EP1461528B1 - Motor vehicle electric starter equipped comprising a starting motor with improved splines - Google Patents

Motor vehicle electric starter equipped comprising a starting motor with improved splines Download PDF

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Publication number
EP1461528B1
EP1461528B1 EP02803834A EP02803834A EP1461528B1 EP 1461528 B1 EP1461528 B1 EP 1461528B1 EP 02803834 A EP02803834 A EP 02803834A EP 02803834 A EP02803834 A EP 02803834A EP 1461528 B1 EP1461528 B1 EP 1461528B1
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EP
European Patent Office
Prior art keywords
hub
pinion
shaft
tooth
launcher
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
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EP02803834A
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German (de)
French (fr)
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EP1461528A1 (en
Inventor
Gérard Vilou
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Valeo Equipements Electriques Moteur SAS
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Valeo Equipements Electriques Moteur SAS
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Publication of EP1461528A1 publication Critical patent/EP1461528A1/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

Definitions

  • a motor vehicle starter comprises in a conventional manner and as described for example in the document FR-A-2,673,247 , a motor rotary electric motor 10 having a rotor coupled to an output shaft 12 equipped with a movable pinion 14 intended to cooperate with a toothed ring gear 16 for starting the combustion engine (not shown) of the motor vehicle.
  • the pinion 14 is slidably mounted on the output shaft 12 between a rest position in which it is disengaged from the ring gear 16, and an active working position in which it meshes with said ring 16, which is connected in rotation crankshaft of the vehicle combustion engine.
  • the crown 16 belongs to a flywheel rigidly or resiliently connected to the crankshaft of the engine of the vehicle.
  • the electric motor 10 comprises an output shaft which is coincident with the output shaft 12 or which is connected thereto via an epicyclic gear reducer as visible in this embodiment. figure 1 .
  • the output shaft 12 and the output shaft of the electric motor 10 have the same axial axis of symmetry.
  • This electric motor comprises, in known manner, an inductor stator surrounding an induced rotor integral with the output shaft of the motor 10.
  • the rotor comprises a bundle of grooved plates for mounting windings connected to a collector that is not referenced to the figure 1 .
  • the electric motor 10 of the starter is associated with a contactor 18 with an electromagnet 17 disposed here above the electric motor 10, and having a dual function of supplying the electric motor 10 with current, and moving the movable pinion 14 between the two positions of rest and work.
  • the excitation of the electromagnet 17 of the contactor 18 is controlled by the actuation of the ignition key, which establishes the electrical circuit to the battery, following the closure of the main contact 19 of the power switch 18.
  • This electromagnetic contactor 18 comprises a fixed core 46, an actuating coil, schematized by crosses at the figure 1 , a mobile core 20 able to act on a contact mobile 19, said main contact, to move it in contact with terminals (not referenced to the figure 1 ) and power the electric motor.
  • the cores 46 and 20 as well as the actuating coil belong to the electromagnet 17.
  • the contact 19 is carried by a rod (not referenced) slidably mounted in the fixed core 46, while the terminals are carried by a cover, one of the terminals being connected to the positive terminal of the battery and the other to the electric motor.
  • the control mechanism is associated with the mobile core and here comprises a control lever. More specifically, the movable core 20 of the contactor 18 is mechanically connected by a control lever 22 to a launcher 24 comprising a hub 30 the pinion 14 and a transmission device here freewheel 26.
  • the control lever 22 fork-shaped is mounted pivotably on an axle 28 carried by a rod elastically connected to the movable core 20 via a spring 48, and the free wheel 26 is interposed axially between the pinion 14 and the drive hub 30 actuated by the lever of 22.
  • the output shaft 12 and that of the electric motor 12 are rotatably mounted in a housing 32 via a bearing 34 and a bearing 36.
  • the housing 32 has a front portion bearing the bearing 36 AND intended to be fixed on a fixed part of the vehicle and a rear part in the form of breech reported on the front part with tie rods, one of which is visible at the figure 1 .
  • the front portion of the housing 32 carries the bearing 36 and has a clearance for the passage of the ring 16, while the rear portion of the housing 32 carries the bearing 34 and the stator of the electric motor 10 and serves as a housing for the rotor of this electric motor 10.
  • the pinion 14 of the launcher 24 is slidably guided on a smooth cylindrical section of the output shaft 12 via a bearing 38.
  • the drive hub 30 is actuated in rotation by means of two series of helical splines 40, 42 of complementary shapes, respectively arranged on the outer periphery of the output shaft 12, and in the inner periphery of a bushing 31 cylindrical internal drive hub 30.
  • the pinion 14 is thus secured to the drive hub 30 by the disengageable freewheel transmission device 26, which drives the pinion 14 in a direction of rotation corresponding to that of the output shaft 12 during the normal phase. starting, and disengage the mechanical connection rotating drive when the rotational speed of the pinion 14 is greater than that of the drive hub 30.
  • the presence of the wheel transmission device free 26 prevents the pinion 14 in engagement with the ring gear 16, drives the rotor 44 of the electric motor 10 at an excessive speed likely to deteriorate the latter. Such a situation may occur when the driver does not turn off the power of the switch 18 immediately after starting.
  • Freewheel 26 illustrated in FIGS. figures 1 and 2 is of the roller type, but it is clear that any other unidirectional disengageable transmission device can be used, including a conical clutch friction, as described in the documents FR-A-2,772,433 and FR-A-2,826,696 of the plaintiff.
  • the movable core 20 when the drive coil of the electromagnet 17 is activated the movable core 20 is attracted to the fixed core 46 of the switch 18 which causes the translational movement of the launcher 24 to the working position.
  • the spring 48 arranged inside the movable core 20, compresses allowing the further movement of attraction of the core mobile 20, which closes the main contact 19 at the end of the race for the excitation of the electric motor 10.
  • the rotation of the electric motor 10 combined with the thrust of the spring 48, allows the penetration of the pinion 14 as soon as a tooth of the latter passes opposite an entrance of the crown 16.
  • the leading edge the tooth of the pinion 14 comes into contact with the driven flank of the tooth of the crown 16, but with incomplete penetration of the pinion 14 which is of the order of 0.5 to 2 mm.
  • the torque transmitted to the pinion 14 by the electric motor 10 creates the contact force on the tooth of the ring 16, which generates an antagonistic friction force to the further penetration of the pinion 14 into the ring 16, since the The reaction of the spring 48 is insufficient to overcome the frictional force.
  • the transmission of the entire starting torque in this position of incomplete penetration of the pinion 14, would cause high contact pressures may quickly deteriorate the teeth.
  • the helical shape of the splines 40, 42 of the drive hub 30 has made it possible to improve the insertion phase of the pinion 14, since the helix creates a force whose axial component, conjugated with the thrust of the spring 48, pushes the pinion 14 into the ring 16. This results in a screwing effect of the launcher 24 until the pinion 14 comes into axial abutment against a stop 50 carried by the shaft 12 near the bearing 36. During this race of pinion penetration 14, the contact pressure on the teeth is relatively low.
  • the pinion 14 drives the ring 16 in rotation.
  • the torque then increases rapidly, since it is necessary to overcome the resisting torque of the combustion engine.
  • the contact pressure remains acceptable, however, since the length engaged between pinion gear 14 and crown tooth 16 is maximum.
  • the combustion engine takes its idle speed, and drives the pinion 14 of the launcher 24 at a very high speed.
  • the free wheel 26 or the conical clutch is then urged in the opposite direction, and is released to protect the electric motor 10 from an overspeed.
  • the launcher 24 then tends to unscrew on the splines 40 of the shaft 12, which generates an axial force tending to bring the launcher 24 to a stop 52 located opposite the stop 50 and brought to the figure 1 by the epicyclic gearbox.
  • This axial reaction force is added to the restoring forces of the moving core 20 of the electromagnet 17 after the power supply of the contactor 18 has been cut off.
  • the pinion 14 rapidly escapes from the ring gear 16 with a speed sufficient to avoid wear and damage to the ends of the teeth.
  • the flutes 40, 42 of a conventional launcher have in development, straight flanks having a constant inclination angle with respect to the axis of the shaft 12 (see figure 2 ).
  • the stop 50 generally comprises an elastic ring 54 housed in an annular groove of the output shaft 12, and a concentric ring concentrating ring 56 the ring 54. At the end of the working stroke, the pinion 14 abuts against the front face of the ring 56.
  • the invention aims to overcome these disadvantages, and to achieve a starter facilitating the penetration of the starter gear in the ring, and reducing mechanical stresses during operation.
  • this object is achieved by the fact that the helical grooves of the drive hub have a variable contact angle depending on the axial position of the launcher between the rest position and the working position, said contact angle being determined by the inclination of the tangent at the point of engagement of a hub tooth with one of the flanks of two consecutive tree teeth.
  • the contact angle is advantageously greater on the resting position side than on the working position.
  • Such a launcher thus makes it possible to achieve a dual objective, consisting first of all in facilitating the penetration of the pinion into the ring gear, then its escape at the time of the exit after starting, and secondly in reducing the mechanical reactions exerted by the pinion on the stop stop at the end of engagement in the crown.
  • the contact angle is preferably between 15 ° and 30 ° at the moment of penetration of the pinion and at the moment of its exit from the ring.
  • the contact angle is between 0 ° and 20 ° when the pinion abuts against the stop in the working position, and during the driving of the combustion engine.
  • the present invention is based on helical splines 40, 42 having a variable helix angle as a function of the axial position of the launcher 24 along the output shaft shown at 12 to the figure 1 .
  • the geometric axis of the output shaft 12 of the starter is represented at XX '.
  • Two of the shaft teeth 40a, 40b respectively comprise curved flanks AB, CD delimiting a shaft spline 40, which has a variable inclination relative to the axis XX ', in contrast to the straight flanks with a constant inclination angle used. in the starters of the prior art.
  • the tooth 42a of a groove 42 of the hub 30 is shown schematically by a rounded profile and generally elongated in a direction substantially similar to that of the shaft spline 40.
  • the profile here is generally oval
  • a plurality of teeth 40a, 40b, 42a are distributed at regular intervals around the periphery of the shaft 12 to reduce the contact stresses during operation of the starter.
  • the axial position of the center of the tooth 42a of the hub 30 is represented by X 0 on the x axis parallel to the axis XX 'of the shaft 12.
  • This position X 0 corresponds to the axial rest position of the launcher, in which tooth 42a is in contact with K1 with the leading edge AB.
  • the tangent at K 1 makes an angle a1 with the axis XX '.
  • the electric motor 10 begins to rotate (see arrow R illustrating the rotation of the shaft 12), which maintains the tooth 42a against the leading edge AB at the point K2.
  • the tangent at the point K2 makes an angle ⁇ 2 with the axis XX ', favorable to the penetration of the pinion 14 in the ring 16.
  • the value of the angle a2 is preferably chosen between 15 ° and 30 °.
  • the pinion 14 comes into abutment against the stop 50, and the launcher 24 is at this moment in the axial position X 2 end of stroke.
  • the distance X 0 X 2 represents the total axial travel of the pinion 14 between the rest position and the working position.
  • the tooth 42a of the drive hub 30 is always in contact with the leading edge AB at point K3.
  • the tangent at the point K3 makes an angle a3 with the axis of the shaft 12.
  • the value of the angle a3 is smaller than the angle a2, so as to reduce the contact pressure against the stop 50.
  • the value the angle a3 will preferably be chosen between 0 ° and 20 °.
  • the speed of arrival of the pinion 14 against the stop 50 is thus reduced because of the decrease in the angle of inclination of a2 to a3.
  • the shock and the resulting noise are thus reduced, which reduces the stress and wear of the stop 50.
  • the launcher 24 is in freewheel mode, since the pinion 14 rotates faster than the shaft 12.
  • the frictional forces and the residual freewheel torque bring the tooth 42a of the driver hub 30 into contact with the CD flank of the tooth 40b, which is separated from the flank 40a by the groove 40.
  • the tangent to the point of contact K4 makes an angle a4 with the axis of the shaft 12.
  • the value of the angle a4 is preferably chosen between 0 ° and 20 °, that is to say of the same order of magnitude as that of the angle a3. This results in a reduction of the unscrewing forces on the splines 40, 42, which are at the origin of the movements back and forth against the stop 50 following the compression and decompression phases during the drive of the thermal motor. Such a value a4 also reduces noise and wear.
  • the pinion 14 of the launcher 24 is disengaged from the ring 16 following the interruption of the supply of the contactor 18.
  • the intervention of the return forces of the spring 48 of the movable core 20, and the unscrewing forces of the launcher 24 brings back the latter to the rest position.
  • the tooth 42a of the hub 30 arrives in the axial position X 1 the pinion 14 is out of the ring 16.
  • the tooth 42a is in contact at the point K5 with the sidewall CD of the tooth 40b, where the tangent with the axis XX 'makes an angle a5, which will preferably be chosen between 15 ° and 30 °. This high value of the angle a5 ensures rapid output of the pinion 14 out of the ring 16, which reduces wear by friction of the toothing faces.
  • the flute angle is quite high (of the order of 15 ° to 30 °), while at the stop against the stop 50 at the end of engagement in the ring 16, and during the drive of the heat engine, the spline angle is significantly lower (of the order of 0 ° to 20 °).
  • the inclination variation of the spline angle between the rest position and the working position is gradual and continuous.
  • the clearance j between the tooth 42a and the sidewall AB may be variable depending on the position of the launcher and the selected pitcher and tree profiles. This game is preferably greater than 0.05 mm to ensure a good slip without risk of jamming. Excessive play will be avoided, particularly in the working position to limit backlash shocks during the drive phase of the engine.
  • the tooth 142a of the hub gear 30 has a prismatic shape MNPQRS, obtained by molding, extrusion, or cold stamping.
  • Each side of the shaft teeth 140a, 140b is composed of two segments of inclined lines AA1, A1B; CC1, C1D.
  • the segment AA1 makes an angle a1 with the axis of the shaft 12, preferably between 15 ° and 30 °.
  • the segment A1B makes an angle a3 with the axis of the shaft 12, preferably between 0 ° and 20 °.
  • the segment DC1 makes an angle ⁇ 4 with the axis of the shaft 12, preferably between 0 ° and 20 °.
  • the CC1 segment makes an angle a5 with the axis of the shaft 12, preferably between 15 ° and 30 °.
  • the figure 8 corresponds to the rest position, where the edge NM of the tooth 142a of the drive hub 30 is in contact with the segment AA1 of the shaft tooth 140a.
  • the figure 9 corresponds to the contact of the pinion 14 against the ring 16.
  • the pitch angle of contact between the launcher 24 and shaft 12 remains equal to A1 until the point N reaches the intermediate point A1.
  • the contact angle of inclination is set to a3 until the pinion 14 arrives at the stop 50.
  • the edge PN of the tooth 142a of the hub 30 is in contact with the segment BA1 of the tooth 140a.
  • the figure 11 corresponds to the stop position against the stop 50.
  • the edge RS of the tooth 142a of the drive hub 30 is in contact with the segment DC1 of the shaft tooth 140b.
  • the figure 12 corresponds to the freewheel phase for the return of the launcher to the rest position.
  • the contact angle of inclination changes from a4 to a5 when the point R has exceeded the point C1.
  • the starter can have a different structure.
  • the spring 48 of the figure 1 can intervene between the fork and the transmission device 26.
  • this spring can intervene between the stop 50 and the pinion 14 as visible for example in the document US A 2,960,879 .
  • the pinion 14 can extend outside the housing 32 as described in the document FR A 2,745,855 . In this case the stop is outside the housing.
  • the electromagnetic contactor as a variant is mounted in the axial extension of the electric motor as visible in FIG. figure 6 of the document FR 02 08306 deposited on 03/07/2002.
  • the contactor is coaxial with the pinion and the coil of the electromagnet surrounds the launcher being carried by the front part of the housing.
  • the launcher plays the role of the mobile core so that the presence of the control lever is not mandatory.
  • the mechanism for controlling the translational movement of the launcher therefore does not necessarily include a lever.
  • This mechanism comprises alternatively an actuator as described in the document FR A 2,710,696 .
  • the output shaft is coincident with the output shaft of the electric motor and the contactor is coaxial with the actuator being mounted at the front of the motor 10.
  • the alternating contactor extends at the rear of the electric motor perpendicularly thereto as described in the document FR 02 08356 deposited on 03/07/2002.
  • This mechanism has a rod extending parallel to the electric motor and above it. This rod intervenes between the control fork and a return lever on which the mobile core acts.

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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)
  • Gears, Cams (AREA)
  • Insulation, Fastening Of Motor, Generator Windings (AREA)

Abstract

The invention concerns an electric starter comprising a starting motor (24) equipped with a drive pinion (14) for driving a flywheel ring gear, and a transmission device arranged between the drive pinion (14) and a drive hub (30), which consists of two series of helical splines (40, 42) matching in shape arranged respectively on the output shaft (12) and in an internal cylindrical bushing of the hub (30). In order to facilitate penetration of the drive pinion (14) of the starting motor into the ring gear (16), and to reduce mechanical stresses during operation, the helical splines (40, 42) of the drive hub (30) have a variable angle depending on the axial position of the starting motor (24) between the rest position and the working position, said contact angle being determined by the inclination of the tangent at the point of engagement of a tooth of the hub (42a) with one of the flanks (AB, CD) of two consecutive shaft teeth (40a, 40b). The contact angle is greater on the side of the rest position than on the side of the working position. The invention is applicable to a motor vehicle combustion engine.

Description

Domaine technique de l'inventionTechnical field of the invention

L'invention concerne un démarreur électrique pour un moteur à combustion de véhicule automobile, et comprenant :

  • un moteur électrique alimenté par un contacteur à électro-aimant, et ayant un rotor accouplé à un arbre de sortie,
  • un lanceur équipé d'un pignon pour l'entraînement d'une couronne dentée du volant du moteur à combustion du véhicule automobile, ledit pignon pouvant coulisser axialement sur l'arbre de sortie entre une position de repos dans laquelle il est désengagé de la couronne, et une position active de travail dans laquelle il engrène avec ladite couronne,
  • un dispositif de transmission agencé entre le pignon et un moyeu d'entraînement, lequel est composé de deux séries de cannelures hélicoïdales de formes complémentaires agencées respectivement sur l'arbre de sortie, et dans une douille cylindrique interne du moyeu, ledit dispositif de transmission comprenant des moyens pour entraîner le pignon en rotation pendant la phase normale du démarrage, et pour débrayer la liaison mécanique d'entraînement lorsque la vitesse du pignon est supérieure à celle du moyeu,
  • et un mécanisme de commande associé au contacteur pour le déplacement en translation du lanceur entre les deux positions de repos et de travail définies par des moyens de butée.
The invention relates to an electric starter for a motor vehicle combustion engine, and comprising:
  • an electric motor powered by an electromagnet contactor, and having a rotor coupled to an output shaft,
  • a launcher equipped with a pinion for driving a ring gear of the flywheel of the combustion engine of the motor vehicle, said pinion being able to slide axially on the output shaft between a rest position in which it is disengaged from the crown , and an active working position in which it meshes with said crown,
  • a transmission device arranged between the pinion and a drive hub, which is composed of two series of helical grooves of complementary shapes respectively arranged on the output shaft, and in an inner cylindrical sleeve of the hub, said transmission device comprising means for driving the pinion in rotation during the normal starting phase, and for disengaging the mechanical drive connection when the speed of the pinion is greater than that of the hub,
  • and a control mechanism associated with the switch for translational movement of the launcher between the two rest and working positions defined by stop means.

État de la techniqueState of the art

Selon les figures 1 et 2, un démarreur de véhicule automobile comporte d'une manière classique et tel que décrit par exemple dans le document FR-A-2 673 247 , un moteur électrique 10 rotatif ayant un rotor accouplé à un arbre de sortie 12 équipé d'un pignon 14 mobile destiné à coopérer avec une couronne dentée 16 de démarrage pour assurer le démarrage du moteur à combustion (non représenté) du véhicule automobile. Le pignon 14 est monté à coulissement sur l'arbre de sortie 12 entre une position de repos dans laquelle il est désengagé de la couronne dentée 16, et une position active de travail dans laquelle il engrène avec ladite couronne 16, laquelle est liée en rotation au vilebrequin du moteur à combustion de véhicule.According to figures 1 and 2 , a motor vehicle starter comprises in a conventional manner and as described for example in the document FR-A-2,673,247 , a motor rotary electric motor 10 having a rotor coupled to an output shaft 12 equipped with a movable pinion 14 intended to cooperate with a toothed ring gear 16 for starting the combustion engine (not shown) of the motor vehicle. The pinion 14 is slidably mounted on the output shaft 12 between a rest position in which it is disengaged from the ring gear 16, and an active working position in which it meshes with said ring 16, which is connected in rotation crankshaft of the vehicle combustion engine.

Plus précisément la couronne 16 appartient à un volant lié en rotation de manière rigide ou élastique au vilebrequin du moteur du véhicule. Le moteur électrique 10 comporte un arbre de sortie qui est confondu avec l'arbre de sortie 12 ou qui est relié à celui-ci par l'intermédiaire d'un réducteur à train épicycloïdal comme visible dans cette figure 1. Dans tous les cas l'arbre de sortie 12 et l'arbre de sortie du moteur électrique 10 ont le même axe axial de symétrie. Ce moteur électrique comporte de manière connue un stator inducteur entourant un rotor induit solidaire de l'arbre de sortie du moteur 10. Le rotor comporte un paquet de tôles rainurées pour le montage d'enroulements reliés à un collecteur non référencé à la figure 1.More precisely, the crown 16 belongs to a flywheel rigidly or resiliently connected to the crankshaft of the engine of the vehicle. The electric motor 10 comprises an output shaft which is coincident with the output shaft 12 or which is connected thereto via an epicyclic gear reducer as visible in this embodiment. figure 1 . In all cases the output shaft 12 and the output shaft of the electric motor 10 have the same axial axis of symmetry. This electric motor comprises, in known manner, an inductor stator surrounding an induced rotor integral with the output shaft of the motor 10. The rotor comprises a bundle of grooved plates for mounting windings connected to a collector that is not referenced to the figure 1 .

Le moteur électrique 10 du démarreur est associé à un contacteur 18 à électro-aimant 17 disposé ici au-dessus du moteur électrique 10, et ayant une double fonction d'alimentation du moteur électrique 10 en courant, et de déplacement du pignon 14 mobile entre les deux positions de repos et de travail. L'excitation de l'électro-aimant 17 du contacteur 18 est pilotée par l'actionnement de la clé de contact, qui établit le circuit électrique vers la batterie, suite à la fermeture du contact principal 19 de puissance du contacteur 18.The electric motor 10 of the starter is associated with a contactor 18 with an electromagnet 17 disposed here above the electric motor 10, and having a dual function of supplying the electric motor 10 with current, and moving the movable pinion 14 between the two positions of rest and work. The excitation of the electromagnet 17 of the contactor 18 is controlled by the actuation of the ignition key, which establishes the electrical circuit to the battery, following the closure of the main contact 19 of the power switch 18.

Ce contacteur électromagnétique 18 comporte un noyau fixe 46, une bobine d'actionnement, schématisée par des croix à la figure 1, d'un noyau mobile 20 propre à agir sur un contact mobile 19, dit contact principal, pour déplacer celui-ci au contact de bornes (non référencées à la figure 1) et alimenter le moteur électrique. Les noyaux 46 et 20 ainsi que la bobine d'actionnement appartiennent à l'électroaimant 17.This electromagnetic contactor 18 comprises a fixed core 46, an actuating coil, schematized by crosses at the figure 1 , a mobile core 20 able to act on a contact mobile 19, said main contact, to move it in contact with terminals (not referenced to the figure 1 ) and power the electric motor. The cores 46 and 20 as well as the actuating coil belong to the electromagnet 17.

Plus précisément le contact 19 est porté par une tige (non référencée) montée à coulissement dans le noyau fixe 46, tandis que les bornes sont portées par un capot, l'une des bornes étant reliée à la borne positive de la batterie et l'autre au moteur électrique.More precisely the contact 19 is carried by a rod (not referenced) slidably mounted in the fixed core 46, while the terminals are carried by a cover, one of the terminals being connected to the positive terminal of the battery and the other to the electric motor.

Le mécanisme de commande est associé au noyau mobile et comporte ici un levier de commande. Plus précisément le noyau mobile 20 du contacteur 18 est relié mécaniquement par un levier de commande 22 à un lanceur 24 comprenant un moyeu 30 le pignon 14 et un dispositif de transmission ici à roue libre 26. Le levier de commande 22 en forme de fourchette est monté à pivotement sur un axe 28 porté par une tige reliée élastiquement au noyau mobile 20 par_l'intermédiaire d'un ressort 48, et la roue libre 26 est intercalée axialement entre le pignon 14 et le moyeu d'entraînement 30 actionné par le levier de commande 22. L'arbre de sortie 12 et celui du moteur électrique 12 sont montés à rotation dans un carter 32 par l'intermédiaire d'un palier 34 et d'un roulement 36. Le carter 32 comporte une partie avant portant le roulement 36 ET destinée à être fixée sur une partie fixe du véhicule et une partie arrière en forme de culasse rapportée sur la partie avant à l'aide de tirants dont l'un est visible à la figure 1. La partie avant du carter 32 porte le roulement 36 et présente un dégagement pour le passage de la couronne 16, tandis que la partie arrière du carter 32 porte le palier 34 ainsi que le stator du moteur électrique 10 et sert de logement au rotor de ce moteur électrique 10.The control mechanism is associated with the mobile core and here comprises a control lever. More specifically, the movable core 20 of the contactor 18 is mechanically connected by a control lever 22 to a launcher 24 comprising a hub 30 the pinion 14 and a transmission device here freewheel 26. The control lever 22 fork-shaped is mounted pivotably on an axle 28 carried by a rod elastically connected to the movable core 20 via a spring 48, and the free wheel 26 is interposed axially between the pinion 14 and the drive hub 30 actuated by the lever of 22. The output shaft 12 and that of the electric motor 12 are rotatably mounted in a housing 32 via a bearing 34 and a bearing 36. The housing 32 has a front portion bearing the bearing 36 AND intended to be fixed on a fixed part of the vehicle and a rear part in the form of breech reported on the front part with tie rods, one of which is visible at the figure 1 . The front portion of the housing 32 carries the bearing 36 and has a clearance for the passage of the ring 16, while the rear portion of the housing 32 carries the bearing 34 and the stator of the electric motor 10 and serves as a housing for the rotor of this electric motor 10.

Entre les deux positions de repos et de travail, le pignon 14 du lanceur 24 est guidé en coulissement sur un tronçon cylindrique lisse de l'arbre de sortie 12 par l'intermédiaire d'un coussinet 38.Between the two positions of rest and work, the pinion 14 of the launcher 24 is slidably guided on a smooth cylindrical section of the output shaft 12 via a bearing 38.

Le moyeu d'entraînement 30 est actionné en rotation par l'intermédiaire de deux séries de cannelures 40, 42 hélicoïdales de formes complémentaires, agencées respectivement sur la périphérie externe de l'arbre de sortie 12, et dans la périphérie interne d'une douille 31 cylindrique interne du moyeu d'entraînement 30.The drive hub 30 is actuated in rotation by means of two series of helical splines 40, 42 of complementary shapes, respectively arranged on the outer periphery of the output shaft 12, and in the inner periphery of a bushing 31 cylindrical internal drive hub 30.

Le pignon 14 est ainsi solidarisé au moyeu d'entraînement 30 par le dispositif de transmission débrayable à roue libre 26, lequel permet d'entraîner le pignon 14 dans un sens de rotation correspondant à celui de l'arbre de sortie 12 pendant la phase normale de démarrage, et de débrayer la liaison mécanique d'entraînement en rotation lorsque la vitesse de rotation du pignon 14 est supérieure à celle du moyeu d'entraînement 30. En fin de démarrage du moteur à combustion, la présence du dispositif de transmission à roue libre 26 évite que le pignon 14 en prise avec la couronne 16, entraîne le rotor 44 du moteur électrique 10 à une vitesse excessive susceptible de détériorer ce dernier. Une telle situation peut intervenir lorsque le conducteur ne coupe pas l'alimentation du contacteur 18 immédiatement après le démarrage.The pinion 14 is thus secured to the drive hub 30 by the disengageable freewheel transmission device 26, which drives the pinion 14 in a direction of rotation corresponding to that of the output shaft 12 during the normal phase. starting, and disengage the mechanical connection rotating drive when the rotational speed of the pinion 14 is greater than that of the drive hub 30. At the end of start of the combustion engine, the presence of the wheel transmission device free 26 prevents the pinion 14 in engagement with the ring gear 16, drives the rotor 44 of the electric motor 10 at an excessive speed likely to deteriorate the latter. Such a situation may occur when the driver does not turn off the power of the switch 18 immediately after starting.

La roue libre 26 illustrée aux figures 1 et 2 est du type à galets, mais il est clair que tout autre dispositif de transmission unidirectionnel débrayable peut être utilisé, notamment un embrayage conique à friction, tel que décrit dans les documents FR-A-2 772 433 et FR-A-2 826 696 de la demanderesse.Freewheel 26 illustrated in FIGS. figures 1 and 2 is of the roller type, but it is clear that any other unidirectional disengageable transmission device can be used, including a conical clutch friction, as described in the documents FR-A-2,772,433 and FR-A-2,826,696 of the plaintiff.

Le fonctionnement d'un tel lanceur 24 classique est le suivant :The operation of such a conventional launcher 24 is as follows:

lorsque la bobine d'entraînement de l'électro-aimant 17 est activée le noyau mobile 20 est attiré vers le noyau fixe 46 du contacteur 18 ce qui provoque le déplacement en translation du lanceur 24 vers la position de travail. Lorsque le pignon 14 arrive en dent contre dent sur la couronne 16, le ressort 48, agencé à l'intérieur du noyau mobile 20, se comprime en autorisant la poursuite du mouvement d'attraction du noyau mobile 20, lequel ferme le contact principal 19 en fin de course pour l'excitation du moteur électrique 10.when the drive coil of the electromagnet 17 is activated the movable core 20 is attracted to the fixed core 46 of the switch 18 which causes the translational movement of the launcher 24 to the working position. When the pinion 14 arrives tooth-to-tooth on the ring gear 16, the spring 48, arranged inside the movable core 20, compresses allowing the further movement of attraction of the core mobile 20, which closes the main contact 19 at the end of the race for the excitation of the electric motor 10.

A ce moment, la mise en rotation du moteur électrique 10 combinée avec la poussée du ressort 48, permet la pénétration du pignon 14 dès qu'une dent de ce dernier passe en regard d'un entre en de la couronne 16. Le flanc menant de la dent du pignon 14 entre en contact avec le flanc mené de la dent de la couronne 16, mais avec une pénétration incomplète du pignon 14 qui est de l'ordre de 0,5 à 2 mm. Le couple transmis au pignon 14 par le moteur électrique 10 crée la force de contact sur la dent de la couronne 16, ce qui engendre une force de frottement antagoniste à la poursuite de la pénétration du pignon 14 dans la couronne 16, étant donné que la réaction du ressort 48 est insuffisante pour vaincre la force de frottement. La transmission de l'intégralité du couple de démarrage dans cette position de pénétration incomplète du pignon 14, provoquerait des pressions de contact élevées susceptibles de détériorer rapidement les dentures.At this time, the rotation of the electric motor 10 combined with the thrust of the spring 48, allows the penetration of the pinion 14 as soon as a tooth of the latter passes opposite an entrance of the crown 16. The leading edge the tooth of the pinion 14 comes into contact with the driven flank of the tooth of the crown 16, but with incomplete penetration of the pinion 14 which is of the order of 0.5 to 2 mm. The torque transmitted to the pinion 14 by the electric motor 10 creates the contact force on the tooth of the ring 16, which generates an antagonistic friction force to the further penetration of the pinion 14 into the ring 16, since the The reaction of the spring 48 is insufficient to overcome the frictional force. The transmission of the entire starting torque in this position of incomplete penetration of the pinion 14, would cause high contact pressures may quickly deteriorate the teeth.

La forme hélicoïdale des cannelures 40, 42 du moyeu d'entraînement 30 a permis d'améliorer la phase d'introduction du pignon 14, étant donné que l'hélice crée une force dont la composante axiale, conjuguée avec la poussée du ressort 48, pousse le pignon 14 dans la couronne 16. Il en résulte un effet de vissage du lanceur 24 jusqu'à ce que le pignon 14 arrive en butée axiale contre un arrêt 50 porté par l'arbre 12 près du roulement 36. Durant cette course de pénétration du pignon 14, la pression de contact sur les dents est relativement faible.The helical shape of the splines 40, 42 of the drive hub 30 has made it possible to improve the insertion phase of the pinion 14, since the helix creates a force whose axial component, conjugated with the thrust of the spring 48, pushes the pinion 14 into the ring 16. This results in a screwing effect of the launcher 24 until the pinion 14 comes into axial abutment against a stop 50 carried by the shaft 12 near the bearing 36. During this race of pinion penetration 14, the contact pressure on the teeth is relatively low.

En fin de course de pénétration du lanceur 24 correspondant à la position de travail, le pignon 14 entraîne la couronne 16 en rotation. Le couple augmente alors rapidement, étant donné qu'il faut vaincre le couple résistant du moteur à combustion. La pression de contact reste néanmoins acceptable étant donné que la longueur en prise entre dent de pignon 14 et dent de couronne 16 est maximale.At the end of the penetration stroke of the launcher 24 corresponding to the working position, the pinion 14 drives the ring 16 in rotation. The torque then increases rapidly, since it is necessary to overcome the resisting torque of the combustion engine. The contact pressure remains acceptable, however, since the length engaged between pinion gear 14 and crown tooth 16 is maximum.

En fin de démarrage, le moteur à combustion prend sa vitesse de ralenti, et entraîne le pignon 14 du lanceur 24 à une vitesse très élevée. La roue libre 26 ou l'embrayage conique est alors sollicité en sens inverse, et se débloque pour protéger le moteur électrique 10 d'une survitesse. Le lanceur 24 a alors tendance à se dévisser sur les cannelures 40 de l'arbre 12, ce qui engendre une force axiale tendant à ramener le lanceur 24 vers une butée 52 située à l'opposé de l'arrêt 50 et portée à la figure 1 par le réducteur à train épicycloïdal. Cette force axiale de réaction s'ajoute aux forces de rappel du noyau mobile 20 de l'électro-aimant 17 après la coupure de l'alimentation du contacteur 18. Le pignon 14 s'échappe rapidement de la couronne 16 avec une vitesse suffisante pour éviter une usure et une détérioration des extrémités des dents.At the end of the start, the combustion engine takes its idle speed, and drives the pinion 14 of the launcher 24 at a very high speed. The free wheel 26 or the conical clutch is then urged in the opposite direction, and is released to protect the electric motor 10 from an overspeed. The launcher 24 then tends to unscrew on the splines 40 of the shaft 12, which generates an axial force tending to bring the launcher 24 to a stop 52 located opposite the stop 50 and brought to the figure 1 by the epicyclic gearbox. This axial reaction force is added to the restoring forces of the moving core 20 of the electromagnet 17 after the power supply of the contactor 18 has been cut off. The pinion 14 rapidly escapes from the ring gear 16 with a speed sufficient to avoid wear and damage to the ends of the teeth.

La présence des cannelures 40, 42 hélicoïdales du lanceur 24 des figures 1 et 2, présentent ainsi un double avantage :

  • elles facilitent l'engagement du pignon 14 dans la couronne 16 en évitant une usure prématurée des flancs de dents ;
  • elles accroissent la vitesse de sortie du pignon 14 en évitant la détérioration des faces frontales de dentures.
The presence of the helical grooves 40, 42 of the launcher 24 of the figures 1 and 2 , thus have a double advantage:
  • they facilitate the engagement of the pinion 14 in the ring 16 avoiding premature wear of the tooth flanks;
  • they increase the output speed of the pinion 14 avoiding the deterioration of the end faces of teeth.

Les cannelures 40, 42 d'un lanceur conventionnel présentent en développé, des flancs rectilignes ayant un angle d'inclinaison constant par rapport à l'axe de l'arbre 12 (voir figure 2).The flutes 40, 42 of a conventional launcher have in development, straight flanks having a constant inclination angle with respect to the axis of the shaft 12 (see figure 2 ).

On a constaté que ces avantages sont d'autant plus prononcés que l'angle d'inclinaison des cannelures 40, 42 est grand par rapport à l'axe longitudinal. Mais l'augmentation de l'angle d'inclinaison des cannelures 40, 42 provoque une augmentation de la force axiale générée par les pics de couple lors de l'entraînement du moteur thermique. Cette force s'exerce contre l'arrêt 50 qui doit être dimensionné en conséquence pour éviter une usure prématurée. L'arrêt 50 comporte généralement un anneau 54 élastique logé dans une gorge annulaire de l'arbre de sortie 12, et une bague 56 circulaire coiffant concentriquement l'anneau 54. En fin de course de travail, le pignon 14 vient buter contre la face frontale de la bague 56.It has been found that these advantages are all the more pronounced as the angle of inclination of the splines 40, 42 is large relative to the longitudinal axis. But increasing the inclination angle of the splines 40, 42 causes an increase in the axial force generated by the torque peaks during the drive of the engine. This force is exerted against the stop 50 which must be dimensioned accordingly to avoid premature wear. The stop 50 generally comprises an elastic ring 54 housed in an annular groove of the output shaft 12, and a concentric ring concentrating ring 56 the ring 54. At the end of the working stroke, the pinion 14 abuts against the front face of the ring 56.

Les inconvénients d'un angle de cannelures trop grand sont les suivants :

  • risque d'usure de la surface de l'anneau 54 en contact avec l'arbre 12 ;
  • risque d'usure de la surface de l'anneau 54 en contact avec la bague 56 ;
  • risque de cisaillement de l'anneau 54 élastique ;
  • risque d'usure et même d'éclatement de la bague 56 ;
  • détérioration de la gorge de logement de l'anneau 54 ;
  • risque de rupture de l'arbre 12 au niveau de la gorge.
The disadvantages of an angle of grooves too large are the following:
  • risk of wear of the surface of the ring 54 in contact with the shaft 12;
  • risk of wear of the surface of the ring 54 in contact with the ring 56;
  • risk of shearing the elastic ring 54;
  • risk of wear and even bursting of the ring 56;
  • deterioration of the housing groove of the ring 54;
  • risk of rupture of the shaft 12 at the throat.

Pour réduire ces risques, un renforcement de la tenue mécanique de l'arrêt 50 par augmentation de son dimensionnement, se heurte à un problème d'encombrement. En effet, le diamètre extérieur de la bague 56 ne doit pas être supérieur au diamètre du pignon 14 pour éviter tout contact avec la couronne 16. Une augmentation de la section de l'anneau 54 nécessiterait une gorge plus importante, ce qui affaiblit d'autre part la résistance mécanique de l'arbre 12.To reduce these risks, a strengthening of the mechanical strength of the stop 50 by increasing its dimensioning, faces a problem of space. Indeed, the outer diameter of the ring 56 must not be greater than the diameter of the pinion 14 to avoid contact with the ring 16. An increase in the section of the ring 54 would require a larger groove, which weakens on the other hand the mechanical strength of the shaft 12.

Un autre inconvénient résulte du bruit engendré par le choc mécanique du pignon 14 venant en butée contre l'arrêt 50. Plus l'angle d'inclinaison des cannelures 40, 42 est élevé, plus le choc est important, ainsi que le bruit. Ce bruit apparaît aussi à chaque phase de compression et de décompression du moteur thermique lorsque ce dernier est entraîné par le démarreur. En effet à chaque décompression, le moteur thermique entraîne le pignon 14 à une vitesse supérieure à celle de l'arbre de sortie 12. Il en résulte un passage momentané en roue libre avec rattrapage des jeux de denture, et recul du pignon 14. A la compression suivante, le démarreur redevient menant avec un rattrapage du jeu de denture et de jeu contre l'arrêt 50 qui se traduit par un choc mécanique et une émission sonore.Another disadvantage results from the noise generated by the mechanical shock of the pinion 14 abutting against the stop 50. The greater the angle of inclination of the grooves 40, 42, the greater the shock is important, as well as the noise. This noise also appears at each stage of compression and decompression of the engine when the latter is driven by the starter. Indeed, at each decompression, the heat engine drives the pinion 14 at a speed greater than that of the output shaft 12. This results in a momentary passage freewheel with catching of the sets of teeth, and retreat of the pinion 14. A the next compression, the starter becomes again leading with a catch-up of the backlash and play against the stop 50 which results in a mechanical shock and a sound emission.

Objet de l'inventionObject of the invention

L'invention a pour but de pallier ces inconvénients, et de réaliser un démarreur facilitant la pénétration du pignon du lanceur dans la couronne, et réduisant les contraintes mécaniques pendant le fonctionnement.The invention aims to overcome these disadvantages, and to achieve a starter facilitating the penetration of the starter gear in the ring, and reducing mechanical stresses during operation.

Selon l'invention, ce but est atteint par le fait que les cannelures hélicoïdales du moyeu d'entraînement possèdent un angle de contact variable en fonction de la position axiale du lanceur entre la position de repos et la position de travail, ledit angle de contact étant déterminé par l'inclinaison de la tangente au point d'engagement d'une dent de moyeu avec l'un des flancs de deux dents d'arbre consécutives.According to the invention, this object is achieved by the fact that the helical grooves of the drive hub have a variable contact angle depending on the axial position of the launcher between the rest position and the working position, said contact angle being determined by the inclination of the tangent at the point of engagement of a hub tooth with one of the flanks of two consecutive tree teeth.

L'angle de contact est avantageusement plus grand du côté de la position de repos que de la position de travail.The contact angle is advantageously greater on the resting position side than on the working position.

Un tel lanceur permet ainsi d'atteindre un double objectif, consistant d'une part à faciliter la pénétration du pignon dans la couronne, puis son échappement au moment de la sortie après démarrage, et d'autre part à réduire les réactions mécaniques exercées par le pignon sur la butée d'arrêt en fin d'engagement dans la couronne.Such a launcher thus makes it possible to achieve a dual objective, consisting first of all in facilitating the penetration of the pinion into the ring gear, then its escape at the time of the exit after starting, and secondly in reducing the mechanical reactions exerted by the pinion on the stop stop at the end of engagement in the crown.

Selon un mode de réalisation préférentiel, l'angle de contact est de préférence compris entre 15° et 30° au moment de la pénétration du pignon et au moment de sa sortie de la couronne. L'angle de contact est compris entre 0° et 20° lorsque le pignon vient en butée contre l'arrêt dans la position de travail, et pendant l'entraînement du moteur à combustion.According to a preferred embodiment, the contact angle is preferably between 15 ° and 30 ° at the moment of penetration of the pinion and at the moment of its exit from the ring. The contact angle is between 0 ° and 20 ° when the pinion abuts against the stop in the working position, and during the driving of the combustion engine.

Pour obtenir un engagement et un échappement en douceur du pignon dans et hors de la couronne, le dispositif peut avantageusement être complété par une ou plusieurs des caractéristiques suivantes :

  • l'angle de contact peut être variable de façon continue ou discontinue ;
  • pour une position axiale prédéterminée du lanceur, l'angle de contact est différent selon que la dent de moyeu coopère avec le flanc d'une dent d'arbre, ou avec le flanc opposé de la dent d'arbre adjacente;
  • chaque dent de moyeu est conformée pour définir un jeu de fonctionnement entre les flancs correspondants des dents d'arbre, ledit jeu est minimum lorsque le lanceur se trouve en position de travail ;
  • les flancs des dents d'arbre et des dents de moyeu présentent des formes conjuguées, notamment des segments rectilignes ou curvilignes, pour augmenter la surface de contact en prise ;
  • chaque dent de moyeu possède un profil arrondi et allongé suivant la direction de déplacement dans la cannelure d'arbre ;
  • chaque dent de moyeu présente une forme prismatique coopérant avec des segments de droites inclinées appartenant aux flancs des dents d'arbre.
To obtain a commitment and a smooth escape of the pinion in and out of the crown, the device can advantageously be completed by one or more of the following characteristics:
  • the contact angle can be variable continuously or discontinuously;
  • for a predetermined axial position of the launcher, the contact angle is different depending on whether the hub tooth cooperates with the sidewall of a shaft tooth, or with the opposite side of the adjacent shaft tooth;
  • each hub tooth is shaped to define an operating clearance between the corresponding flanks of the shaft teeth, said clearance is minimum when the launcher is in the working position;
  • the flanks of the shaft teeth and the hub teeth have conjugate shapes, including rectilinear or curvilinear segments, to increase the contact contact area;
  • each hub tooth has a rounded and elongated profile in the direction of movement in the shaft spline;
  • each hub tooth has a prismatic shape cooperating with inclined line segments belonging to the flanks of the shaft teeth.

Description sommaire des dessinsBrief description of the drawings

D'autres avantages et caractéristiques ressortiront plus clairement de la description qui va suivre de modes particuliers de réalisation de l'invention donnés à titre d'exemples non limitatifs, et représentés aux dessins annexés, dans lesquels :

  • La figure 1 est une vue schématique en coupe d'un démarreur connu de l'art antérieur.
  • La figure 2 montre une vue du lanceur équipant le démarreur de la figure 1.
  • Les figures 3 à 7 sont des vues schématiques en développé d'un premier mode de réalisation d'un lanceur selon l'invention, les cannelures d'arbre et du lanceur se trouvant en différentes positions lors des phases d'engagement et d'échappement du pignon.
  • Les figures 8 à 12 représentent des vues similaires à celles des figures 3-7 d'une variante de réalisation des cannelures.
Other advantages and features will emerge more clearly from the following description of particular embodiments of the invention given as non-limiting examples, and represented in the accompanying drawings, in which:
  • The figure 1 is a schematic sectional view of a starter known from the prior art.
  • The figure 2 shows a view of the launcher equipping the starter of the figure 1 .
  • The Figures 3 to 7 are schematic views in developed of a first embodiment of a launcher according to the invention, the shaft splines and launcher lying in different positions during the engagement and exhaust phases of the pinion.
  • The Figures 8 to 12 represent views similar to those of Figures 3-7 of an alternative embodiment of the splines.

Description de deux modes de réalisation préférentiels.Description of two preferred embodiments.

Les mêmes numéros de repères seront utilisés pour désigner des pièces similaires ou identiques à celles des figures 1 et 2.The same reference numbers will be used to designate similar or identical parts to those of figures 1 and 2 .

En référence aux figures 3 à 7, la présente invention est basée sur des cannelures 40, 42 hélicoïdales ayant un angle d'hélice variable en fonction de la position axiale du lanceur 24 le long de l'arbre de sortie représenté en 12 à la figure 1.With reference to Figures 3 to 7 , the present invention is based on helical splines 40, 42 having a variable helix angle as a function of the axial position of the launcher 24 along the output shaft shown at 12 to the figure 1 .

Sur la figure 3 correspondant à la position de repos du lanceur 24, l'axe géométrique de l'arbre de sortie 12 du démarreur est représenté en XX'. Deux des dents d'arbre 40a, 40b comportent respectivement des flancs incurvés AB, CD délimitant une cannelure d'arbre 40, laquelle présente une inclinaison variable par rapport à l'axe XX', contrairement aux flancs rectilignes à angle d'inclinaison constant utilisés dans les démarreurs de l'art antérieur. La dent 42a d'une cannelure 42 du moyeu 30 entraîneur est schématisée par un profil arrondi et globalement allongé suivant une direction sensiblement voisine de celle de la cannelure d'arbre 40. Le profil est ici globalement ovale Une pluralité de dents 40a, 40b, 42a sont réparties à intervalles réguliers à la périphérie de l'arbre 12 pour diminuer les contraintes de contact lors du fonctionnement du démarreur.On the figure 3 corresponding to the rest position of the launcher 24, the geometric axis of the output shaft 12 of the starter is represented at XX '. Two of the shaft teeth 40a, 40b respectively comprise curved flanks AB, CD delimiting a shaft spline 40, which has a variable inclination relative to the axis XX ', in contrast to the straight flanks with a constant inclination angle used. in the starters of the prior art. The tooth 42a of a groove 42 of the hub 30 is shown schematically by a rounded profile and generally elongated in a direction substantially similar to that of the shaft spline 40. The profile here is generally oval A plurality of teeth 40a, 40b, 42a are distributed at regular intervals around the periphery of the shaft 12 to reduce the contact stresses during operation of the starter.

La position axiale du centre de la dent 42a du moyeu 30 est représentée par X0 sur l'axe x parallèle à l'axe XX' de l'arbre 12. Cette position X0 correspond à la position axiale de repos du lanceur, dans laquelle la dent 42a se trouve en contact en K1 avec le flanc menant AB. La tangente en K1 fait un angle a1 avec l'axe XX'.The axial position of the center of the tooth 42a of the hub 30 is represented by X 0 on the x axis parallel to the axis XX 'of the shaft 12. This position X 0 corresponds to the axial rest position of the launcher, in which tooth 42a is in contact with K1 with the leading edge AB. The tangent at K 1 makes an angle a1 with the axis XX '.

Sur la figure 4, le pignon 14 arrive en butée contre la couronne 16, et le lanceur 24 se trouve à cet instant à la position axiale X1. La distance X0X1 représente l'intervalle entre la couronne 16 et le lanceur 24 au repos. Le moteur électrique 10 commence à tourner (voir flèche R illustrant la rotation de l'arbre 12), ce qui maintient la dent 42a contre le flanc menant AB au point K2. La tangente au point K2 fait un angle a2 avec l'axe XX', favorable à la pénétration du pignon 14 dans la couronne 16. La valeur de l'angle a2 est de préférence choisie entre 15° et 30°.On the figure 4 the pinion 14 comes into abutment against the crown 16, and the launcher 24 is at this moment in the axial position X 1 . The distance X 0 X 1 represents the interval between the ring 16 and the launcher 24 at rest. The electric motor 10 begins to rotate (see arrow R illustrating the rotation of the shaft 12), which maintains the tooth 42a against the leading edge AB at the point K2. The tangent at the point K2 makes an angle α2 with the axis XX ', favorable to the penetration of the pinion 14 in the ring 16. The value of the angle a2 is preferably chosen between 15 ° and 30 °.

Lorsqu'une dent de pignon14 arrive en regard d'un entre dent de la couronne 16, le pignon 14 commence sa pénétration dans la couronne 16. La rotation du moteur électrique 10 va ensuite favoriser la poursuite de la pénétration suite à la présence d'un angle a2 élevé.When a pinion tooth 14 comes opposite a gap in the ring gear 16, the pinion 14 begins to penetrate into the ring gear 16. The rotation of the electric motor 10 will then favor the continuation of the penetration due to the presence of the pinion. a high angle a2.

Sur la figure 5, le pignon 14 arrive en butée contre l'arrêt 50, et le lanceur 24 se trouve à cet instant à la position axiale X2 de fin de course. La distance X0X2 représente la course axiale totale du pignon 14 entre la position de repos et la position de travail. Ayant à entraîner le moteur à combustion, la dent 42a du moyeu 30 entraîneur est toujours en contact avec le flanc menant AB au point K3. La tangente au point K3 fait un angle a3 avec l'axe de l'arbre 12. La valeur de l'angle a3 est inférieure à l'angle a2, de manière à réduire la pression de contact contre l'arrêt 50. La valeur de l'angle a3 sera de préférence choisie entre 0° et 20°.On the figure 5 the pinion 14 comes into abutment against the stop 50, and the launcher 24 is at this moment in the axial position X 2 end of stroke. The distance X 0 X 2 represents the total axial travel of the pinion 14 between the rest position and the working position. Having to drive the combustion engine, the tooth 42a of the drive hub 30 is always in contact with the leading edge AB at point K3. The tangent at the point K3 makes an angle a3 with the axis of the shaft 12. The value of the angle a3 is smaller than the angle a2, so as to reduce the contact pressure against the stop 50. The value the angle a3 will preferably be chosen between 0 ° and 20 °.

La vitesse d'arrivée du pignon 14 contre l'arrêt 50 est ainsi réduite du fait de la diminution de l'angle d'inclinaison de a2 à a3. Le choc et le bruit qui en résultent sont ainsi diminués, ce qui réduit les contraintes et l'usure de l'arrêt 50.The speed of arrival of the pinion 14 against the stop 50 is thus reduced because of the decrease in the angle of inclination of a2 to a3. The shock and the resulting noise are thus reduced, which reduces the stress and wear of the stop 50.

Sur la figure 6, le lanceur 24 se trouve en mode de roue libre, étant donné que le pignon 14 tourne plus vite que l'arbre 12. Les forces de frottement et le couple résiduel de roue libre amènent la dent 42a du moyeu 30 entraîneur en contact avec le flanc CD de la dent 40b, laquelle est séparée du flanc 40a par la cannelure 40. La tangente au point de contact K4 fait un angle a4 avec l'axe de l'arbre 12.On the figure 6 , the launcher 24 is in freewheel mode, since the pinion 14 rotates faster than the shaft 12. The frictional forces and the residual freewheel torque bring the tooth 42a of the driver hub 30 into contact with the CD flank of the tooth 40b, which is separated from the flank 40a by the groove 40. The tangent to the point of contact K4 makes an angle a4 with the axis of the shaft 12.

La valeur de l'angle a4 est choisie de préférence entre 0° et 20°, c'est à dire du même ordre de grandeur que celui de l'angle a3. Il en résulte une réduction des forces de dévissage sur les cannelures 40, 42, qui sont à l'origine des mouvements de va-et-vient contre l'arrêt 50 à la suite des phases de compression et de décompression pendant l'entraînement du moteur thermique. Une telle valeur a4 permet également de diminuer les bruits et l'usure.The value of the angle a4 is preferably chosen between 0 ° and 20 °, that is to say of the same order of magnitude as that of the angle a3. This results in a reduction of the unscrewing forces on the splines 40, 42, which are at the origin of the movements back and forth against the stop 50 following the compression and decompression phases during the drive of the thermal motor. Such a value a4 also reduces noise and wear.

Sur la figure 7, le pignon 14 du lanceur 24 se dégage de la couronne 16 suite à l'interruption de l'alimentation du contacteur 18. L'intervention des forces de rappel du ressort 48 du noyau mobile 20, et des forces de dévissage du lanceur 24 ramène ce dernier vers la position de repos. Lorsque la dent 42a du moyeu 30 arrive dans la position axiale X1 le pignon 14 est sorti de la couronne 16. La dent 42a se trouve en contact au point K5 avec le flanc CD de la dent 40b, où la tangente avec l'axe XX' fait un angle a5, qui sera choisi de préférence entre 15° et 30°. Cette valeur élevée de l'angle a5 assure une sortie rapide du pignon 14 hors de la couronne 16, ce qui réduit les usures par frottement des faces de denture.On the figure 7 , the pinion 14 of the launcher 24 is disengaged from the ring 16 following the interruption of the supply of the contactor 18. The intervention of the return forces of the spring 48 of the movable core 20, and the unscrewing forces of the launcher 24 brings back the latter to the rest position. When the tooth 42a of the hub 30 arrives in the axial position X 1 the pinion 14 is out of the ring 16. The tooth 42a is in contact at the point K5 with the sidewall CD of the tooth 40b, where the tangent with the axis XX 'makes an angle a5, which will preferably be chosen between 15 ° and 30 °. This high value of the angle a5 ensures rapid output of the pinion 14 out of the ring 16, which reduces wear by friction of the toothing faces.

On constate qu'au moment de la pénétration du pignon 14 et au moment de son échappement de la couronne 16, l'angle de cannelure est assez élevé (de l'ordre de 15° à 30°), tandis que lors de la butée contre l'arrêt 50 en fin d'engagement dans la couronne 16, et pendant l'entraînement du moteur thermique, l'angle de cannelure est nettement plus faible (de l'ordre de 0° à 20°). La variation d'inclinaison de l'angle de cannelure entre la position de repos et la position de travail est progressive et continue.It is found that at the time of penetration of the pinion 14 and at the time of its escape from the ring 16, the flute angle is quite high (of the order of 15 ° to 30 °), while at the stop against the stop 50 at the end of engagement in the ring 16, and during the drive of the heat engine, the spline angle is significantly lower (of the order of 0 ° to 20 °). The inclination variation of the spline angle between the rest position and the working position is gradual and continuous.

Il est clair que le profil du flanc CD peut être différent de celui du flanc AB. Le jeu j entre la dent 42a et le flanc AB peut être variable en fonction de la position du lanceur et des profils de lanceur et d'arbre choisis. Ce jeu est de préférence supérieur à 0.05 mm pour assurer un bon glissement sans risque de coincement. On évitera des jeux trop importants, notamment en position travail pour limiter les chocs de rattrapage de jeu pendant la phase d'entraînement du moteur thermique.It is clear that the profile of the sidewall CD may be different from that of the sidewall AB. The clearance j between the tooth 42a and the sidewall AB may be variable depending on the position of the launcher and the selected pitcher and tree profiles. This game is preferably greater than 0.05 mm to ensure a good slip without risk of jamming. Excessive play will be avoided, particularly in the working position to limit backlash shocks during the drive phase of the engine.

En référence aux figures 8 à 12 d'une variante de réalisation, la dent 142a du moyeu 30 entraîneur présente une forme prismatique MNPQRS, obtenue par moulage, extrusion, ou frappe à froid. Chaque flanc des dents d'arbre 140a, 140b est composé de deux segments de droites inclinées AA1, A1B ; CC1, C1D.With reference to Figures 8 to 12 of an alternative embodiment, the tooth 142a of the hub gear 30 has a prismatic shape MNPQRS, obtained by molding, extrusion, or cold stamping. Each side of the shaft teeth 140a, 140b is composed of two segments of inclined lines AA1, A1B; CC1, C1D.

Le segment AA1 fait un angle a1 avec l'axe de l'arbre 12, de préférence compris entre 15° et 30°. Le segment A1B fait un angle a3 avec l'axe de l'arbre 12, de préférence compris entre 0° et 20°.The segment AA1 makes an angle a1 with the axis of the shaft 12, preferably between 15 ° and 30 °. The segment A1B makes an angle a3 with the axis of the shaft 12, preferably between 0 ° and 20 °.

Le segment DC1 fait un angle a4 avec l'axe de l'arbre 12, de préférence compris entre 0° et 20°. Le segment CC1 fait un angle a5 avec l'axe de l'arbre 12, de préférence compris entre 15° et 30°.The segment DC1 makes an angle α4 with the axis of the shaft 12, preferably between 0 ° and 20 °. The CC1 segment makes an angle a5 with the axis of the shaft 12, preferably between 15 ° and 30 °.

Le choix de la valeur des angles correspond à celui décrit précédemment dans les figures 3 à 7.The choice of the value of the angles corresponds to that described previously in the Figures 3 to 7 .

La figure 8 correspond à la position de repos, où l'arête NM de la dent 142a du moyeu 30 entraîneur est en contact avec le segment AA1 de la dent d'arbre 140a.The figure 8 corresponds to the rest position, where the edge NM of the tooth 142a of the drive hub 30 is in contact with the segment AA1 of the shaft tooth 140a.

La figure 9 correspond au contact du pignon 14 contre la couronne 16. L'angle d'inclinaison de contact entre lanceur 24 et arbre 12 reste égal à a1 jusqu'à ce que le point N arrive au point intermédiaire A1.The figure 9 corresponds to the contact of the pinion 14 against the ring 16. The pitch angle of contact between the launcher 24 and shaft 12 remains equal to A1 until the point N reaches the intermediate point A1.

Sur la figure 10, l'angle d'inclinaison de contact prend la valeur a3 jusqu'à l'arrivée du pignon 14 contre l'arrêt 50. L'arête PN de la dent 142a du moyeu 30 entraîneur est en contact avec le segment BA1 de la dent d'arbre 140a.On the figure 10 the contact angle of inclination is set to a3 until the pinion 14 arrives at the stop 50. The edge PN of the tooth 142a of the hub 30 is in contact with the segment BA1 of the tooth 140a.

La figure 11 correspond à la position de butée contre l'arrêt 50. L'arête RS de la dent 142a du moyeu 30 entraîneur est en contact avec le segment DC1 de la dent d'arbre 140b.The figure 11 corresponds to the stop position against the stop 50. The edge RS of the tooth 142a of the drive hub 30 is in contact with the segment DC1 of the shaft tooth 140b.

La figure 12 correspond à la phase de roue libre pour le retour du lanceur vers la position de repos. L'angle d'inclinaison de contact passe de a4 à a5 lorsque le point R a dépassé le point C1.The figure 12 corresponds to the freewheel phase for the return of the launcher to the rest position. The contact angle of inclination changes from a4 to a5 when the point R has exceeded the point C1.

Il en résulte un maximum de surface de contact, notamment en position de travail et lors du rattrapage de jeu pendant l'entraînement du moteur thermique.This results in a maximum contact surface, especially in the working position and during the play catch during the drive of the engine.

Bien entendu le démarreur peut avoir une structure différente. En particulier le ressort 48 de la figure 1 peut intervenir entre la fourchette et le dispositif de transmission 26. En variante ce ressort peut intervenir entre l'arrêt 50 et le pignon 14 comme visible par exemple dans le document US A 2 960 879 . Le pignon 14 peut s'étendre à l'extérieur du carter 32 comme décrit dans le document FR A 2 745 855 . Dans ce cas l'arrêt est à l'extérieur du carter.Of course the starter can have a different structure. In particular the spring 48 of the figure 1 can intervene between the fork and the transmission device 26. Alternatively this spring can intervene between the stop 50 and the pinion 14 as visible for example in the document US A 2,960,879 . The pinion 14 can extend outside the housing 32 as described in the document FR A 2,745,855 . In this case the stop is outside the housing.

Le contacteur électromagnétique en variante est monté dans le prolongement axial du moteur électrique comme visible à la figure 6 du document FR 02 08306 déposé le 03/07/2002. Dans ce cas le contacteur est coaxial au pignon et la bobine de l'électroaimant entoure le lanceur en étant portée par la partie avant du carter. Le lanceur joue le rôle du noyau mobile en sorte que la présence du levier de commande n'est pas obligatoire. Le mécanisme de commande du déplacement en translation du lanceur ne comporte donc pas forcément un levier. Ce mécanisme comporte en variante un actionneur comme décrit dans le document FR A 2 710 696 . Dans ce cas l'arbre de sortie est confondu avec l'arbre de sortie du moteur électrique et le contacteur est coaxial à l'actionneur en étant monté à l'avant du moteur 10.The electromagnetic contactor as a variant is mounted in the axial extension of the electric motor as visible in FIG. figure 6 of the document FR 02 08306 deposited on 03/07/2002. In this case the contactor is coaxial with the pinion and the coil of the electromagnet surrounds the launcher being carried by the front part of the housing. The launcher plays the role of the mobile core so that the presence of the control lever is not mandatory. The mechanism for controlling the translational movement of the launcher therefore does not necessarily include a lever. This mechanism comprises alternatively an actuator as described in the document FR A 2,710,696 . In this case the output shaft is coincident with the output shaft of the electric motor and the contactor is coaxial with the actuator being mounted at the front of the motor 10.

Le contacteur en variante s'étend à l'arrière du moteur électrique de manière perpendiculaire à celui-ci comme décrit dans le document FR 02 08356 déposé le 03/07/2002. Dans ce cas il faut prévoir un mécanisme de renvoi entre le levier de commande en forme de fourchette et le noyau mobile du contacteur. Ce mécanisme comporte une tige s'étendant parallèlement au moteur électrique et au dessus de celui-ci. Cette tige intervient entre la fourchette de commande et un levier de renvoi sur lequel agit le noyau mobile.The alternating contactor extends at the rear of the electric motor perpendicularly thereto as described in the document FR 02 08356 deposited on 03/07/2002. In this case it is necessary to provide a return mechanism between the fork-shaped control lever and the movable core of the contactor. This mechanism has a rod extending parallel to the electric motor and above it. This rod intervenes between the control fork and a return lever on which the mobile core acts.

Claims (11)

  1. Electric starter for a combustion engine of a motor vehicle, and comprising:
    - an electric motor (10) which is supplied by a contactor (18) with an electro-magnet (17), and has a rotor (44) which is coupled to an output shaft (12);
    - a launcher (24) equipped with a pinion (14) in order to drive a toothed ring (16) of the flywheel of the combustion engine, the said pinion being able to slide axially on the output shaft (12), between a position of rest in which it is disengaged from the ring (16), and an active position of work in which it engages with the said ring (16);
    - a transmission device which is disposed between the pinion (14) and a drive hub (30), which consists of two series of helical grooves (40, 42) with complementary forms which are disposed respectively in the output shaft (12), and in a cylindrical bush (31) inside the hub (30), the said transmission device comprising means to rotate the pinion (14) during the normal starting stage, and to disengage the mechanical drive connection when the speed of the pinion (14) is greater than that of the hub (30); and
    - a control mechanism (22) which is associated with the contactor (18) for displacement in translation of the launcher (24), between the two positions of rest and work defined by stop means,
    characterised in that the helical grooves (40, 42) in the drive hub (30) have a contact angle (a1, a2, a3, a4, a5) which is variable according to the axial position of the launcher (24), between the position of rest and the position of work, the said contact angle being determined by the inclination of the tangent to the point of engagement of a tooth of the hub (42a) with one of the flanks (AB, CD) of two consecutive teeth (40a, 40b) of the shaft.
  2. Starter according to claim 1, characterised in that the contact angle is greater on the rest position side than on the work position side.
  3. Starter according to claim 1, characterised in that the contact angle is variable continuously or discontinuously.
  4. Starter according to claim 1, characterised in that the contact angle is between 15° and 30° at the moment of penetration of the pinion (14) and at the moment of emergence of the latter from the ring (16).
  5. Starter according to claim 4, characterised in that the contact angle is between 0° and 20° when the pinion (14) abuts the stop (50) in the work position, and during the driving of the combustion engine.
  6. Starter according to claim 1, characterised in that, for a predetermined axial position of the launcher (24), the contact angle is different, depending on whether the tooth (42a) of the hub is co-operating with the flank (AB) of the tooth (40a) of the shaft, or with the flank (CD) of the adjacent tooth (40b) of the shaft.
  7. Starter according to claim 1, characterised in that each tooth (42a) of the hub is formed so as to define functioning play between the corresponding flanks (AB, CD) of the teeth (40a, 40b) of the shaft.
  8. Starter according to claim 7, characterised in that the said play is minimum when the launcher (24) is in the position of work.
  9. Starter according to claim 7, characterised in that the flanks of the teeth (40a, 40b; 140a, 140b) of the shaft and of the teeth (42a, 142b) of the hub have conjugated forms, and in particular straight or curved segments, in order to increase the contact surface during engagement.
  10. Starter according to claim 9, characterised in that each tooth (42a) of the hub has a rounded profile which is elongate according to the direction of displacement in the groove in the shaft (40).
  11. Starter according to claim 9, characterised in that each tooth (142a) of the hub has a prismatic form (MNPQRS) which co-operates with segments of inclined straight lines (AA1, A1B; CC1, C1D) which belong to the flanks of the teeth of the shaft (140a, 140b).
EP02803834A 2001-11-30 2002-11-27 Motor vehicle electric starter equipped comprising a starting motor with improved splines Expired - Lifetime EP1461528B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0115556 2001-11-30
FR0115556A FR2833043B1 (en) 2001-11-30 2001-11-30 ELECTRIC STARTER OF A MOTOR VEHICLE EQUIPPED WITH A STARTER WITH IMPROVED SPLINES
PCT/FR2002/004061 WO2003046371A1 (en) 2001-11-30 2002-11-27 Motor vehicle electric starter equipped comprising a starting motor with improved splines

Publications (2)

Publication Number Publication Date
EP1461528A1 EP1461528A1 (en) 2004-09-29
EP1461528B1 true EP1461528B1 (en) 2008-03-12

Family

ID=8870010

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Application Number Title Priority Date Filing Date
EP02803834A Expired - Lifetime EP1461528B1 (en) 2001-11-30 2002-11-27 Motor vehicle electric starter equipped comprising a starting motor with improved splines

Country Status (7)

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EP (1) EP1461528B1 (en)
AT (1) ATE389108T1 (en)
BR (1) BR0206597A (en)
DE (1) DE60225594T2 (en)
FR (1) FR2833043B1 (en)
PL (1) PL201139B1 (en)
WO (1) WO2003046371A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2920837B1 (en) * 2007-09-10 2013-08-02 Valeo Equip Electr Moteur ROTATING ELECTRIC MACHINE, IN PARTICULAR A STARTER

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2960879A (en) * 1956-10-13 1960-11-22 Lafitte Theodore Positively operated starting device for starting motors
US4479394A (en) * 1981-06-18 1984-10-30 Eaton Stamping Company Electric starter with confined cushion
JPH0633750B2 (en) * 1987-08-26 1994-05-02 株式会社日立製作所 Starter with reduction mechanism
DE3813496A1 (en) * 1988-04-22 1989-11-02 Pierburg Gmbh Starter motor for the starting sequence of an internal combustion engine
FR2673247B1 (en) * 1991-02-22 1996-03-01 Valeo Equip Electr Moteur STARTER OF INTERNAL COMBUSTION ENGINE, PARTICULARLY, STARTER OF MOTOR VEHICLE.

Also Published As

Publication number Publication date
PL368822A1 (en) 2005-04-04
EP1461528A1 (en) 2004-09-29
FR2833043B1 (en) 2004-01-23
DE60225594T2 (en) 2009-03-26
ATE389108T1 (en) 2008-03-15
PL201139B1 (en) 2009-03-31
FR2833043A1 (en) 2003-06-06
DE60225594D1 (en) 2008-04-24
BR0206597A (en) 2004-02-25
WO2003046371A1 (en) 2003-06-05

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