous variation automatic transmission.
  • the mechanical coupling 1 further comprises a bell-shaped element 9 that accommodates the clutch elements 3 inside it at least in part and which can be fixed integrally in rotation to a second rotating body 10 which is to be kinematically connected to the first rotating body 5 about the axis of rotation 4 of the first rotating body 5.
  • the second rotating body 10 coincides with the shaft of the first cogwheel of the gear reducer of the motor vehicle 8 with continuous variation automatic transmission.
  • the driven belt pulley 5 to which the support element 2 is fixed is rotatably fitted on the shaft 10 of the first cogwheel of the gear reducer of the motor vehicle 8 and the bell-shaped element 9 is fitted on the shaft 10 and. axially locked by a nut 12 screwed on a threaded portion of the shaft 10.
  • the described use of the mechanical coupling 1 is to be intended to be a non-limiting example since the mechanical coupling 1 can be used in various different fields of engineering in which there are mechanical drivetrains that may also be different from that shown in Figures 3 and 4.
  • the support element 2 comprises a first load plate 13, substantially disc shaped and with a contoured central hole 14 in order to be fixed to the belt pulley 5, i.e. to the first rotating body, by fitting the support element 2 on a hub that is integral in rotation with the driven belt pulley 5.
  • the support element 2 comprises a second load plate 15 that is contoured and which has a circular central hole 16 that is adapted to allow the passage, without interference, of the hub of the driven pulley 5 and of the respective contrast spring of the belt drive 7, which consists in a helical spring that is fitted on the hub of the driven pulley 5 and which is compressed between the outside wall of the driven pulley 5 and the first load plate 13.
  • the two load plates 13 and 15 are parallel with and connected to each other by a plurality of pins 17, one for each clutch element 3 and each of the clutch elements 3 is rotatably fitted on one of the pins 17 and is interposed between the first load plate 13 and the second load plate 15 to achieve a hinging between the clutch elements 3 and the support element 2.
  • the pins 17 are each made from a substantially cylindrical body with a circular base which has, at its ends, a radially enlarged portion 18 and a radially reduced portion 19.
  • Each pin 17 is snugly inserted, at its radially enlarged portion 18, in a respective first hole 20 that is formed on the first load plate 13 and, at its radially reduced portion 19, in a respective second hole 21 that is coaxial with the respective first hole 20 and which is formed on the second load plate 15.
  • each pin 17 On the radially reduced portion 19 of each pin 17 there is a circular groove 22 that is adapted to accommodate an elastic seal ring 23.
  • the second holes 21 are made on protuberances 24 which extend in the direction of the clutch elements 3 and there are spacer rings 25 fitted on the pins 17 and interposed between the first load plate 13 and the clutch elements 3.
  • the clutch elements 3 can move radially with respect to the axis of rotation 4 of the driven pulley 5 from a position in which they are disengaged from the bell-shaped element 9 to a position in which they are engaged with the bell-shaped element 9 to transmit the motion of the driven pulley 5, i.e. of the first rotating body, to the shaft 10, i.e. to the second rotating body.
  • this movement occurs as an effect of reaching a preset angular speed of actuation of the support element 2, i.e. of the driven pulley 5, and against the action of elastic means 6 that are removably associated with the clutch elements 3.
  • each clutch element 3 comprises a body that is substantially C-shaped, hinged in proximity to a first one of its ends 3 a to a respective pin 17 and with its centre of curvature facing towards the axis of rotation 4 of the support element 2.
  • each clutch element 3 comprises at least one friction surface 3b, upon which material 50 with a high friction coefficient is deposited, and which is defined on the opposite side with respect to the centre of curvature of the clutch element 3 so as to be adapted to engage by friction with the inside surface 51 of the bell-shaped element 9.
  • the elastic means 6 comprise a plurality of flexion springs 26, one for each clutch element 3, which can be removably fixed to the first load plate 13 and inserted in respective cavities 27 formed in central portions 3 c of the clutch elements 3.
  • each one of the flexion springs 26 is substantially V- shaped and the ends of the V can be removably fixed, by slotting, to the first load plate 13 and the body of the V is inserted into the respective cavity 27.
  • the mechanical coupling 1 comprises a plurality of openings 28 formed on the outside surface of the bell-shaped element 9, and more precisely on its front face 29, to enable the extraction and/or insertion of at least one of the elastic means 6, i.e. the flexion springs 26, and of the additional masses 30 that can be associated with the clutch elements 3, without dismantling the mechanical coupling 1 from the drivetrain of the motor vehicle 8, i.e. with the support element 2 associated with the driven pulley 5 and with the bell-shaped element 9 associated with the shaft 10 of the first cogwheel of the gear reducer of the motor vehicle 8.
  • rollers 31 that can be removably fixed to the clutch elements 3 to increase the total mass of each one of the clutch elements 3.
  • each roller 31 is accommodated in a seat 32 that is formed by the respective clutch element 3 and which is shaped so as to fit into the seat 32 once it has been inserted and rotated by 90° with respect to its axis of insertion 33.
  • This rotation is made possible, for example, by a hexagonal hole 34 into which a screwdriver with hexagonal head 36 or the like can be inserted.
  • the first load plate 13 is shaped so as to allow the passage of the head of the hexagonal head screwdriver 36 to tighten and/or loosen the rollers 31 without having to dismantle the mechanical coupling 1.
  • the flexion springs 26 can easily be extracted and/or inserted by using a needle-nose pliers 35 or the like.
  • the bell-shaped element 9 is made from a substantially cylindrical body with a circular base, preferably obtained from a solid piece with materials of exceptionally high mechanical strength in order to prevent breakage and failures following the high revolutions per minute to which the mechanical coupling 1 is subject, which is open at one front face thereof for inserting the support element 3, and, in particular, at least the first load plate 13 and the clutch elements 3.
  • the bell-shaped element 9 has, on its outside surface, and more precisely on its outside cylindrical surface 37, a plurality of circular ridges 38 for the structural rigidity of the bell-shaped element 9.
  • the mechanical coupling 1 comprises means 40 for conveying air that can be associated with the bell-shaped element 9 and which are adapted to convey air into the bell-shaped element 9.
  • the conveyor means 40 comprise at least one covering element 41 that can be fixed externally to the bell-shaped element 9, for example by means of screws 42, and which comprises a plurality of open scoops 43, obtained for example by deformation by pressing, formed at the openings 28 and which define a plurality of channels for conveying air in the direction of the openings 28.
  • the temperature of the bell-shaped element 9 and of the clutch elements 3 is maintained at optimal values so as to limit the wear of the material 50 with high friction coefficient and, at the same time, evacuation of the dust produced by the wear of the clutch elements 3 is favoured through the discharge holes 39.
  • centrifugal type clutch mechanical coupling particularly for motor vehicles with continuous variation automatic transmission and the like, according to the invention, fully achieves the intended aim and objects, since it allows its adjustment without necessarily needing to be dismantled.
  • Another advantage of the mechanical coupling according to the invention consists in that it operates constantly at optimal temperatures thanks to the ventilation provided by the means for conveying air, as a consequence prolonging the useful life of the parts subject to wear.
  • a further advantage of the mechanical coupling according to the invention consists in that it is highly reliable and mechanically strong, it is easy to implement with a structure that is simple, and it can be produced at low cost.
  • centrifugal type clutch mechanical coupling particularly for motor vehicles with continuous variation automatic transmission and the like, thus conceived is susceptible of numerous modifications and variations, all of which are within the scope of the appended claims.
  • the materials employed, as well as the dimensions, may be any according to requirements and to the state of the art.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

Abstract

L'invention concerne un accouplement mécanique de type centrifuge (1), en particulier pour des véhicules motorisés à transmission automatique à variation continue et similaires, comportant un élément de support (2) qui porte une pluralité d'éléments d'embrayage (3) et qui peut être fixé d'une seule pièce en rotation autour d'un axe de rotation (4) à un premier corps tournant (5), et un élément en forme de cloche (9) qui reçoit les éléments d'embrayage (3) à l'intérieur de celui-ci au moins en partie et qui peut être fixé d'une seule pièce en rotation autour de l'axe de rotation (4) à un second corps tournant (10) qui doit être raccordé de manière cinématique au premier corps tournant (5). De manière plus détaillée, les éléments d'embrayage (3) peuvent être mis en œuvre avec l'élément en forme de cloche (9), contre l'action des moyens élastiques (6) qui peuvent être associés de manière amovible aux éléments d'embrayage (3), pour transférer le mouvement du premier corps tournant (5) au second corps tournant (10). L'accouplement comporte une pluralité d'ouvertures (28) formées sur la surface extérieure de l'élément en forme de cloche (9) pour extraire et insérer au moins l'un des moyens élastiques (6) et des masses supplémentaires (30) qui peuvent être associées aux éléments d'embrayage (3), l'élément de support (2) étant associé au premier corps tournant (5) et l'élément en forme de cloche (9) étant associé au second corps tournant (10).
PCT/IT2010/000201 2010-05-06 2010-05-06 Embrayage centrifuge, en particulier pour des véhicules motorisés à transmission automatique à variation continue et similaires WO2011138804A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/IT2010/000201 WO2011138804A1 (fr) 2010-05-06 2010-05-06 Embrayage centrifuge, en particulier pour des véhicules motorisés à transmission automatique à variation continue et similaires

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IT2010/000201 WO2011138804A1 (fr) 2010-05-06 2010-05-06 Embrayage centrifuge, en particulier pour des véhicules motorisés à transmission automatique à variation continue et similaires

Publications (1)

Publication Number Publication Date
WO2011138804A1 true WO2011138804A1 (fr) 2011-11-10

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PCT/IT2010/000201 WO2011138804A1 (fr) 2010-05-06 2010-05-06 Embrayage centrifuge, en particulier pour des véhicules motorisés à transmission automatique à variation continue et similaires

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104832558A (zh) * 2015-04-10 2015-08-12 浙江亚特电器有限公司 一种离合器冷却系统

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE503046A (fr) *
BG22277A1 (fr) * 1972-07-31 1977-02-20
US5845757A (en) * 1996-12-13 1998-12-08 Ryobi North America, Inc. Centrifugal clutch
CN2871964Y (zh) * 2005-12-30 2007-02-21 三阳工业股份有限公司 离合器构造
FR2895044A1 (fr) * 2005-12-16 2007-06-22 Mikasa Sangyo Kk Embrayage centrifuge pour machine de compactage vibrante.
US20080156609A1 (en) * 2007-01-03 2008-07-03 The Hilliard Corp. Tunable centrifugal clutch
US20090173593A1 (en) * 2008-01-04 2009-07-09 I Lin Clutch Housing
DE202009001968U1 (de) * 2008-10-06 2009-08-13 Tong Yah Electronic Technology Co., Ltd. Kupplung für Motorräder und deren Deckel
CN201335110Y (zh) * 2009-01-09 2009-10-28 光阳工业股份有限公司 车辆离合器结构

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE503046A (fr) *
BG22277A1 (fr) * 1972-07-31 1977-02-20
US5845757A (en) * 1996-12-13 1998-12-08 Ryobi North America, Inc. Centrifugal clutch
FR2895044A1 (fr) * 2005-12-16 2007-06-22 Mikasa Sangyo Kk Embrayage centrifuge pour machine de compactage vibrante.
CN2871964Y (zh) * 2005-12-30 2007-02-21 三阳工业股份有限公司 离合器构造
US20080156609A1 (en) * 2007-01-03 2008-07-03 The Hilliard Corp. Tunable centrifugal clutch
US20090173593A1 (en) * 2008-01-04 2009-07-09 I Lin Clutch Housing
DE202009001968U1 (de) * 2008-10-06 2009-08-13 Tong Yah Electronic Technology Co., Ltd. Kupplung für Motorräder und deren Deckel
CN201335110Y (zh) * 2009-01-09 2009-10-28 光阳工业股份有限公司 车辆离合器结构

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104832558A (zh) * 2015-04-10 2015-08-12 浙江亚特电器有限公司 一种离合器冷却系统

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