EP1298318B1 - Starter drive with clutch in particular for an internal combustion engine in a vehicle - Google Patents

Starter drive with clutch in particular for an internal combustion engine in a vehicle Download PDF

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Publication number
EP1298318B1
EP1298318B1 EP02291951.8A EP02291951A EP1298318B1 EP 1298318 B1 EP1298318 B1 EP 1298318B1 EP 02291951 A EP02291951 A EP 02291951A EP 1298318 B1 EP1298318 B1 EP 1298318B1
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EP
European Patent Office
Prior art keywords
crown
driver
reliefs
driven
damping
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.)
Expired - Lifetime
Application number
EP02291951.8A
Other languages
German (de)
French (fr)
Other versions
EP1298318A3 (en
EP1298318A2 (en
Inventor
Alain Chauville
Zeng Gang Liu
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.)
Valeo Equipements Electriques Moteur SAS
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Valeo Equipements Electriques Moteur SAS
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Publication date
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Publication of EP1298318A2 publication Critical patent/EP1298318A2/en
Publication of EP1298318A3 publication Critical patent/EP1298318A3/en
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Publication of EP1298318B1 publication Critical patent/EP1298318B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
    • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N11/00—Starting of engines by means of electric motors
    • F02N11/02—Starting of engines by means of electric motors the motors having longitudinally-shiftable rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/022—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch
    • F02N15/023—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the overrunning type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
    • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
    • F02N15/062—Starter drives
    • F02N15/063—Starter drives with resilient shock absorbers

Definitions

  • the present invention relates to starters, for a thermal engine, in particular for a motor vehicle, provided with a toothed launching wheel, of the type comprising an electric motor, a launcher carrying a pinion for rotating the motor gearwheel. thermal and movable on an output shaft in rotation with the shaft of the electric motor between a passive position in which the pinion does not mesh the gear wheel and the motor is not excited, and an active position in which the pinion meshes with the toothed wheel and in which the motor is excited; the launcher comprising a coaxial inlet portion and rotatably connected to the X-X longitudinal axis output shaft, an output portion rotatably connected to the pinion, and a rotational coupling device of the two parts.
  • Starters of this type are known from the prior art for example by the documents FR A 2,772,473 and FR A 2,795,884 . It turned out that the mechanical organs of the launcher and more generally of the starter undergo shocks during the starting phase of the engine. Axial shocks when the launcher is moved against the toothed wheel of the engine, torsional shocks when the pinion meshes with the gear wheel. These shocks are dimensioning for the design of the pinion, and can also cause wear of the mechanical parts of the launcher and more generally of the starter.
  • the disengageable coupling device comprises a conical clutch having a frustoconical friction surface carried by the outlet portion and cooperating with a complementary frustoconical friction surface carried by the inlet portion. It is important to spare these frustoconical friction surfaces.
  • the coupling device comprises two members that can be fixed in rotation by the damping means.
  • disengageable coupling device and the shock-absorbing means are arranged concentrically, which makes it necessary to increase the radial size of the starter fixing casing to the fixed part of the vehicle, knowing that this casing serves as housing for the launcher .
  • the object of the present invention is not to increase the radial size of the coupling device while providing it with an at least torsional shock-absorbing means.
  • the radial space of the launcher is not increased and the bell is split into two elements namely the driver and the ring between which is involved circumferentially the coupling means placed axially between the ring and the driver .
  • the coupling device is of the roller type, each of which is engaged between a track portion of the upstream coupling portion and a track portion of the downstream coupling portion; the downstream coupling part, of a cylindrical shape, extending coaxially in said ring.
  • the trainer comprises a base having substantially the shape of a disk coaxial with the output shaft and driving reliefs on the face of the base facing towards the pinion extending to the once in a radial direction and in an axial direction, the crown having raised reliefs oriented towards the driving reliefs extending both in a radial direction and in an axial direction, the damping means comprising a plurality of damping elements, each damping element being arranged between a driving relief and a led relief.
  • leading and driven reliefs are distributed angularly equidistantly on their support surface in a circle centered on the axis of the latter, the reliefs being equal in number to the number of leading reliefs. .
  • the damping elements are grouped in pairs which each form an assembly in which the two damping elements are connected by a connecting element so that a notch is formed between them, a relief leading or a led relief being engaged in the notch.
  • the section of each relief leading or led in a plane perpendicular to the longitudinal axis X-X adopts the shape of a radial tab having two rectilinear lateral faces converging towards the longitudinal axis X-X.
  • each connecting element contributes to damping the shocks in the axial direction.
  • the ring and the member of the outlet portion delimit between them tangential housings having a radial width evolving, in a first direction of rotation, between a minimum width and a maximum width, and that a spring prestressed in compression and a roller urged by the spring in direction of the minimum width of the housing are arranged in each housing, the ring bearing substantially radial internal ribs separating two adjacent housing on each of which bears one of the springs, and in that the raised reliefs are the axial extension of these grooves internal.
  • a washer is interposed between the damping means and the rollers to prevent axial displacements of the rollers caused by the deformation of the damping means.
  • FIG. figure 1 To facilitate the understanding of the invention, the general structure of a conventional starter will first be described with reference to FIG. figure 1 .
  • a motor vehicle comprises a heat engine, which for its start, is provided with a launching wheel or toothed start (not shown) intended to be rotated by the pinion of a starter.
  • This starter essentially comprises an electric motor 1 whose driving shaft 2 drives in rotation about an axis XX an output shaft 2 'axially aligned on the shaft 2, a launcher 3 axially sliding on the shaft 2' but secured in rotation thereof and carrying a pinion 5 driving in rotation of the toothed launching wheel, and a pivoting fork 4 moving the launcher 3 axially on the shaft 2 ', between a passive position of rest and a active engagement position.
  • a gear reduction gear with epicyclic gear train operates in a known manner between the two shafts 2, 2 '.
  • the output shaft is integral in rotation with the shaft of the electric motor, constituting the armature shaft thereof. All of these elements are enclosed in a housing 6 serving to support an electromagnetic contactor (not shown) extending parallel to the electric motor.
  • the casing 6 is also used for fixing the starter on a fixed part of the motor vehicle.
  • the radial size of the casing 6 is not modified thanks to the characteristics of the invention described below.
  • the contactor is described for example in the document FR A 2,795,884 , which will be referred to for more details, and therefore comprises a coil connected to the starter switch of the motor vehicle, a mobile core, a fixed core, a movable contact and springs.
  • the fork is connected, here via a spring, to the mobile core.
  • This mobile core when the coil is activated following a closing of the start switch, moves to act on a movable contact intended to come into contact with pads, one of which is connected to the positive terminal of the battery of the vehicle and the other to the electric motor 1, for powering the electric motor 1.
  • the movable core pivots the fork 4, which moves the launcher 3.
  • the pinion 5 mounted at one end of the launcher 3, meshes with the throwing wheel of the engine to start it and comes into contact with a stop (not referenced) worn by the end of the output shaft 2 '.
  • the launcher 3 comprises, on the one hand, an input portion 7, rotatably connected to the shaft 2 'by a complementary helical spline link acting locally between the inner periphery of the input portion 7 and the outer periphery of the shaft 2 ', and, on the other hand, an outlet portion 8 comprising the pinion 5.
  • the invention essentially relates to the launcher 3 traversed by the output shaft 2 ', which will be described below with reference to the Figures 2 to 8 .
  • the inlet portion 7 comprises, axially aligned on the axis XX, a tubular input shaft segment, constituting an axially oriented inlet tubular sleeve, carrying a gutter-shaped fork guide 11 or annular groove, in which is engaged the control end 4 'of the fork 4, and an upstream coupling portion 12.
  • the tubular sleeve 10 locally present internally at its inner periphery the aforementioned helical grooves to engage in a complementary manner with the helical grooves locally present at its outer periphery the output shaft 2 'so that the sleeve 10 is rotatably connected to the output shaft 2' but can move axially relative thereto.
  • the outlet portion 8 essentially consists of a tubular output shaft segment 13, constituting an axially oriented output tubular sleeve, carrying the pinion 5 at its front end 14 and a coupling downstream portion 15 at its rear end 16.
  • the coupling device 9 disengageable is as on the figure 1 of pebble type.
  • the rollers bear the reference 22.
  • the upstream coupling part 12 comprises according to a feature of the invention, a driver 17, of transverse orientation, integral with the inlet sleeve 10, a ring 18, axially oriented, movable relative to the driver 17, a hollow-shaped assembly cover 19 linking the driver 17 and the ring gear 18 in axial translation to one another.
  • a damping means 20 is placed axially between the driver 17 and the ring 18 and ensures the connection in rotation between them.
  • the damping means 20 intervenes axially and circumferentially between the ring 18 and the driver 17 rigidly connected to the inlet sleeve 10.
  • This damping means is circumferentially elastic so that the ring 18 and the driver 17 belong to a damper of torsion with circumferential action.
  • the material of the rear end of the cover 19 is folded radially in contact with the rear face of the driver 17 for axial setting of the driver assembly 17- 20-ring damping means 18 between the front wall of transverse orientation , traversed by the shaft 2 ', the cover 19 and the folded material of the rear end of the cover 19 having an annular flange of axial orientation within which is housed said assembly.
  • the downstream coupling portion 15 is formed by the rear end 16 of the output shaft 13, which has a cylindrical outer surface defining a track 21 rolling for the rollers 22 which are interposed between the track 21 and the inner surface of the ring 18 as it will be exposed below.
  • the rear end 16 is of a diameter slightly greater than the rest of the shaft 13. The downstream coupling part 15 is engaged coaxially in the mobile ring 18.
  • the driver 17 comprises a base 25 having substantially the shape of a disc coaxial with the axis XX and having a front face 26 facing the pinion 5.
  • the driver 17 belongs to a torsion damper comprising the means 20.
  • the ring 18 has a dual function because it belongs to the coupling device 9 and cooperates with the damping means belonging to a circumferential action torsion damper.
  • the ring 18 has substantially the shape of a cylinder coaxial with the axis XX, having a wall of a certain radial thickness and having a rear end face 28 oriented towards the base 25.
  • Conducted reliefs 29 extending both in a radial direction and in an axial direction protrude from the face 28 of the ring 18.
  • the outer diameter of the ring 18 is substantially the same as that of the base 25 of the driver 17.
  • leading reliefs 27 and led 29 are distributed, preferably, angularly equidistantly on their support surface in a circle centered on the axis of the latter.
  • the reliefs 29 are equal in number to the number of leading reliefs 27.
  • the damping means 20 comprises a plurality of damping elements 30, typically blocks, which are each arranged, in a plane perpendicular to the axis XX, between a driving relief 27 and a raised relief 29, as illustrated in FIG. figure 3 .
  • the damping elements 30 are grouped in pairs which each form an assembly in which the two elements 30 are connected by a connecting element 31 so that a notch 32 is formed between them.
  • the driving reliefs 27 each engage in a notch 32, so that these driving reliefs 27 are capped by the connecting elements 31 which separate them from the crown 18.
  • the raised features 29 s interposed between each pair of damping elements 30.
  • each driving relief 27 or led 29 in a plane perpendicular to the longitudinal axis X-X preferably adopts the shape of a radial tab having two rectilinear lateral faces converging towards the longitudinal axis X-X.
  • the tabs extend from the peripheral surface of the base 25 and the crown 18.
  • the damping elements 30 are elastic and made of elastomer, for example rubber or a suitable synthetic elastic material. Alternatively the damping elements are metallic and have for example an accordion shape.
  • the raised reliefs 29 are separated from the base 25 of the coach 17 by a set J.
  • the cover 19 envelops the assembly consisting of the driver 17, the damping means 20 and the ring 18 radially and in both axial directions. In addition to the functions described above, it also ensures the connection in axial translation between the ring 18 and the outlet portion 8.
  • the cover 19 consists of a thin cylindrical wall of axis XX, the two axial faces being partially closed by thin walls substantially shaped discs recessed in their centers.
  • the ring 18 and the track 21 delimit between them tangential housing 24 having a radial width moving in the direction of rotation R, between a minimum width and a maximum width.
  • a spring 23 prestressed in compression and a roller 22 coaxial with the ring gear 18 are arranged in each housing 24.
  • the ring gear 18 carries radial internal ribs 34 separating two adjacent housings 24, the spring 23 bearing on one side on a rib 34 , and the roller 22 being biased by the spring 23 towards the minimum width of the housing 24.
  • the roller 22 rolls on the track 21 and on the bottom of the housing 24 which faces it, in the opposite direction to R and is wedged in the zone of minimum width of the 24. The roller 22 then prevents the track 21 and the ring 18 to move relative to each other, and thus ensures the transmission of torque.
  • the roller 22 rolls on the track 21 and on the bottom of the housing 24 which faces it, in the direction of R, thus towards the zone of greater width of the housing 24.
  • the roller 22 reaches a point where the width of the housing 24 is greater than the diameter of the roller 22, it can then roll freely on the track 21 because it is no longer in contact with the bottom of the housing 24.
  • the track 21 and the ring 18 are free to rotate relative to each other, and the transmission of the couple is no longer insured.
  • a washer 33 of axis XX is interposed between the damping means 20 and the ring gear 18 so as to separate the damping means 20 from the rollers 22 in order to avoid axial displacements of the rollers 22 caused by the deformation of the damping means 20.
  • the outer edge of the washer 33 is cut to fit the shape of the reliefs carried out 29.
  • the torsional shocks propagating from the driving axle 2 towards the pinion 6 or in the opposite direction therefore pass respectively from the driving reliefs 27 to the raised reliefs 29 or from the reliefs led 29 to the driving reliefs 27 , and are damped in both cases by the deformation of the damping elements 30 located between them.
  • the connecting elements 31 and the damping elements 30 absorb part of the energy transmitted between the ring 18 and the driver 17 by deformation.
  • the clearance J is dimensioned in such a way that the deformation of the connecting elements 31 and of the damping elements 30 does not cause contacts between the led projections 29 and the base 25 of the driver 17.
  • the connecting elements 31 contribute to damping the axial shock.
  • an upstream coupling portion 12 consisting of a ring gear 18 secured to a driver 17, rigidly connected to the sleeve 10, via a damping means 20, in place of a bell in the old art, has the advantage of allowing a slight deformation of the upstream coupling portion 12 without the axis of the ring 18 being modified, the deformation being absorbed by the damping means 20, This prevents the rollers 22 cantilever with respect to the track 21 and the bottom of the housing 24 and therefore limits the risk of chipping.
  • FIGS. 7 and 8 illustrate a second embodiment of the invention in which the raised reliefs 29 are constituted by the extension in the axial direction of the ribs 34.
  • the raised reliefs 29 therefore do not extend radially to the periphery of the crown 18.
  • the ring 18 extends radially to the front face of the base 25.
  • the distribution and the shape of the driving reliefs 27 are complementary to those of the led reliefs, the driving reliefs 27 being interlocked between the raised projections 29, inside the ring gear 18, and the damping elements 30 being also arranged inside the crown 18, each between a leading relief 27 and a raised relief 29.
  • This second embodiment allows a simpler and less expensive manufacture of the rings 18.
  • the disengageable coupling device is of the conical clutch type, the ring gear 18 bearing at its inner or outer periphery a frustoconical friction surface capable of cooperating in a complementary manner with a frustoconical friction surface carried by the rear end 16 of the downstream part 15.
  • the ring gear 18 bearing at its inner or outer periphery a frustoconical friction surface capable of cooperating in a complementary manner with a frustoconical friction surface carried by the rear end 16 of the downstream part 15.
  • downstream coupling part extends coaxially with respect to the crown.
  • This downstream part enters the ring gear or, alternatively, surrounds the ring gear when the coupling device comprises a conical clutch with a friction surface of the type of ring.
  • the coupling device comprises a conical clutch with a friction surface of the type of ring.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Description

La présente invention concerne des démarreurs, pour moteur thermique, notamment de véhicule automobile, doté d'une roue de lancement dentée, du type comprenant un moteur électrique, un lanceur porteur d'un pignon d'entraînement en rotation de la roue dentée du moteur thermique et déplaçable sur un arbre de sortie solidaire en rotation de l'arbre du moteur électrique entre une position passive dans laquelle le pignon n'engrène pas la roue dentée et le moteur n'est pas excité, et une position active dans laquelle le pignon engrène avec la roue dentée et dans laquelle le moteur est excité ; le lanceur comprenant une partie d'entrée coaxiale et liée en rotation à l'arbre de sortie d'axe longitudinal X-X, une partie de sortie liée en rotation au pignon, et un dispositif d'accouplement en rotation des deux parties.The present invention relates to starters, for a thermal engine, in particular for a motor vehicle, provided with a toothed launching wheel, of the type comprising an electric motor, a launcher carrying a pinion for rotating the motor gearwheel. thermal and movable on an output shaft in rotation with the shaft of the electric motor between a passive position in which the pinion does not mesh the gear wheel and the motor is not excited, and an active position in which the pinion meshes with the toothed wheel and in which the motor is excited; the launcher comprising a coaxial inlet portion and rotatably connected to the X-X longitudinal axis output shaft, an output portion rotatably connected to the pinion, and a rotational coupling device of the two parts.

Des démarreurs de ce type sont connus de l'art antérieur par exemple par les documents FR A 2 772 473 et FR A 2 795 884 . Il s'est avéré que les organes mécaniques du lanceur et plus généralement du démarreur subissent des chocs pendant la phase de démarrage du moteur thermique. Des chocs axiaux quand le lanceur est déplacé contre la roue dentée du moteur thermique, des chocs torsionnels quand le pignon engrène la roue dentée. Ces chocs sont dimensionnant pour la conception du pignon, et peuvent également provoquer l'usure des pièces mécaniques du lanceur et plus généralement du démarreur.Starters of this type are known from the prior art for example by the documents FR A 2,772,473 and FR A 2,795,884 . It turned out that the mechanical organs of the launcher and more generally of the starter undergo shocks during the starting phase of the engine. Axial shocks when the launcher is moved against the toothed wheel of the engine, torsional shocks when the pinion meshes with the gear wheel. These shocks are dimensioning for the design of the pinion, and can also cause wear of the mechanical parts of the launcher and more generally of the starter.

Il est connu par le document FR A 2 795 884 d'utiliser des dispositifs d'accouplement débrayables comprenant une cloche entraînée en rotation par la partie d'entrée, un arbre tubulaire constituant une extrémité de la partie de sortie et dont la surface extérieure définit une piste, et des organes d'accouplement unidirectionnel liant la piste à la cloche pour la transmission du couple orienté suivant un premier sens, et permettant à la cloche de tourner librement par rapport à la piste quand le couple est orienté en sens opposé. Ces organes sont des galets, typiquement liés à des ressorts et disposés dans des logements de formes adaptés pratiqués dans la cloche.He is known by the document FR A 2,795,884 using disengageable coupling devices comprising a bell rotated by the inlet portion, a tubular shaft constituting an end of the outlet portion and whose outer surface defines a track, and unidirectional coupling members binding the track to the bell for transmitting the torque oriented following a first direction, and allowing the bell to rotate freely relative to the track when the torque is oriented in the opposite direction. These bodies are rollers, typically linked to springs and arranged in housings of suitable shapes made in the bell.

Ces cloches sont constituées d'une seule pièce, qui se déforme lors du passage du couple entre l'axe du moteur électrique et la piste de roue libre. Cette déformation peut entraîner une usure et un écaillage prématuré des galets et de la piste.These bells consist of a single piece, which deforms during the passage of torque between the axis of the electric motor and the freewheel track. This deformation can lead to premature wear and peeling of the rollers and the track.

En variante comme décrit dans le document FR A 2 772 433 le dispositif d'accouplement débrayable comporte un embrayage conique doté d'une surface de frottement tronconique porté par la partie de sortie et coopérant avec une portée de frottement tronconique complémentaire portée par la partie d'entrée. Il importe de ménager ces surfaces de frottement tronconiques.Alternatively as described in the document FR A 2,772,433 the disengageable coupling device comprises a conical clutch having a frustoconical friction surface carried by the outlet portion and cooperating with a complementary frustoconical friction surface carried by the inlet portion. It is important to spare these frustoconical friction surfaces.

Dans le but de remédier à ces inconvénients il a été proposé dans le document FR A 2 754 856 , conforme au préambule de la revendication 1, de doter le dispositif d'accouplement d'un moyen d'amortissement des chocs mécaniques, au moins torsionnels.In order to remedy these drawbacks, it was proposed in document FR A 2,754,856 , according to the preamble of claim 1, to provide the coupling device with a means of damping mechanical shocks, at least torsional.

Selon une caractéristique avantageuse, le dispositif d'accouplement comprend deux organes solidarisables en rotation par le moyen d'amortissement.According to an advantageous characteristic, the coupling device comprises two members that can be fixed in rotation by the damping means.

En pratique le dispositif d'accouplement débrayable et le moyen d'amortissement des chocs sont agencés concentriquement ce qui nécessite d'augmenter la taille radiale du carter de fixation du démarreur à la partie fixe du véhicule, sachant que ce carter sert de logement au lanceur.In practice the disengageable coupling device and the shock-absorbing means are arranged concentrically, which makes it necessary to increase the radial size of the starter fixing casing to the fixed part of the vehicle, knowing that this casing serves as housing for the launcher .

La présente invention a pour objet de ne pas augmenter la taille radiale du dispositif d'accouplement tout en dotant celui-ci d'un moyen d'amortissement des chocs au moins torsionnel.The object of the present invention is not to increase the radial size of the coupling device while providing it with an at least torsional shock-absorbing means.

Suivant l'invention cet objet est résolu par la partie caractérisante de la revendication 1.According to the invention this object is solved by the characterizing part of claim 1.

Grâce à l'invention l'encombrement radial du lanceur n'est pas augmenté et la cloche est scindée en deux éléments à savoir l'entraîneur et la couronne entre lesquels intervient circonférentiellement le moyen d'accouplement placé axialement entre la couronne et l'entraîneur.Thanks to the invention the radial space of the launcher is not increased and the bell is split into two elements namely the driver and the ring between which is involved circumferentially the coupling means placed axially between the ring and the driver .

Selon une autre caractéristique avantageuse de l'invention, le dispositif d'accouplement est du type à galets, dont chacun est engagé entre une portion de piste de la partie amont d'accouplement et une portion de piste de la partie aval d'accouplement ; la partie aval d'accouplement, d'une forme cylindrique, s'étendant coaxialement dans ladite couronne.According to another advantageous characteristic of the invention, the coupling device is of the roller type, each of which is engaged between a track portion of the upstream coupling portion and a track portion of the downstream coupling portion; the downstream coupling part, of a cylindrical shape, extending coaxially in said ring.

Selon une autre caractéristique avantageuse de l'invention, l'entraîneur comprend une base ayant sensiblement la forme d'un disque coaxial à l'arbre de sortie et des reliefs menants sur la face de la base orientée vers le pignon s'étendant à la fois suivant une direction radiale et suivant une direction axiale, la couronne présentant des reliefs menés orientés vers les reliefs menants s'étendant à la fois suivant une direction radiale et suivant une direction axiale, le moyen d'amortissement comportant une pluralité d'éléments amortisseurs, chaque élément amortisseur étant disposé entre un relief menant et un relief mené.According to another advantageous characteristic of the invention, the trainer comprises a base having substantially the shape of a disk coaxial with the output shaft and driving reliefs on the face of the base facing towards the pinion extending to the once in a radial direction and in an axial direction, the crown having raised reliefs oriented towards the driving reliefs extending both in a radial direction and in an axial direction, the damping means comprising a plurality of damping elements, each damping element being arranged between a driving relief and a led relief.

Selon une autre caractéristique avantageuse de l'invention, les reliefs menants et menés sont distribués de façon angulairement équidistante sur leur surface de support en un cercle centré sur l'axe de ce dernier, les reliefs menés étant en nombre égal au nombre de reliefs menants.According to another advantageous characteristic of the invention, the leading and driven reliefs are distributed angularly equidistantly on their support surface in a circle centered on the axis of the latter, the reliefs being equal in number to the number of leading reliefs. .

Selon une autre caractéristique avantageuse de l'invention, les éléments amortisseurs sont groupés par paires qui forment chacune un ensemble dans lequel les deux éléments amortisseurs sont reliés par un élément de liaison de telle façon qu'une encoche soit formée entre eux, un relief menant ou un relief mené étant engagé dans l'encoche.According to another advantageous characteristic of the invention, the damping elements are grouped in pairs which each form an assembly in which the two damping elements are connected by a connecting element so that a notch is formed between them, a relief leading or a led relief being engaged in the notch.

Selon une autre caractéristique avantageuse de l'invention, la section de chaque relief menant ou mené dans un plan perpendiculaire à l'axe longitudinal X-X adopte la forme d'une patte radiale présentant deux faces latérales rectilignes convergeantes vers l'axe longitudinal X-X.According to another advantageous characteristic of the invention, the section of each relief leading or led in a plane perpendicular to the longitudinal axis X-X adopts the shape of a radial tab having two rectilinear lateral faces converging towards the longitudinal axis X-X.

Selon une autre caractéristique avantageuse de l'invention, chaque élément de liaison contribue à amortir les chocs suivant la direction axiale.According to another advantageous characteristic of the invention, each connecting element contributes to damping the shocks in the axial direction.

Selon une caractéristique avantageuse de l'invention, la couronne et l'organe de la partie de sortie délimitent entre eux des logements tangentiels présentant une largeur radiale évoluant, dans un premier sens de rotation, entre une largeur minimale et une largeur maximale, et en ce que un ressort précontraint en compression et un galet sollicité par le ressort en direction de la largeur minimale du logement sont disposés dans chaque logement, la couronne portant des nervures internes sensiblement radiales séparant deux logements adjacents sur chacune desquelles prend appui l'un des ressorts, et en ce que les reliefs menés sont la prolongation axiale de ces rainures internes.According to an advantageous characteristic of the invention, the ring and the member of the outlet portion delimit between them tangential housings having a radial width evolving, in a first direction of rotation, between a minimum width and a maximum width, and that a spring prestressed in compression and a roller urged by the spring in direction of the minimum width of the housing are arranged in each housing, the ring bearing substantially radial internal ribs separating two adjacent housing on each of which bears one of the springs, and in that the raised reliefs are the axial extension of these grooves internal.

Selon une caractéristique avantageuse de l'invention, une rondelle est interposée entre le moyen d'amortissement et les galets pour éviter des déplacements axiaux des galets provoqués par la déformation du moyen d'amortissement.According to an advantageous characteristic of the invention, a washer is interposed between the damping means and the rollers to prevent axial displacements of the rollers caused by the deformation of the damping means.

D'autres caractéristiques et avantages de l'invention ressortiront clairement de la description qui en est faite ci-après, à titre indicatif et nullement limitatif, en référence aux dessins annexés, dans lesquels:

  • la Figure 1 est une vue en coupe longitudinale, illustrant un démarreur conforme à l'art antérieur ;
  • la Figure 2 est une vue en perspective du lanceur conforme à un premier mode de réalisation de l'invention ;
  • la Figure 3 est une autre vue en perspective du lanceur selon la figure 2 ;
  • la Figure 4 est une vue éclatée du lanceur selon la figure 2 ;
  • la Figure 5 est une vue en coupe d'un détail de la figure 4 ;
  • la Figure 6 est une vue en coupe d'un détail de la figure 2 ;
  • la Figure 7 est une vue éclatée d'un lanceur conforme à un second mode de réalisation de l'invention ;
  • la Figure 8 est une vue en perspective montrant le lanceur selon la figure 7 à l'état assemblé.
Other characteristics and advantages of the invention will emerge clearly from the description which is given hereinafter, by way of indication and in no way limitative, with reference to the appended drawings, in which:
  • the Figure 1 is a longitudinal sectional view, illustrating a starter according to the prior art;
  • the Figure 2 is a perspective view of the launcher according to a first embodiment of the invention;
  • the Figure 3 is another perspective view of the launcher according to the figure 2 ;
  • the Figure 4 is an exploded view of the launcher according to the figure 2 ;
  • the Figure 5 is a sectional view of a detail of the figure 4 ;
  • the Figure 6 is a sectional view of a detail of the figure 2 ;
  • the Figure 7 is an exploded view of a launcher according to a second embodiment of the invention;
  • the Figure 8 is a perspective view showing the launcher according to the figure 7 in the assembled state.

Pour faciliter la compréhension de l'invention, on décrira d'abord la structure générale d'un démarreur classique en se référant à la figure 1.To facilitate the understanding of the invention, the general structure of a conventional starter will first be described with reference to FIG. figure 1 .

Ainsi qu'on le sait un véhicule automobile comporte un moteur thermique, qui pour son démarrage, est doté d'une roue de lancement ou de démarrage dentée (non représentée) destinée à être entraînée en rotation par le pignon d'un démarreur. Ce démarreur comprend essentiellement un moteur électrique 1 dont l'arbre moteur 2 entraîne en rotation autour d'un axe X-X un arbre de sortie 2' axialement aligné sur l'arbre 2, un lanceur 3 axialement coulissant sur l'arbre 2' mais solidaire en rotation de celui-ci et porteur d'un pignon 5 d'entraînement en rotation de la roue de lancement dentée, et une fourchette pivotante 4 déplaçant le lanceur 3 axialement sur l'arbre 2', entre une position passive de repos et une position active d'engagement.As is known, a motor vehicle comprises a heat engine, which for its start, is provided with a launching wheel or toothed start (not shown) intended to be rotated by the pinion of a starter. This starter essentially comprises an electric motor 1 whose driving shaft 2 drives in rotation about an axis XX an output shaft 2 'axially aligned on the shaft 2, a launcher 3 axially sliding on the shaft 2' but secured in rotation thereof and carrying a pinion 5 driving in rotation of the toothed launching wheel, and a pivoting fork 4 moving the launcher 3 axially on the shaft 2 ', between a passive position of rest and a active engagement position.

A la figure 1 un réducteur de vitesse à train d'engrenage épicycloïdal intervient de manière connue entre les deux arbres 2, 2'. En variante les deux arbres 2 et 2' sont confondus. Dans tous les cas l'arbre de sortie est solidaire en rotation de l'arbre du moteur électrique, constituant l'arbre d'induit de celui-ci. L'ensemble de ces éléments est enfermé dans un carter 6 servant de support à un contacteur électromagnétique (non représenté) s'étendant parallèlement au moteur électrique. Le carter 6 sert également à la fixation du démarreur sur une partie fixe du véhicule automobile. L'encombrement radial du carter 6 n'est pas modifié grâce aux caractéristiques de l'invention décrites ci-après.To the figure 1 a gear reduction gear with epicyclic gear train operates in a known manner between the two shafts 2, 2 '. In a variant, the two shafts 2 and 2 'coincide. In all cases the output shaft is integral in rotation with the shaft of the electric motor, constituting the armature shaft thereof. All of these elements are enclosed in a housing 6 serving to support an electromagnetic contactor (not shown) extending parallel to the electric motor. The casing 6 is also used for fixing the starter on a fixed part of the motor vehicle. The radial size of the casing 6 is not modified thanks to the characteristics of the invention described below.

Le contacteur est décrit par exemple dans le document FR A 2 795 884 , auquel on se reportera pour plus de précisions, et comporte donc une bobine reliée à l'interrupteur de démarrage du véhicule automobile, un noyau mobile, un noyau fixe, un contact mobile et des ressorts. La fourchette est reliée, ici via un ressort, au noyau mobile. Ce noyau mobile, lorsque la bobine est activée suite à une fermeture de l'interrupteur de démarrage, se déplace pour agir sur un contact mobile destiné à venir en contact avec des plots, dont l'un est relié à la borne positive de la batterie du véhicule et l'autre au moteur électrique 1, pour alimentation électrique du moteur électrique 1. Lors de son déplacement le noyau mobile fait pivoter la fourchette 4, qui déplace le lanceur 3.The contactor is described for example in the document FR A 2,795,884 , which will be referred to for more details, and therefore comprises a coil connected to the starter switch of the motor vehicle, a mobile core, a fixed core, a movable contact and springs. The fork is connected, here via a spring, to the mobile core. This mobile core, when the coil is activated following a closing of the start switch, moves to act on a movable contact intended to come into contact with pads, one of which is connected to the positive terminal of the battery of the vehicle and the other to the electric motor 1, for powering the electric motor 1. During its movement, the movable core pivots the fork 4, which moves the launcher 3.

Dans la position active (moteur électrique 1 alimenté ou excité), le pignon 5, monté à une extrémité du lanceur 3, engrène la roue de lancement du moteur thermique pour démarrer celui-ci et vient en contact avec une butée (non référencée) portée par l'extrémité de l'arbre de sortie 2'.In the active position (electric motor 1 powered or energized), the pinion 5, mounted at one end of the launcher 3, meshes with the throwing wheel of the engine to start it and comes into contact with a stop (not referenced) worn by the end of the output shaft 2 '.

Dans la position passive de repos (moteur électrique non excité), le pignon 5 est désengagé de cette roue de lancement et occupe la position illustrée à la figure 1.In the passive rest position (electric motor not energized), the pinion 5 is disengaged from this launch wheel and occupies the position illustrated in FIG. figure 1 .

Le lanceur 3 comprend, d'une part, une partie d'entrée 7, liée en rotation à l'arbre 2' par une liaison à cannelures hélicoïdales complémentaires intervenant localement entre la périphérie interne de la partie d'entrée 7 et la périphérie externe de l'arbre 2', et, d'autre part, une partie de sortie 8 comprenant le pignon 5. Un dispositif d'accouplement 9 débrayable, ici à roue libre à galets en variante à embrayage conique, intervient entre les parties 7, 8 et est susceptible de solidariser en rotation les deux parties 7 et 8 et transmet à la partie de sortie 8 un couple exercé par l'arbre 2', si ce couple s'exerce dans un premier sens de rotation R, qui est le sens de rotation normal du moteur électrique 1. Si le couple s'exerce dans le sens opposé, ce couple à partir d'un seuil n'est pas transmis ; la partie 8 étant alors libre en rotation par rapport à la partie d'entrée 7 solidaire en torsion de l'arbre 2' en sorte que lorsque le moteur thermique démarre et que la vitesse de la roue de lancement augmente, le pignon 5 ne peut entraîner le moteur électrique 1 à une vitesse trop élevée qui pourrait l'endommager.The launcher 3 comprises, on the one hand, an input portion 7, rotatably connected to the shaft 2 'by a complementary helical spline link acting locally between the inner periphery of the input portion 7 and the outer periphery of the shaft 2 ', and, on the other hand, an outlet portion 8 comprising the pinion 5. A coupling device 9 disengageable, here freewheel roller optionally conical clutch, intervenes between the parts 7, 8 and is capable of securing in rotation the two parts 7 and 8 and transmits to the output portion 8 a torque exerted by the shaft 2 ', if this torque is exerted in a first direction of rotation R, which is the direction normal rotation of the electric motor 1. If the torque is exercised in the opposite direction, this pair from a threshold is not transmitted; the part 8 then being free in rotation with respect to the input portion 7 integral torsion of the shaft 2 'so that when the engine starts and the speed of the throwing wheel increases, the pinion 5 can not driving the electric motor 1 at too high a speed which could damage it.

L'invention concerne essentiellement le lanceur 3 traversé par l'arbre de sortie 2', qui sera décrite ci-dessous en se référant aux figures 2 à 8.The invention essentially relates to the launcher 3 traversed by the output shaft 2 ', which will be described below with reference to the Figures 2 to 8 .

La partie d'entrée 7 comprend, axialement alignés sur l'axe X-X, un segment d'arbre d'entrée 10 tubulaire, constituant un manchon tubulaire d'entrée d'orientation axiale, portant un guide de fourchette 11 en forme de gouttière ou gorge annulaire, dans laquelle est engagée l'extrémité 4' de commande de la fourchette 4, et une partie amont d'accouplement 12. Le manchon tubulaire 10 présente localement intérieurement à sa périphérie interne les cannelures hélicoïdales précitées pour venir en prise de manière complémentaire avec les cannelures hélicoïdales que présente localement à sa périphérie externe l'arbre de sortie 2' en sorte que le manchon 10 est lié en rotation à l'arbre de sortie 2' mais peut se déplacer axialement par rapport à celui-ci. Deux rondelles sont rapportées à fixation sur le manchon 10 pour former le guide de fourchette 11. En variante une seule rondelle est rapportée sur le manchon 10 et l'autre flanc de la gorge formant le guide de fourchette est constitué par la face arrière d'un entraîneur 17 ou d'un couvercle 19 décrits ci-après.
La partie de sortie 8 est essentiellement constituée d'un segment d'arbre de sortie 13 tubulaire, constituant un manchon tubulaire de sortie d'orientation axiale, portant le pignon 5 à son extrémité avant 14 et une partie aval d'accouplement 15 à son extrémité arrière 16.The inlet portion 7 comprises, axially aligned on the axis XX, a tubular input shaft segment, constituting an axially oriented inlet tubular sleeve, carrying a gutter-shaped fork guide 11 or annular groove, in which is engaged the control end 4 'of the fork 4, and an upstream coupling portion 12. The tubular sleeve 10 locally present internally at its inner periphery the aforementioned helical grooves to engage in a complementary manner with the helical grooves locally present at its outer periphery the output shaft 2 'so that the sleeve 10 is rotatably connected to the output shaft 2' but can move axially relative thereto. Two washers are attached to attach to the sleeve 10 to form the fork guide 11. Alternatively a single washer is attached to the sleeve 10 and the other side of the groove forming the fork guide is constituted by the rear face of a driver 17 or cover 19 described below.
The outlet portion 8 essentially consists of a tubular output shaft segment 13, constituting an axially oriented output tubular sleeve, carrying the pinion 5 at its front end 14 and a coupling downstream portion 15 at its rear end 16.

Le dispositif d'accouplement 9 débrayable est comme sur la figure 1 de type à galets. Les galets portent la référence 22. La partie amont d'accouplement 12 comprend suivant une caractéristique de l'invention, un entraîneur 17, d'orientation transversale, solidaire du manchon d'entrée 10, une couronne 18, d'orientation axiale, mobile par rapport à l'entraîneur 17, un couvercle 19 d'assemblage de forme creuse liant l'un à l'autre l'entraîneur 17 et la couronne 18 en translation axiale.The coupling device 9 disengageable is as on the figure 1 of pebble type. The rollers bear the reference 22. The upstream coupling part 12 comprises according to a feature of the invention, a driver 17, of transverse orientation, integral with the inlet sleeve 10, a ring 18, axially oriented, movable relative to the driver 17, a hollow-shaped assembly cover 19 linking the driver 17 and the ring gear 18 in axial translation to one another.

Suivant une caractéristique de l'invention un moyen d'amortissement 20 est placé axialement entre l'entraîneur 17 et la couronne 18 et assure la liaison en rotation entre eux. Ainsi le moyen d'amortissement 20 intervient axialement et circonférentiellement entre la couronne 18 et l'entraîneur 17 lié rigidement au manchon d'entrée 10. Ce moyen amortisseur est circonférentiellement élastique en sorte que la couronne 18 et l'entraîneur 17 appartiennent à un amortisseur de torsion à action circonférentielle.According to a feature of the invention a damping means 20 is placed axially between the driver 17 and the ring 18 and ensures the connection in rotation between them. Thus the damping means 20 intervenes axially and circumferentially between the ring 18 and the driver 17 rigidly connected to the inlet sleeve 10. This damping means is circumferentially elastic so that the ring 18 and the driver 17 belong to a damper of torsion with circumferential action.

Comme à la figure 1 la matière de l'extrémité arrière du couvercle 19 est rabattue radialement au contact de la face arrière de l'entraîneur 17 pour calage axial de l'ensemble entraîneur 17- moyen d'amortissement 20- couronne 18 entre la paroi avant d'orientation transversale, traversée par l'arbre 2', du couvercle 19 et la matière rabattue de l'extrémité arrière du couvercle 19 comportant un rebord annulaire d'orientation axiale à l'intérieur duquel se loge ledit ensemble.As in figure 1 the material of the rear end of the cover 19 is folded radially in contact with the rear face of the driver 17 for axial setting of the driver assembly 17- 20-ring damping means 18 between the front wall of transverse orientation , traversed by the shaft 2 ', the cover 19 and the folded material of the rear end of the cover 19 having an annular flange of axial orientation within which is housed said assembly.

La partie aval d'accouplement 15 est constituée par l'extrémité arrière 16 de l'arbre de sortie 13, qui présente une surface extérieure cylindrique définissant une piste 21 de roulement pour les galets 22 qui sont interposés entre cette piste 21 et la surface interne de la couronne 18 comme il sera exposé plus bas. L'extrémité arrière 16 est d'un diamètre légèrement supérieur au reste de l'arbre 13. La partie aval d'accouplement 15 est engagée de manière coaxiale dans la couronne mobile 18.The downstream coupling portion 15 is formed by the rear end 16 of the output shaft 13, which has a cylindrical outer surface defining a track 21 rolling for the rollers 22 which are interposed between the track 21 and the inner surface of the ring 18 as it will be exposed below. The rear end 16 is of a diameter slightly greater than the rest of the shaft 13. The downstream coupling part 15 is engaged coaxially in the mobile ring 18.

La transmission sélective du couple entre la partie d'entrée 7 et la partie de sortie 8 est assurée par les galets 22 maintenus par des ressorts 23 disposés dans des logements profilés 24 pratiqués dans la couronne 18.The selective transmission of the torque between the inlet part 7 and the outlet part 8 is ensured by the rollers 22 held by springs 23 arranged in profiled housings 24 made in the ring gear 18.

L'entraîneur 17 comprend une base 25 ayant sensiblement la forme d'un disque coaxial à l'axe X-X et présentant une face avant 26 orientée vers le pignon 5. Des reliefs menants 27 solidaires de la base 25, s'étendant à la fois suivant une direction radiale et suivant une direction axiale, font saillies sur la face avant 26 de la base 25. L'entraîneur 17 appartient à un amortisseur de torsion comprenant le moyen 20.The driver 17 comprises a base 25 having substantially the shape of a disc coaxial with the axis XX and having a front face 26 facing the pinion 5. Driving reliefs 27 integral with the base 25, extending at a time in a radial direction and in an axial direction, protrude from the front face 26 of the base 25. The driver 17 belongs to a torsion damper comprising the means 20.

Dans le mode de réalisation représenté sur les figures 2,. 3 et 4, la couronne 18 a une double fonction car elle appartient au dispositif d'accouplement 9 et coopère avec le moyen d'amortissement en appartenant à un amortisseur de torsion à action circonférentielle. Pour ce faire la couronne 18 présente sensiblement la forme d'un cylindre coaxial à l'axe X-X, ayant une paroi d'une certaine épaisseur radiale et présentant une face frontale arrière 28 orientée vers la base 25. Des reliefs menés 29 s'étendant à la fois suivant une direction radiale et suivant une direction axiale font saillies sur la face 28 de la couronne 18. Le diamètre extérieur de la couronne 18 est sensiblement le même que celui de la base 25 de l'entraîneur 17.In the embodiment shown on the Figures 2, 3 and 4 , the ring 18 has a dual function because it belongs to the coupling device 9 and cooperates with the damping means belonging to a circumferential action torsion damper. To do this, the ring 18 has substantially the shape of a cylinder coaxial with the axis XX, having a wall of a certain radial thickness and having a rear end face 28 oriented towards the base 25. Conducted reliefs 29 extending both in a radial direction and in an axial direction protrude from the face 28 of the ring 18. The outer diameter of the ring 18 is substantially the same as that of the base 25 of the driver 17.

Les reliefs menants 27 et menés 29 sont distribués, de préférence, de façon angulairement équidistante sur leur surface de support en un cercle centré sur l'axe de ce dernier. Les reliefs menés 29 sont en nombre égal au nombre de reliefs menants 27.The leading reliefs 27 and led 29 are distributed, preferably, angularly equidistantly on their support surface in a circle centered on the axis of the latter. The reliefs 29 are equal in number to the number of leading reliefs 27.

Le moyen d'amortissement 20 comprend une pluralité d'éléments amortisseurs 30, typiquement des blocs, qui sont chacun disposés, dans un plan perpendiculaire à l'axe X-X, entre un relief menant 27 et un relief mené 29, comme illustré sur la figure 3.The damping means 20 comprises a plurality of damping elements 30, typically blocks, which are each arranged, in a plane perpendicular to the axis XX, between a driving relief 27 and a raised relief 29, as illustrated in FIG. figure 3 .

Dans l'exemple représenté, les éléments amortisseurs 30 sont groupés par paires qui forment chacune un ensemble dans lequel les deux éléments 30 sont reliés par un élément de liaison 31 de telle façon qu'une encoche 32 soit formée entre eux.In the example shown, the damping elements 30 are grouped in pairs which each form an assembly in which the two elements 30 are connected by a connecting element 31 so that a notch 32 is formed between them.

A l'état assemblé du lanceur, les reliefs menants 27 s'engagent chacun dans une encoche 32, de telle sorte que ces reliefs menants 27 soient coiffés par les éléments de liaison 31 qui les séparent de la couronne 18. Les reliefs menés 29 s'intercalent entre chaque paire d'éléments amortisseurs 30.In the assembled state of the launcher, the driving reliefs 27 each engage in a notch 32, so that these driving reliefs 27 are capped by the connecting elements 31 which separate them from the crown 18. The raised features 29 s interposed between each pair of damping elements 30.

La section de chaque relief menant 27 ou mené 29 dans un plan perpendiculaire à l'axe longitudinal X-X adopte de préférence la forme d'une patte radiale présentant deux faces latérales rectilignes convergeant vers l'axe longitudinal X-X. Les pattes s'étendent à partir de la surface périphérique de la base 25 et de la couronne 18.The section of each driving relief 27 or led 29 in a plane perpendicular to the longitudinal axis X-X preferably adopts the shape of a radial tab having two rectilinear lateral faces converging towards the longitudinal axis X-X. The tabs extend from the peripheral surface of the base 25 and the crown 18.

Les éléments amortisseurs 30 sont élastiques et réalisés en élastomère, par exemple en caoutchouc ou dans un matériau élastique synthétique approprié. En variante les éléments amortisseurs sont métalliques et ont par exemple une forme en accordéon.The damping elements 30 are elastic and made of elastomer, for example rubber or a suitable synthetic elastic material. Alternatively the damping elements are metallic and have for example an accordion shape.

Comme illustré sur la figure 5, les reliefs menés 29 sont séparés de la base 25 de l'entraîneur 17 par un jeu J.As illustrated on the figure 5 , the raised reliefs 29 are separated from the base 25 of the coach 17 by a set J.

En se référant à la figure 3, on constate que le couvercle 19 enveloppe l'ensemble constitué par l'entraîneur 17, le moyen d'amortissement 20 et la couronne 18 radialement et dans les deux directions axiales. Outre les fonctions décrites plus haut, il assure également la liaison en translation axiale entre la couronne 18 et la partie de sortie 8. Le couvercle 19 est constitué d'une paroi cylindrique mince d'axe X-X, les deux faces axiales étant partiellement fermées par des parois minces sensiblement en forme de disques évidés en leurs centres.Referring to the figure 3 it is found that the cover 19 envelops the assembly consisting of the driver 17, the damping means 20 and the ring 18 radially and in both axial directions. In addition to the functions described above, it also ensures the connection in axial translation between the ring 18 and the outlet portion 8. The cover 19 consists of a thin cylindrical wall of axis XX, the two axial faces being partially closed by thin walls substantially shaped discs recessed in their centers.

Comme le montre la figure 6, la couronne 18 et la piste 21 délimitent entre elles des logements tangentiels 24 présentant une largeur radiale évoluant, dans le sens de rotation R, entre une largeur minimale et une largeur maximale. Un ressort 23 précontraint en compression et un galet 22 coaxial à la couronne 18 sont disposés dans chaque logement 24. La couronne 18 porte des nervures internes radiales 34 séparant deux logements 24 adjacents, le ressort 23 prenant appui d'un côté sur une nervure 34, et le galet 22 étant sollicité par le ressort 23 en direction de la largeur minimale du logement 24.As shown in figure 6 , the ring 18 and the track 21 delimit between them tangential housing 24 having a radial width moving in the direction of rotation R, between a minimum width and a maximum width. A spring 23 prestressed in compression and a roller 22 coaxial with the ring gear 18 are arranged in each housing 24. The ring gear 18 carries radial internal ribs 34 separating two adjacent housings 24, the spring 23 bearing on one side on a rib 34 , and the roller 22 being biased by the spring 23 towards the minimum width of the housing 24.

Quand le couple s'exerce dans le sens de rotation R, le galet 22 roule sur la piste 21 et sur le fond du logement 24 qui lui fait face, dans la direction opposée à R et vient se caler dans la zone de largeur minimale du logement 24. Le galet 22 empêche alors la piste 21 et la couronne 18 de bouger l'une par rapport à l'autre, et assure donc la transmission du couple.When the torque is exerted in the direction of rotation R, the roller 22 rolls on the track 21 and on the bottom of the housing 24 which faces it, in the opposite direction to R and is wedged in the zone of minimum width of the 24. The roller 22 then prevents the track 21 and the ring 18 to move relative to each other, and thus ensures the transmission of torque.

Quand le couple s'exerce dans le sens de rotation opposé à R, le galet 22 roule sur la piste 21 et sur le fond du logement 24 qui lui fait face, dans la direction de R, donc vers la zone de plus grande largeur du logement 24. Quand le galet 22 atteint un point où la largeur du logement 24 est plus grande que le diamètre du galet 22, il peut alors rouler librement sur la piste 21 car il n'est plus en contact avec le fond du logement 24. La piste 21 et la couronne 18 sont donc libres en rotation l'une part rapport à l'autre, et la transmission du couple n'est plus assurée.When the torque is exerted in the direction of rotation opposite R, the roller 22 rolls on the track 21 and on the bottom of the housing 24 which faces it, in the direction of R, thus towards the zone of greater width of the housing 24. When the roller 22 reaches a point where the width of the housing 24 is greater than the diameter of the roller 22, it can then roll freely on the track 21 because it is no longer in contact with the bottom of the housing 24. The track 21 and the ring 18 are free to rotate relative to each other, and the transmission of the couple is no longer insured.

Il est à noter qu'une rondelle 33 d'axe X-X est interposée entre le moyen d'amortissement 20 et la couronne 18 de façon à séparer le moyen d'amortissement 20 des galets 22 pour éviter des déplacements axiaux des galets 22 provoqués par la déformation du moyen d'amortissement 20. Le bord extérieur de la rondelle 33 est découpé pour s'adapter à la forme des reliefs menés 29.It should be noted that a washer 33 of axis XX is interposed between the damping means 20 and the ring gear 18 so as to separate the damping means 20 from the rollers 22 in order to avoid axial displacements of the rollers 22 caused by the deformation of the damping means 20. The outer edge of the washer 33 is cut to fit the shape of the reliefs carried out 29.

Concernant le fonctionnement du lanceur 3, on comprend que les chocs torsionnels qui se propagent de l'axe moteur 2 vers le pignon 6 ou en sens inverse passent donc respectivement des reliefs menants 27 aux reliefs menés 29 ou des reliefs menés 29 aux reliefs menants 27, et sont amortis dans les deux cas par la déformation des éléments amortisseurs 30 situés entre eux.As regards the operation of the launcher 3, it will be understood that the torsional shocks propagating from the driving axle 2 towards the pinion 6 or in the opposite direction therefore pass respectively from the driving reliefs 27 to the raised reliefs 29 or from the reliefs led 29 to the driving reliefs 27 , and are damped in both cases by the deformation of the damping elements 30 located between them.

En cas de choc axial, les éléments de liaison 31 et les éléments amortisseurs 30 absorbent une partie de l'énergie transmise entre la couronne 18 et l'entraîneur 17 par déformation. Le jeu J est dimensionné de telle façon que la déformation des éléments de liaison 31 et des éléments amortisseurs 30 n'entraînent pas de contacts entre les reliefs menés 29 et la base 25 de l'entraîneur 17. Les éléments de liaison 31 contribuent à amortir le choc axial.In the event of an axial impact, the connecting elements 31 and the damping elements 30 absorb part of the energy transmitted between the ring 18 and the driver 17 by deformation. The clearance J is dimensioned in such a way that the deformation of the connecting elements 31 and of the damping elements 30 does not cause contacts between the led projections 29 and the base 25 of the driver 17. The connecting elements 31 contribute to damping the axial shock.

L'utilisation d'une partie amont d'accouplement 12 constituée d'une couronne 18 solidaire d'un entraîneur 17, lié rigidement au manchon 10, par l'intermédiaire d'un moyen d'amortissement 20, en lieu et place d'une cloche dans l'art ancien, présente l'avantage de permettre une légère déformation de la partie amont d'accouplement 12 sans que l'axe de la couronne 18 ne soit modifié, la déformation étant absorbée par le moyen d'amortissement 20, ce qui évite que les galets 22 se mettent en porte-à-faux par rapport à la piste 21 et au fond des logements 24 et limite donc les risques d'écaillage.The use of an upstream coupling portion 12 consisting of a ring gear 18 secured to a driver 17, rigidly connected to the sleeve 10, via a damping means 20, in place of a bell in the old art, has the advantage of allowing a slight deformation of the upstream coupling portion 12 without the axis of the ring 18 being modified, the deformation being absorbed by the damping means 20, This prevents the rollers 22 cantilever with respect to the track 21 and the bottom of the housing 24 and therefore limits the risk of chipping.

Les figures 7 et 8 illustrent un second mode de réalisation de l'invention dans lequel les reliefs menés 29 sont constitués par la prolongation dans la direction axiale des nervures 34. Les reliefs menés 29 ne s'étendent donc pas radialement jusqu'à la périphérie de la couronne 18. Dans ce mode de réalisation, la couronne 18 s'étend radialement jusqu'à la face avant de la base 25.The Figures 7 and 8 illustrate a second embodiment of the invention in which the raised reliefs 29 are constituted by the extension in the axial direction of the ribs 34. The raised reliefs 29 therefore do not extend radially to the periphery of the crown 18. In this embodiment, the ring 18 extends radially to the front face of the base 25.

La distribution et la forme des reliefs menants 27 sont complémentaires de celles des reliefs menés, les reliefs menants 27 s'emboîtant entre les reliefs menés 29, à l'intérieur de la couronne 18, et les éléments amortisseurs 30 étant eux aussi disposés à l'intérieur de la couronne 18, chacun entre un relief menant 27 et un relief mené 29.The distribution and the shape of the driving reliefs 27 are complementary to those of the led reliefs, the driving reliefs 27 being interlocked between the raised projections 29, inside the ring gear 18, and the damping elements 30 being also arranged inside the crown 18, each between a leading relief 27 and a raised relief 29.

Ce second mode de réalisation permet une fabrication plus simple et moins coûteuse des couronnes 18.This second embodiment allows a simpler and less expensive manufacture of the rings 18.

De multiples modifications peuvent être apportées aux modes de réalisation décrits et représentés. Ainsi les positions des reliefs menants 27 et menés 29 peuvent être indifféremment inversées, les reliefs menés 29 étant engagés dans les encoches 32 et les reliefs menants 27 séparant les paires d'éléments amortisseurs 30. Les reliefs pourraient avoir toute autre forme appropriée et les éléments amortisseurs pourraient être réunis en une couronne, afin de faciliter l'assemblage du lanceur.Multiple modifications can be made to the embodiments described and shown. Thus the positions of the leading reliefs 27 and led 29 can be indifferently reversed, the raised reliefs 29 being engaged in the notches 32 and the reliefs The reliefs could have any other suitable shape and the damping elements could be combined in a crown, in order to facilitate the assembly of the launcher.

En variante le dispositif d'accouplement débrayable est du type à embrayage conique la couronne 18 portant à sa périphérie interne ou externe une suface de frottement tronconique propre à coopérer de manière complémentaire avec une surface de frottement tronconique portée par l'extrémité arrière 16 de la partie aval 15. Pour plus de précisions on se reportera par exemple aux documents FR A 2 772 433 et PCT/FR 02/02160 .In a variant, the disengageable coupling device is of the conical clutch type, the ring gear 18 bearing at its inner or outer periphery a frustoconical friction surface capable of cooperating in a complementary manner with a frustoconical friction surface carried by the rear end 16 of the downstream part 15. For more details, see for example the documents FR A 2,772,433 and PCT / FR 02/02160 .

Dans tous les cas la partie aval d'accouplement s'étend coaxialement par rapport à la couronne Cette partie aval pénètre dans la couronne ou en variante entoure la couronne lorsque le dispositif d'accouplement comporte un embrayage conique avec une surface de frottement du type de celle des figures 3 et 8 du document PCT/FR 02/02160 . Dans les cas des figures 5 et 6 de ce document la partie aval pénètre dans la couronne reliée à l'entraîneur par le moyen amortisseur.In all cases the downstream coupling part extends coaxially with respect to the crown. This downstream part enters the ring gear or, alternatively, surrounds the ring gear when the coupling device comprises a conical clutch with a friction surface of the type of ring. that of figures 3 and 8 of document PCT / FR 02/02160 . In the case of Figures 5 and 6 of this document the downstream part enters the crown connected to the trainer by the damping means.

Claims (11)

  1. Starter system for a heat engine, in particular for a motor vehicle, provided with a toothed starter wheel, of the type comprising an electric motor (1), a starter (3) which carries a pinion (5) for rotatably driving the toothed wheel of the heat engine and which can be moved on an output shaft (2') which is fixedly joined in terms of rotation to the shaft (2) of the electric motor (1) between a passive position in which the pinion (5) is disengaged from the toothed wheel and the electric motor (1) is not excited and an active position in which the pinion (5) engages with the toothed wheel and in which the electric motor is excited, in which the starter (3) comprises an input portion (7) which is coaxial with, and connected in terms of rotation to, the output shaft (2') having a longitudinal axis (X-X), an output portion (8) which is connected in terms of rotation to the pinion (5), and a coupling device (9) which can be disengaged in terms of rotation from the two portions comprising an upstream coupling portion (12) which belongs to the input portion (7), a downstream coupling portion (15) which belongs to the output portion (8) and a circumferentially resilient damping means (20) for mechanical shocks, at least torsional shocks, and in which the input portion (7) comprises a tubular input sleeve (10) which is rotatably connected to the output shaft (2') by means of a connection having complementary helical splines which act locally between the internal periphery of the sleeve (10) and the external periphery of the output shaft (2'), a driver (17) which is rigidly connected to the tubular input sleeve (10) and a crown (18) which is coaxial with the output shaft (2'), the downstream coupling portion (15) extending coaxially relative to the crown (18), characterized in that the driver (17) is orientated transversely relative to the output shaft (2'), in that the crown (18) can be moved relative to the driver (17), in that it comprises an assembly cover (19) of hollow form which connects the driver (17) and the crown (18) to each other in terms of axial translation, in that the damping means (20) is placed axially between the crown (18) and the driver (17) and in that the crown (18) and the driver (17) are fixedly joined in terms of rotation by the damping means (20) which act axially and circumferentially between the crown (18) and the driver (17).
  2. Starter system according to Claim 1, characterized in that the cover (19) surrounds, radially and in both axial directions, the assembly constituted by the driver (17), the damping means (20) and the crown (18).
  3. Starter system according to Claim 1 or Claim 2, characterized in that the output portion (8) is constituted by a tubular output shaft segment (13) which carries the pinion (5) at the front end (14) thereof and the downstream coupling portion (15) at the rear end (16) thereof, in that the coupling device (9) is of the type having rollers (22), each of which is engaged between a track portion of the inner surface of the crown (18) of the upstream coupling portion (12) and a track portion (21) of the downstream coupling portion (15), and in that the downstream coupling portion (15), having a cylindrical form, extends coaxially in said crown (18).
  4. Starter system according to any one of the preceding claims, characterized in that the driver (17) comprises a base (25) which substantially has the shape of a disc which is coaxial with the output shaft (2') and driving reliefs (27) on the face (26) of the base (25) orientated towards the pinion (5) extending both in a radial direction and in an axial direction, in that the crown (18) has driven reliefs (29) which are orientated towards the driving reliefs (27) extending both in a radial direction and in an axial direction, in that the damping means (20) comprises a plurality of damping elements (30), each damping element (30) being arranged between a driving relief (27) and a driven relief (29), and in that the outer diameter of the crown (18) is generally the same as that of the base (25) of the driver (17).
  5. Starter system according to Claim 4, characterized in that the driving reliefs (27) and driven reliefs (29) are distributed in an angularly equidistant manner on their support surface in a circle which is centred on the axis of the latter, the number of driven reliefs (29) being equal to the number of driven reliefs (27).
  6. Starter system according to Claim 5, characterized in that the cross-section of each driving relief (27) or driven relief (29) in a plane perpendicular relative to the longitudinal axis (X-X) is in the form of a radial lug which has two rectilinear lateral faces which converge towards the longitudinal axis (X-X).
  7. Starter system according to any one of Claims 4 to 6, characterized in that the driven reliefs (29) are separated from the base of the driver (17) by a clearance (J).
  8. Starter system according to any one of Claims 4 to 7, characterized in that the damping elements (30) are grouped in pairs which each form a group in which the two damping elements (30) are connected by means of a connection element (31) in such a manner that a notch (32) is formed between them, a driving relief (27) or a driven relief (29) being engaged in the notch (32).
  9. Electrical starter system according to Claim 7 and Claim 8, characterized in that each connection element (31) contributes to damping shocks in the axial direction and in that the clearance (J) is sized in such a manner that the deformation of the connection elements (31) and of the damping elements (30) does not bring about contact between the driven reliefs (29) and the base (25) of the driver (17).
  10. Starter system according to any one of Claims 4 to 9, characterized in that the crown (18) and the downstream coupling portion (15) together delimit tangential housings (24) which have a radial width which develops, in a first rotation direction, between a minimum width and a maximum width, and in that a spring (23) which is preloaded in terms of compression and a roller (22) which is urged by the spring (23) in the direction of the minimum width of the housing (24) are arranged in each housing (24), the crown (18) carrying substantially radial internal ribs (34) which separate two adjacent housings (24) and on each of which one of the springs (23) is supported, and in that the driven reliefs (29) are the axial continuation of these internal webs (34).
  11. Starter system according to any one of Claims 3 to 10, characterized in that a washer (33) is interposed between the damping means (20) and the rollers (22) in order to prevent axial displacements of the rollers (22) brought about by the deformation of the damping means (20).
EP02291951.8A 2001-08-17 2002-08-02 Starter drive with clutch in particular for an internal combustion engine in a vehicle Expired - Lifetime EP1298318B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0110911 2001-08-17
FR0110911A FR2830574B1 (en) 2001-08-17 2001-08-17 STARTER, PARTICULARLY FOR AN ENGINE OF A MOTOR VEHICLE OF THE COUPLING LAUNCHER TYPE

Publications (3)

Publication Number Publication Date
EP1298318A2 EP1298318A2 (en) 2003-04-02
EP1298318A3 EP1298318A3 (en) 2006-05-17
EP1298318B1 true EP1298318B1 (en) 2013-04-24

Family

ID=8866599

Family Applications (2)

Application Number Title Priority Date Filing Date
EP02291987A Withdrawn EP1298319A1 (en) 2001-08-17 2002-07-25 Starter drive with clutch in particular for an internal combustion engine in a vehicle
EP02291951.8A Expired - Lifetime EP1298318B1 (en) 2001-08-17 2002-08-02 Starter drive with clutch in particular for an internal combustion engine in a vehicle

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP02291987A Withdrawn EP1298319A1 (en) 2001-08-17 2002-07-25 Starter drive with clutch in particular for an internal combustion engine in a vehicle

Country Status (4)

Country Link
EP (2) EP1298319A1 (en)
KR (1) KR100859849B1 (en)
BR (1) BR0203269B1 (en)
FR (1) FR2830574B1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2830574B1 (en) * 2001-08-17 2004-05-28 Valeo Equip Electr Moteur STARTER, PARTICULARLY FOR AN ENGINE OF A MOTOR VEHICLE OF THE COUPLING LAUNCHER TYPE
US7360464B2 (en) * 2003-12-15 2008-04-22 Automotive Components Holdings, Llc Variable rate impact and oscillation absorber in starter motors
FR2902840B1 (en) * 2006-06-27 2013-03-29 Valeo Equip Electr Moteur STARTING DEVICE FOR THERMAL ENGINE
US7373908B2 (en) * 2006-08-29 2008-05-20 Gm Global Technology Operations, Inc. Reduced noise engine start-stop system using traditional crank device
DE102009026593A1 (en) * 2009-05-29 2010-12-02 Robert Bosch Gmbh Method for the mechanical synchronization of two rotating, off-axis spur gears

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR516919A (en) * 1918-06-29 1921-04-28 Max Wild Starter device particularly for automobile engines
FR839572A (en) * 1938-06-21 1939-04-06 Further training provided in the establishment of starters for internal combustion engines
US5046373A (en) * 1989-08-07 1991-09-10 Briggs & Stratton Corp. Starter motor construction
JPH04232379A (en) * 1990-12-28 1992-08-20 Mitsubishi Electric Corp Starter device
FR2754856B1 (en) * 1996-10-23 1998-11-27 Valeo Equip Electr Moteur STARTER LAUNCHER OF A FREE-WHEEL MOTOR VEHICLE WITH A TORSION DAMPER AND STARTER EQUIPPED WITH SUCH A LAUNCHER
FR2759119B1 (en) * 1997-02-06 1999-03-05 Valeo Equip Electr Moteur MOTOR VEHICLE STARTER COMPRISING AN IMPROVED LAUNCHER
FR2830574B1 (en) * 2001-08-17 2004-05-28 Valeo Equip Electr Moteur STARTER, PARTICULARLY FOR AN ENGINE OF A MOTOR VEHICLE OF THE COUPLING LAUNCHER TYPE

Also Published As

Publication number Publication date
EP1298319A1 (en) 2003-04-02
EP1298318A3 (en) 2006-05-17
KR100859849B1 (en) 2008-09-24
BR0203269B1 (en) 2010-11-03
FR2830574B1 (en) 2004-05-28
FR2830574A1 (en) 2003-04-11
BR0203269A (en) 2003-05-27
KR20030016170A (en) 2003-02-26
EP1298318A2 (en) 2003-04-02

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