WO2006097271A1 - Embrayage a friction centrifuge - Google Patents

Embrayage a friction centrifuge Download PDF

Info

Publication number
WO2006097271A1
WO2006097271A1 PCT/EP2006/002316 EP2006002316W WO2006097271A1 WO 2006097271 A1 WO2006097271 A1 WO 2006097271A1 EP 2006002316 W EP2006002316 W EP 2006002316W WO 2006097271 A1 WO2006097271 A1 WO 2006097271A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive shaft
group according
friction group
splined
friction
Prior art date
Application number
PCT/EP2006/002316
Other languages
English (en)
Inventor
Giovanni Galvano
Original Assignee
Garage Italia 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 Garage Italia S.R.L. filed Critical Garage Italia S.R.L.
Publication of WO2006097271A1 publication Critical patent/WO2006097271A1/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
    • F16D43/06—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like
    • F16D43/08—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces
    • F16D43/10—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces the centrifugal masses acting directly on the pressure ring, no other actuating mechanism for the pressure ring being provided
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F16H55/563—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable actuated by centrifugal masses
    • 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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/067—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions mechanical actuating means

Definitions

  • the present invention relates to an expansion friction group adapted to permit or block the transmission of the rotary movement of a drive shaft, and finds use in any device which functions by exploiting the rotary movement of a drive shaft, for example an automobile .
  • An expansion friction group of known type generally foresees coplanar jaws which extend radially and angularly spaced from a driving shaft and are radially moveable against an internal cylindrical surface of a drum, concentric to these jaws, to which the driven shaft is fixed.
  • the jaws radially extend due to the centrifugal force to which they are subjected by the rotation of the driving shaft, until the angular speed of the driving shaft reaches a limit value such to generate a centrifugal force on them sufficient to hold them against the cylindrical surface of the drum, thus enabling the transmission of the rotary movement from the driving shaft to the driven shaft .
  • one object of the invention is to make an expansion friction group which optimises the friction moment with which the rotation is transmitted while limiting to a maximum the overall size of the group .
  • one object of the invention is to optimise such friction moment by maximising the friction area.
  • Another object of the invention is to make an expansion friction group which is reliable, functional and at the same time extremely versatile in the adjustment of its angular connection speed.
  • Not the last object of the invention is to make an automobile, in particular a four-wheel vehicle, which has a functional, efficient, versatile and economical friction group which is not oversize.
  • a friction group for the transmission of a rotary movement of a drive shaft, characterised in that it has an element splined to said drive shaft in a manner to rotate therewith and a counter element idly splined to said drive shaft, said element having centrifugal operation means for its reversible expansion in the direction of the axis of said drive shaft, from a contracted configuration of disengagement from said counter element to an engagement configuration with said counter element to drive it solidly into rotation.
  • the present invention also discloses an automobile, in particular a four-wheel vehicle, which is characterised in that it has one such friction group.
  • FIG. 1 shows an exploded perspective view of a preferred embodiment of the friction group in accordance with the present invention, wherein the friction group is associated with a centrifugal speed variator group;
  • FIG. 2 shows a side elevation view of the device of figure 1, axially sectioned
  • Figure 3 shows an exploded perspective view of the expandable element of the friction group of figure 1;
  • FIG. 4 shows a plan view of the moveable half-part of the expandable element
  • Figure 5 shows a side elevation view of the axially sectioned expandable element.
  • the friction group 1 has an element 2 splined to a drive shaft in a manner to rotate therewith and a counter element 4 idly splined to the drive shaft 3.
  • the element 2 has centrifugal operation means 5 for its reversible expansion in the direction of the drive shaft 3 axis, from a contracted configuration of disengagement from the counter element 4 to an engagement configuration with the counter element 4 in order to solidly drive it into rotation.
  • the element 2 and the counter element 4 have complementary, mutually engageable surfaces 6 and 7, of conical or frustoconical shape.
  • the friction surface is continuous and very extensive, and ensures, even at low angular rotation velocities of the drive shaft, a high friction moment while maintaining a reduced axial size.
  • At least one of the surfaces 6 and 7, in particular the first, is composed of a high friction coefficient deposit layer 8, for example Ferodo lining.
  • the element 2 has a half-part 9 which is fixed with respect to the drive shaft 3 and faces a half-part 10 which is moveable in the direction of the axis of the drive shaft 3.
  • the expansion means 5 comprise a plurality of preferably spherical rolling elements 11, each positioned in a corresponding seat 14 made between the preferably flat surfaces 12 and 13 and facing the fixed half-part 9 and moveable half-part 10.
  • Each seat 14 is in particular formed by preferably specular impressions on the surfaces 12 and 13.
  • Each seat 14 moreover extends radially with respect to the axis of the drive shaft 3 and has a cam profile 15 that can be operated by the rolling element 11.
  • the cam profile 15 has a groove 40 which holds the rolling element 11 in a radially more external zone 41 of the seat 14 when the friction is connected or in a radially more internal zone 42 of the seat 14 when the friction is disconnected.
  • the rolling element 11 in response to the opposition of its radial centrifugal advancement by the cam profile 15, exerts on the moveable half-part 10 a thrusting force having a component along the direction of the axis of the drive motor 3 .
  • the fixed half-part 9 is made fixed to the rotation of the drive motor 3 by means of a fixing pin 16, while the moveable half-part 10 is idly splined to the drive shaft 3 through a roller bearing 17 borne by a bush 18 which is splined to the drive shaft 3.
  • the friction group 1 thus has anti-rotation means 19 of the moveable half-part 10 with respect to the fixed half-part 9.
  • the anti-rotation means' 19 comprise a plurality of stems 20 which cross through the facing surfaces 12 and 13 with an orientation parallel to the axis of the drive shaft 3 and are slidably inserted in slots 21 of complementary shape.
  • the bush 18 and the fixed half-part 9 are tightly connected in direct contact with each other and are locked with respect to axial translation by means of a nut 43, screwed on the drive shaft 3 on the external side of the fixed half-part 9 and cooperating with a counter shoulder 44, of the drive shaft 3, for the end of the bush 18 opposite to the fixed half-part 9.
  • the friction group 1 moreover has adjustment means of the angular speed of the drive shaft 3, at which the switching occurs from the disengagement configuration to the engagement configuration between the element 2 and the counter element 4.
  • the adjustment means are composed of adjustment elements of the distance present in the disengagement position between the mutually engageable surfaces 7 and 8 of the element 2 and counter element 4.
  • the adjustment elements adjust the distance present, in the configuration of disengagement between the mutually engageable surfaces 7 and 8 of the element 2 and counter element 4 , between the facing surfaces 12 and 13 of the fixed half-part 9 and the moveable half-part 10.
  • the preferred embodiment shows the surfaces 12 and 13 in contact in the configuration of disengagement between the mutually engageable surfaces 7 and 8 of the element 2 and counter element 4, in other solutions the surfaces 12 and 13 may be differently spaced in the configuration of disengagement between the mutually engageable surfaces 7 and 8 of the element 2 and counter element 4.
  • Such adjustment elements are advantageously composed of stems 20, each of which with an adjustable spacing segment between the facing surfaces 12 and 13 of the fixed half-part 9 and moveable half-part 10.
  • the spacing segment is equal to zero.
  • Each stem 20 has a threaded portion 22 engaged in a counter- threaded seat 23 made in the fixed half-part 9, and can be screwed for the adjustment of the spacing segment.
  • a tensioning spring 26 is fit on each stem 20, compressed between the enlarged head 25 of the stem 20 and the counter-threaded seat 23.
  • the spring 26 maintains the set adjustment steady by means of an increase in the contact pressure between the threads of the stem 20 and the seat 23, which determines an increase in the force necessary to screw the stem 20.
  • the friction group 1 is associated with a centrifugal speed variator group 27, it too splined to the drive shaft 3.
  • the variator group 27 is splined to a bush 28 which is in turn idly splined to the drive shaft 3, and has in succession a driving half pulley 29 splined in a fixed manner with respect to the rotation and axial translation, a driving half pulley 30 splined in a fixed manner with respect to the rotation but not to the axial translation, and an elastic conical plate 31, splined in a fixed manner with respect to the rotation and axial translate.
  • the variator group 27 has additional centrifugal rolling elements 32 positioned between the plate 31 and the moveable half pulley 30, adapted to bend the plate 31 during their centrifugal radial displacement in order to cause the displacement of the moveable driving half pulley 30 with respect to the fixed driving half pulley 29.
  • the external side of the moveable half pulley 30, which forces the rolling elements 32 to bend the plate . 31 has a driving cylindrical surface 33 for the external edge of the plate 31 during the bending of the latter.
  • the counter element 4, adjacent to the plate 31, is splined to the bush 28, in a fixed manner with respect to the rotation and axial sliding.
  • the elements splined to the bush 28 are tightly connected to each other by means of a nut 35, screwed to one end of the bush 28 and cooperating with a shoulder 36 of the drive shaft 3 which intercepts the other end of the bush 28.
  • roller bearings 37 are interposed between the bush 28 and the drive shaft 3.
  • One terminal roller bearing 37 has a collar 38 of interposition between the shoulder 36 and the fixed driving half pulley 29.
  • the device comprising the friction group 1 and possibly also the variator group 27 may be adopted for any automobile, and a particularly recommended application is for a four-wheel vehicle, such as that described in the patent application MI2004A002390.
  • the operation of the device according to the invention appears evident from that described and illustrated, and in particular is substantially the following.
  • the drive shaft 3 increases the speed rate until a limit value is reached wherein the centrifugal force acting on the rolling elements 11 is sufficient to move them radially.
  • Every radially moving rolling element 11 acts against the cam profile 15 with a thrusting force having an axial component which then causes the axial displacement of the moveable half-element 10 until this is engaged with the counter element 4.
  • the groove of the pulley formed by the half-parts 29 and 30 widens or tightens with the variation in the rotation speed of the drive shaft 3, due to the radial movement of the rolling elements 32.
  • the belt (not shown) of the driving pulley radially displaces by varying the distance from the rotation shaft 3, and in a manner directly proportional to the variation of such distance, varies the transmitted torque.
  • the materials used, as well as their dimensions, may be of any type according to needs and 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)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

Selon l’invention, le groupe de friction (1) qui assure la transmission d’un mouvement rotatif d’un arbre de transmission possède un élément (2) cannelé à l’arbre afin d’en suivre la rotation et un contre-élément (4) cannelé librement à l’arbre, l’élément (2) disposant de moyens de fonctionnement centrifuge (11) pour son expansion réversible dans la direction de l’axe de l’arbre entre une configuration de contraction où il se désengage du contre-élément (4) et une configuration d’engagement où il est en prise avec le contre-élément (4) pour l’entraîner fermement en rotation.
PCT/EP2006/002316 2005-03-17 2006-03-14 Embrayage a friction centrifuge WO2006097271A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMI2005A000437 2005-03-17
ITMI20050437 ITMI20050437A1 (it) 2005-03-17 2005-03-17 Gruppo frizione ad espansione

Publications (1)

Publication Number Publication Date
WO2006097271A1 true WO2006097271A1 (fr) 2006-09-21

Family

ID=36572035

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/002316 WO2006097271A1 (fr) 2005-03-17 2006-03-14 Embrayage a friction centrifuge

Country Status (2)

Country Link
IT (1) ITMI20050437A1 (fr)
WO (1) WO2006097271A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR510360A (fr) * 1919-07-22 1920-12-03 Alsacienne Constr Meca Manoeuvre au tomatique pour embrayage ou débrayage
US1922931A (en) * 1930-06-12 1933-08-15 Defays Victor Jean Joseph Clutching device
GB525777A (en) * 1939-02-28 1940-09-04 Borg & Beck Co Ltd Improvements in or relating to centrifugal clutches
DE1963173A1 (de) * 1969-12-17 1971-06-24 Leopold Ruess Fliehkraftkupplung
US4564357A (en) * 1981-07-31 1986-01-14 Valeo Pulley assembly
JPH11336862A (ja) * 1998-05-25 1999-12-07 Koyo Seiko Co Ltd 可変径プーリ
US20040224806A1 (en) * 2003-04-18 2004-11-11 Mitsugi Chonan Continuously variable transmission

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR510360A (fr) * 1919-07-22 1920-12-03 Alsacienne Constr Meca Manoeuvre au tomatique pour embrayage ou débrayage
US1922931A (en) * 1930-06-12 1933-08-15 Defays Victor Jean Joseph Clutching device
GB525777A (en) * 1939-02-28 1940-09-04 Borg & Beck Co Ltd Improvements in or relating to centrifugal clutches
DE1963173A1 (de) * 1969-12-17 1971-06-24 Leopold Ruess Fliehkraftkupplung
US4564357A (en) * 1981-07-31 1986-01-14 Valeo Pulley assembly
JPH11336862A (ja) * 1998-05-25 1999-12-07 Koyo Seiko Co Ltd 可変径プーリ
US20040224806A1 (en) * 2003-04-18 2004-11-11 Mitsugi Chonan Continuously variable transmission

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 03 30 March 2000 (2000-03-30) *

Also Published As

Publication number Publication date
ITMI20050437A1 (it) 2006-09-18

Similar Documents

Publication Publication Date Title
US9476465B2 (en) Spatial wedging friction overrunning clutch
GB2332027A (en) Wear-adjusting device for a disc brake for a motor vehicle
US20130118853A1 (en) Decoupling Pulley
US9933024B2 (en) Variable two-way over-running clutch
SE508936C2 (sv) Drivorgan för inställning av en mutter i ett förband för anbringande av vridmoment på muttern samt vridbar hylsnyckelkropp till drivorganet
EP2670991B1 (fr) Palier à roulement pour dispositif de galet tendeur de courroie
CN106233018A (zh) 凸轮机构
EP0550261B1 (fr) Dispositif de transmission pour force motrice
TW577964B (en) Tensioner
WO2006097271A1 (fr) Embrayage a friction centrifuge
US20170198756A1 (en) Disengaging overload clutch with latching by way of magnetically loaded control elements
US3547242A (en) Torque limiting devices or overload clutches
US20100236355A1 (en) Variable eccentricity assembly
KR100326407B1 (ko) 샤프트의연결및검사방법과장치
CA2182632A1 (fr) Outil a impulsions
JP2881653B2 (ja) トルク制限継手装置
US20180104801A1 (en) Torque-limiting driver with embodied roller
US4013156A (en) Centrifugal clutch
KR100670953B1 (ko) 제동력 조정이 가능한 에어 브레이크
US20110308906A1 (en) Mechanical device for the transmission of a force with a threshold
EP2522872B1 (fr) Embrayage à disques avec engagement / dégagement centrifuge
EP2841736A1 (fr) Assemblage d'axe de piston
US6300692B1 (en) Linear actuator with expansion device
DE102008012682A1 (de) Kupplung für eine Ausgleichswelle einer Brennkraftmaschine
WO1999023362A1 (fr) Mecanisme de changement de phase

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application
NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: RU

WWW Wipo information: withdrawn in national office

Country of ref document: RU

122 Ep: pct application non-entry in european phase

Ref document number: 06707552

Country of ref document: EP

Kind code of ref document: A1

WWW Wipo information: withdrawn in national office

Ref document number: 6707552

Country of ref document: EP