EP1478844B1 - Starter, particularly for a motor vehicle, provided with a torque-accumulating bendix gear - Google Patents

Starter, particularly for a motor vehicle, provided with a torque-accumulating bendix gear Download PDF

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Publication number
EP1478844B1
EP1478844B1 EP03722671A EP03722671A EP1478844B1 EP 1478844 B1 EP1478844 B1 EP 1478844B1 EP 03722671 A EP03722671 A EP 03722671A EP 03722671 A EP03722671 A EP 03722671A EP 1478844 B1 EP1478844 B1 EP 1478844B1
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EP
European Patent Office
Prior art keywords
pinion
case
electric starter
spiral spring
output shaft
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
EP03722671A
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German (de)
French (fr)
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EP1478844A1 (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 EP1478844A1 publication Critical patent/EP1478844A1/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
    • F02N15/062—Starter drives
    • F02N15/063—Starter drives with resilient shock absorbers
    • 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
    • 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
    • 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

Definitions

  • a motor vehicle starter conventionally comprises a rotary electric motor for rotating an output shaft equipped with a movable pinion intended to cooperate with a ring gear to start the combustion engine of the vehicle.
  • the ring gear is called the starter ring and is secured by an annular piece, such as a flywheel, rigidly or resiliently connected to the crankshaft of the internal combustion engine of the motor vehicle.
  • the output shaft is in one embodiment coincident with the output shaft of the electric motor of the starter.
  • the output shaft is distinct from the output shaft of the electric motor of the starter.
  • an epicyclic gear train is arranged between the two shafts as described in the document EP 0 708 239 or in the document FR A 2,751,803 .
  • the pinion is generally slidably mounted on the output shaft between a rest position, in which it is disengaged from the ring gear, and an active working position in which it meshes with said ring gear, which is connected in rotation to the crankshaft of the vehicle engine.
  • a control member usually in the form of an actuating lever, is controlled by a contactor, and cooperates with a freewheeling launcher or conical clutch.
  • the conical clutch or the freewheel are arranged between the pinion and a coach belonging to the launcher.
  • the lever acts on the driver or on a housing that includes the freewheel or the conical clutch. In a conventional starter the housing is integral with the trainer.
  • This trainer comprises a drive bushing having at its inner periphery helical grooves cooperating in a complementary manner with helical grooves locally present the output shaft at its outer periphery. In the active position the pinion cooperates with an abutment integral with the output shaft.
  • the main function of the disengageable torque transmission device is to prevent, when the internal combustion engine, also called the engine, of the motor vehicle starts, the pinion drives the electric motor of the starter at a speed that is too great, which may deteriorate this motor. latest.
  • the documents FR 96 13016 , FR 96 13015 and FR 96 09550 - published respectively under the numbers FR 2 754 857 , FR 2 754 856 and FR 2 751 803 - refer to damping devices intended to absorb shocks and vibrations generated during starter operation. The damping function results in a decrease in the intensity of the shocks received at the thrower.
  • These damping devices are generally constituted by elastomer damping blocks, whose role is to absorb energy to dissipate it in the form of internal friction depending on the structure of the material, and external friction between the parts in relative motion.
  • the damping devices are mounted in a housing secured to the coach.
  • the damping device is mounted between the output shaft and the output member of the reducer.
  • the piston compresses the mixture of air and fuel, and the internal pressure gradually increases to the Top Dead Point subsequently called TDC.
  • TDC Top Dead Point
  • the starter which drives the thermal engine in rotation must therefore provide a higher and higher torque up to the PMH, which results in a decrease in the drive speed.
  • the cylinder After passing the PMH, the cylinder enters the decompression phase, during which the internal pressure creates a torque that accelerates the speed of rotation of the crankshaft. Given the respective torques and moments of inertia of the engine and the starter, the acceleration of the crankshaft is faster than that of the starter gear.
  • the pinion is is therefore driven by the heat engine, and is driven alone in overspeed following the intervention of the freewheel or conical clutch between the pinion and the electric motor of the starter.
  • the heat engine then continues its acceleration movement until the Low Dead Point, subsequently called PMB.
  • a compression phase appears in the next cylinder of the ignition sequence, resulting in a slowing of the crankshaft.
  • the electric motor of the starter no longer having a load to transmit, sees its speed increase according to the conventional laws of ramping to idle electric motors.
  • the freewheel or conical clutch locks, and the starter again provides a torque to the engine.
  • the compression cylinder torque causes the starter to slow down, delivering a higher and higher torque until TDC, and so on until the first explosions appear. Note that from time t1, the speed of the combustion engine N m and the starter speed N d are different.
  • the starter is sometimes leading, sometimes led.
  • At the beginning of each training period there is a catching of the angular clearances, and axial play between the pinion and the stop. This catch-up game results in a shock and a noise emission.
  • the load of the pinion / crown gear increases to TDC, and these load variations also result in noise emission.
  • the interval RL corresponds to the freewheeling period
  • the interval EN corresponds to the training period.
  • the object of the invention is to eliminate the backlash of play of the transmission elements to reduce the noise of the starter launcher during the drive period of the engine.
  • the device according to the invention is characterized in that the launcher is equipped with a torsionally elastic device arranged to store energy during the compression phases of the heat engine, and to restore it during the decompression phases and in that the torsionally elastic device is offset axially relative to the disengageable torque transmission device.
  • Playback is avoided because the presence of the torsionally elastic device makes it possible to keep the flanks of the teeth of the pinion in contact with the flanks of the starter ring. The energy is restored during the decompression phases, unlike the known devices of the prior art that absorb energy.
  • the torsionally elastic device at first, is compressed during the compression phases of the engine of the vehicle, then, in a second step, restores the accumulated energy to give an angular acceleration to the upper gear to that of the crankshaft. the engine of the vehicle.
  • This torsionally elastic device for a given radial space can have a large size because it is offset axially relative to the disengageable torque transmission device.
  • This arrangement makes it possible to preserve and protect the freewheel or the conical clutch and thus to increase the life of the starter while reducing the noise.
  • the torsionally resilient device advantageously comprises a spiral spring spiral wound coaxially surrounding the output shaft, being hooked between a housing of the freewheel or the conical clutch and a portion integral with the pinion or the driver.
  • This arrangement allows to store a lot of energy and allows a large angular movement between the parts between which intervenes the spiral spring. This travel is greater than with a solution involving elastically deformable elements, for example elastomer. It is possible to obtain deflections greater than 120 °, that is to say greater than the maximum instantaneous relative angular shift between the pinion and the ring gear.
  • the torsionally resilient device is housed between the pinion and the disengageable torque transmission device, such as a freewheel or conical clutch device.
  • This torsionally resilient device comprises a spiral spring coaxially surrounding the output shaft, being hooked between a housing of the freewheel or the conical clutch and a tubular extension of the pinion.
  • This preferred embodiment is simple, reliable and economical because it comprises a minimum number of parts and simplifies the pinion devoid of track for a freewheel device or conical clutch.
  • the driver is also simplified because the track or the internal friction surface of the disengageable torque transmission device is advantageously secured to the driver so that the housing associated with the torque transmission device is distinct from the driver and the driver.
  • pinion and is of simple manufacture.
  • This preferred embodiment also makes it possible to further reduce the internal diameter of the spiral spring, which thus for a given external diameter can store the maximum energy.
  • the spiral spring is imprisoned simply, reliably and economically in a compartment of the housing by means of a closing disc secured to the pinion.
  • the launcher 10 comprises a pinion 12 and a torque-free disengageable torque transmission device 14, which is composed of a driver 16 and a housing 17, here of annular shape, delimiting here a housing for rollers 19 .
  • the trainer 16 is equipped, as mentioned above, with helical splines 16a cooperating with complementary splines 16b of the output shaft 18 intended to be rotated by the electric motor of the starter.
  • This shaft 18 is in an integral embodiment with the output shaft of the electric motor or alternatively separate from the output shaft of the electric motor; an epicyclic gear train then intervening for example between the two shafts.
  • the structure of the splines 16a, 16b allows the connection in rotation and the axial displacement of the launcher 10.
  • a bore 20 is formed in the driver 16 to ensure the centering of the track cylindrical 22 of the freewheel 14 on the shaft 18.
  • the grooves 16a belong to a drive sleeve (not referenced) extending axially rearward, in the opposite direction to the pinion 12, the track 22 formed in favor of a protrusion that presents the coach locally at its outer periphery.
  • the housing 17 is hollowed out at its outer periphery for forming ramps 24 inclined, constituting cams, causing in a known manner, the jamming of the rollers 19 in a direction of rotation of the shaft 18, and the release of the rollers 19 reverse.
  • This housing is centered and guided on the shaft 18 by means of a self-lubricating ring 26 allowing the relative movements of translation and rotation.
  • the housing 17 also comprises shoulders for pressure springs acting in known manner on the rollers 19 to wedge them between the track 22 and the ramps 24.
  • a torsionally elastic device 28 is, according to the invention, mounted within the launcher axially offset with respect to the disengageable torque transmission device. This device stores the energy during the compression phases of the engine of the motor vehicle and restores this energy during the decompression phases of the engine.
  • this device 28 consists of a spiral spring hooked between the housing 17 and a part belonging to the pinion or to the driver.
  • This spring is housed in a housing compartment 17.
  • This device 28 is in one embodiment disposed between the housing 17 and the driver 16.
  • This device is arranged in the exemplary embodiment shown between the pinion 12 and the freewheel 14.
  • the housing 17 extends on the left side by a tubular sleeve 30, delimiting a compartment 31 for receiving a spiral spring 32 constituting said elastic torsion device 28.
  • the spiral spring 32 is provided with a recess 34 on the end of its outer turn allowing it to make a connection in rotation with a tab of complementary shape disposed in the sleeve 30 of the housing 17.
  • the stop rotation must be at least unidirectional in the compression direction of the spring 32.
  • the recess 34 has a rectangular section in which is placed the end of the tongue 36 of the sleeve 30. It is clear that the male and female parts of the connection can be reversed.
  • the other end on the inner turn is provided with a lug 38 allowing attachment at least in the direction of rotation necessary for the compression of the spiral spring 32.
  • the lug 38 is formed by a radially inward folding of the ribbon constituting the spring 32. This bent end is housed in a slot 33 formed in the tubular extension 40 of the pinion 12.
  • a closure disc 42 extends between the bushing 30 and the extension 40 to trap the spiral spring 32 in the compartment 31.
  • the disc 42 is fixed to the pinion 12 by welding, riveting or any other known fastening means.
  • the outer part of the disk 42 has a diameter D1 substantially equal to the outside diameter D2 of the tubular bushing 30.
  • Two circular recesses 44 locally bring the outside diameter to a value D3 less than the inside diameter D4 of the bushing 30 ( figure 3 ), so as to form two protruding sectors 46 of angle A and diametrically opposed.
  • Each sector is delimited by two faces 54 and 50 here radial ( figure 7 ).
  • the end of the sleeve 30 has cutouts 48 intended to receive the sectors 46 of the disc 42.
  • Each cutout 48 is delimited by two faces 52 and 56, here radial, of the bushing 30 and has a depth e2 slightly greater than the thickness e1 of the disc 42, and an angular width B> A.
  • the faces 50 and 54 of a sector 46 are intended to come into contact respectively with the faces 52 and 56 of the bushing 30 of the housing 17.
  • the spring 32 which is prestressed, exerts a torque C o tending to bring the face 50 of the disk 42 against the face 52 of the housing 17, so as to angularly position the pinion 12 relative to the housing 17 when the starter is at rest.
  • a hood 55 ( figure 2 ) consists of a tube of deformable material, comprising two folded ends which close the housing 17 by trapping all the components of the launcher 10. The cover is in contact by its inner periphery with the cylindrical outer periphery of the housing 17 comprising the outer periphery of the sleeve 30.
  • This cover 55 has a folded end which serves to hold a disk 142 closing the freewheel device 14 and serving as a support for the control member, such as a lever, mentioned above.
  • the figure 9 illustrates the torque generated by the spiral spring 32 as a function of the relative position PA of the pinion 12 relative to the housing 17.
  • the spring 32 begins to compress, and the pinion 12 rotates relative to the housing 17 with an increasing angle. If the maximum torque at the compression passage reaches the value C M , the pinion 12 makes a displacement A max relative to the housing 17.
  • the spring 32 restores energy by accelerating the speed of the pinion 12, which has a very low inertia compared to the electric motor of the starter.
  • the spring 32 has expanded to the angle A m corresponding to a torque C m provided by the spring.
  • the energy supplied to the pinion 12 is schematically represented by the area of the trapezium PQRS.
  • a m must be greater than 0 at the end of each decompression.
  • d For the normal operating conditions of the starter, d must be greater than A m in order not to have a significant impact of the face 54 against the face 56 of the housing 17.
  • the spring 32 At the end of starting, the spring 32 returns to its rest position bringing the face 50 of the disk 42 against the housing 17. An elastic element can be interposed between the two bearing faces to reduce the end-of-start noise. Upon return to rest of the spring 32, the freewheel 14 comes into action to allow the speed differential between the pinion 12 driven by the engine and the shaft 18 of the starter.
  • the present invention is not limited to the embodiment described.
  • the track 22 and the ramps 24 are alternatively frustoconical in shape to form a conical clutch with frustoconical friction surface as described for example in the documents FR A 2,772,433 or FR A 2,827,915 .
  • the rollers are removed and the pressure springs associated with the rollers and the driver may be plastic.
  • This coach then has the advantage of the shape of figure 3 of the document FR A 2,827,915 the launcher control member is then associated with the trainer. Complementary frustoconical friction surfaces can be reported.
  • the outer periphery of the housing 17 has at its outer periphery in one embodiment the sleeve 30 and a frustoconical wall having at its inner periphery one of the frustoconical friction surfaces of the conical clutch.
  • the spring 32 according to the invention would be mounted in a housing delimited by the wall la of this figure 8 and by the sleeve 30 of the figure 2 according to the invention, the spring 32 acting between the housing and the extension 40 of the pinion.
  • the housing 17 has an annular wall 117 of transverse orientation with respect to the axis of axial symmetry of the figure 2 .
  • This wall 117 is centrally perforated for centering the housing on the sleeve 26 shouldered for this purpose
  • the sleeve 26 extends axially projecting relative to the wall 117 so that the trainer can come into contact therewith. edge of the central hole of the wall 117 is supported to come into contact with the shoulder of the sleeve ( figure 2 ).
  • This wall 117 defines two housings extending on either side thereof. One of the housings is dedicated to the spring 32 and the other has the freewheel or the conical clutch.
  • One of the housing, that of the spring 32, can be of the standard type and the other adaptable depending on applications (free wheel or conical clutch).
  • the pinion 12 with its tubular extension 40 may be of sintered material or any other suitable material because the elastic torsion device intervenes between the pinion and the disengageable torque transmission device freewheel or conical clutch .
  • the pinion 12 is made of sintered material attached to a socket to which the extension 40 belongs.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Mechanical Operated Clutches (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valve Device For Special Equipments (AREA)
  • Jellies, Jams, And Syrups (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

The bendix (10) on an electric starter motor is provided with a rotating output shaft (18) and a torsionally-elastic device (28), arranged between the pinion (12) and the automatically-disengaging torque transmission device, such as a conical clutch or freewheel (14), for storage of energy during the compression phases of the thermal engine and for restoration thereof during the decompression phases. The torsionally-elastic device (28) is axially offset with regard to the automatically-disengaging torque transmission device. Said device (28) guarantees adjustment of the play in the transmission elements, whilst reducing the noise level of the bendix during the starting of an internal combustion engine on a motor vehicle.

Description

Domaine technique de l'inventionTechnical field of the invention

L'invention est relative à un démarreur électrique équipé d'un arbre de sortie rotatif et d'un lanceur pour l'entraînement d'une couronne dentée du volant d'un moteur à combustion de véhicule, ledit lanceur comportant :

  • un pignon pouvant coulisser axialement sur l'arbre de sortie rotatif 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 de couple débrayable, tel qu'un dispositif à roue libre ou à embrayage conique.
The invention relates to an electric starter equipped with a rotary output shaft and a launcher for driving a ring gear of the steering wheel of a vehicle combustion engine, said launcher comprising:
  • a pinion axially slidable on the rotary 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 ring,
  • a disengageable torque transmission device, such as a freewheel or conical clutch device.

Etat de la techniqueState of the art

Un démarreur de véhicule automobile comporte d'une manière classique un moteur électrique rotatif destiné à entraîner en rotation un arbre de sortie équipé d'un pignon mobile destiné à coopérer avec une couronne dentée pour assurer le démarrage du moteur à combustion du véhicule.A motor vehicle starter conventionally comprises a rotary electric motor for rotating an output shaft equipped with a movable pinion intended to cooperate with a ring gear to start the combustion engine of the vehicle.

La couronne dentée est appelée couronne de démarrage et est portée à solidarisation par une pièce annulaire, telle qu'un volant moteur, reliée de manière rigide ou élastique au vilebrequin du moteur à combustion interne du véhicule automobile.The ring gear is called the starter ring and is secured by an annular piece, such as a flywheel, rigidly or resiliently connected to the crankshaft of the internal combustion engine of the motor vehicle.

L'arbre de sortie est dans un mode de réalisation confondu avec l'arbre de sortie du moteur électrique du démarreur. En variante l'arbre de sortie est distinct de l'arbre de sortie du moteur électrique du démarreur. Par exemple un train épicycloïdal est agencé entre les deux arbres comme décrit dans le document EP B 0 708 239 ou dans le document FR A 2 751 803 .The output shaft is in one embodiment coincident with the output shaft of the electric motor of the starter. In a variant, the output shaft is distinct from the output shaft of the electric motor of the starter. For example, an epicyclic gear train is arranged between the two shafts as described in the document EP 0 708 239 or in the document FR A 2,751,803 .

Le pignon est généralement monté à coulissement sur l'arbre de sortie entre une position de repos, dans laquelle il est désengagé de la couronne dentée, et une position active de travail dans laquelle il engrène avec ladite couronne, laquelle est liée en rotation au vilebrequin du moteur de véhicule. Un organe de commande, usuellement sous la forme d'un levier d'actionnement, est commandé par un contacteur, et coopère avec un lanceur à roue libre ou à embrayage conique. L'embrayage conique ou la roue libre sont agencés entre le pignon et un entraîneur appartenant au lanceur. Le levier agit sur l'entraîneur ou sur un boîtier que comporte la roue libre ou l'embrayage conique. Dans un démarreur conventionnel le boîtier est solidaire de l'entraîneur.The pinion is generally slidably mounted on the output shaft between a rest position, in which it is disengaged from the ring gear, and an active working position in which it meshes with said ring gear, which is connected in rotation to the crankshaft of the vehicle engine. A control member, usually in the form of an actuating lever, is controlled by a contactor, and cooperates with a freewheeling launcher or conical clutch. The conical clutch or the freewheel are arranged between the pinion and a coach belonging to the launcher. The lever acts on the driver or on a housing that includes the freewheel or the conical clutch. In a conventional starter the housing is integral with the trainer.

Cet entraîneur comporte une douille d'entraînement présentant à sa périphérie interne des cannelures hélicoïdales coopérant de manière complémentaire avec des cannelures hélicoïdales que présente localement l'arbre de sortie à sa périphérie externe. En position active le pignon coopère avec une butée solidaire de l'arbre de sortie.This trainer comprises a drive bushing having at its inner periphery helical grooves cooperating in a complementary manner with helical grooves locally present the output shaft at its outer periphery. In the active position the pinion cooperates with an abutment integral with the output shaft.

Le dispositif de transmission de couple débrayable a pour fonction principale d'éviter que, lorsque le moteur à combustion interne, dit aussi moteur thermique, du véhicule automobile démarre, le pignon entraîne le moteur électrique du démarreur à une vitesse trop importante susceptible de détériorer ce dernier.The main function of the disengageable torque transmission device is to prevent, when the internal combustion engine, also called the engine, of the motor vehicle starts, the pinion drives the electric motor of the starter at a speed that is too great, which may deteriorate this motor. latest.

Pour plus de précisions on se reportera par exemple au document FR A 2 772 433 montrant le levier d'actionnement constituant l'organe de commande associé au lanceur pour déplacer celui-ci.For more details, see for example the document FR A 2,772,433 showing the actuating lever constituting the control member associated with the launcher to move it.

Les documents FR 96 13016 , FR 96 13015 et FR 96 09550 - publiés respectivement sous les numéros FR 2 754 857 , FR 2 754 856 et FR 2 751 803 - se rapportent à des dispositifs d'amortissement visant à absorber les chocs et vibrations engendrés au cours du fonctionnement du démarreur. La fonction d'amortissement se traduit par une diminution de l'intensité des chocs reçus au niveau du lanceur. Ces dispositifs d'amortissement sont généralement constitués par des blocs amortisseurs en élastomère, dont le rôle est d'absorber de l'énergie pour la dissiper sous forme de frottement interne dépendant de la structure du matériau, et de frottement externe entre les pièces en mouvement relatif. Dans les documents FR A 2 754 857 et FR A 2 827 915 les dispositifs d'amortissement se montent dans un boîtier solidaire de l'entraîneur. Dans le document FR A 2 751 803 le dispositif d'amortissement se monte entre l'arbre de sortie et l'élément de sortie du réducteur.The documents FR 96 13016 , FR 96 13015 and FR 96 09550 - published respectively under the numbers FR 2 754 857 , FR 2 754 856 and FR 2 751 803 - refer to damping devices intended to absorb shocks and vibrations generated during starter operation. The damping function results in a decrease in the intensity of the shocks received at the thrower. These damping devices are generally constituted by elastomer damping blocks, whose role is to absorb energy to dissipate it in the form of internal friction depending on the structure of the material, and external friction between the parts in relative motion. In documents FR A 2,754,857 and FR A 2,827,915 the damping devices are mounted in a housing secured to the coach. In the document FR A 2,751,803 the damping device is mounted between the output shaft and the output member of the reducer.

Le document US A 2 159 514 décrit un autre mode de réalisation dans lequel un ressort spiral est lié en rotation à l'une de ses extrémités à l'arbre de sortie du moteur électrique du démarreur et à l'autre de ses extrémités à un élément menant en prise avec le pignon par l'intermédiaire de cames. Dans le document US A 3 616 700 il est décrit encore un autre mode de réalisation faisant intervenir un élément d'amortissement à action axiale.The document US A 2,159,514 discloses another embodiment in which a spiral spring is rotatably connected at one of its ends to the output shaft of the electric starter motor and at the other end thereof to a drive member engaged with the pinion. via cams. In the document US A 3,616,700 another embodiment is described which involves an axially acting damping element.

Sur la figure 1 est représenté, v étant la vitesse et t le temps, le cycle de compression et de décompression dans chacun des cylindres d'un moteur à combustion au cours du démarrage. La courbe Nm(t) indique la vitesse du moteur thermique, et la courbe Nd(t) celle du démarreur.On the figure 1 is represented, v being the speed and t the time, the cycle of compression and decompression in each of the cylinders of a combustion engine during startup. The curve N m (t) indicates the speed of the engine, and the curve N d (t) that of the starter.

Lors de la phase de compression dans un cylindre prédéterminé, le piston comprime le mélange d'air et de carburant, et la pression interne augmente progressivement jusqu'au Point Mort Haut appelé par la suite PMH. Il en résulte une force proportionnelle qui, par l'intermédiaire de la bielle et du vilebrequin, crée un couple résistant qui s'oppose au mouvement de compression. Le démarreur qui entraîne le moteur thermique en rotation doit donc fournir un couple de plus en plus élevé jusqu'au PMH, ce qui se traduit par une décroissance de la vitesse d'entraînement.During the compression phase in a predetermined cylinder, the piston compresses the mixture of air and fuel, and the internal pressure gradually increases to the Top Dead Point subsequently called TDC. This results in a proportional force which, through the connecting rod and the crankshaft, creates a resisting torque which opposes the compression movement. The starter which drives the thermal engine in rotation must therefore provide a higher and higher torque up to the PMH, which results in a decrease in the drive speed.

Après passage du PMH, le cylindre entre en phase de décompression, au cours de laquelle la pression interne crée un couple moteur qui accélère la vitesse de rotation du vilebrequin. Compte tenu des couples et des moments d'inertie respectifs du moteur thermique et du démarreur, l'accélération du vilebrequin est plus rapide que celle du pignon du démarreur. Le pignon se trouve donc entraîné par le moteur thermique, et est entraîné seul en survitesse suite à l'intervention de la roue libre ou de l'embrayage conique entre le pignon et le moteur électrique du démarreur.After passing the PMH, the cylinder enters the decompression phase, during which the internal pressure creates a torque that accelerates the speed of rotation of the crankshaft. Given the respective torques and moments of inertia of the engine and the starter, the acceleration of the crankshaft is faster than that of the starter gear. The pinion is is therefore driven by the heat engine, and is driven alone in overspeed following the intervention of the freewheel or conical clutch between the pinion and the electric motor of the starter.

Le moteur thermique poursuit ensuite son mouvement d'accélération jusqu'au Point Mort Bas, appelé par la suite par PMB. Une phase de compression apparaît dans le cylindre suivant de l'ordre d'allumage, entraînant un ralentissement du vilebrequin. Dans le même temps, le moteur électrique du démarreur, n'ayant plus de charge à transmettre, voit sa vitesse augmenter suivant les lois classiques de montée en régime à vide des moteurs électriques. Lorsque la vitesse du pignon devient égale à celle de l'arbre de sortie du démarreur, la roue libre ou l'embrayage conique se bloque, et le démarreur fourni de nouveau un couple de rotation au moteur thermique. Le couple du cylindre en compression fait ralentir le démarreur qui délivre un couple de plus en plus élevé jusqu'au PMH, et ainsi de suite jusqu'à l'apparition des premières explosions. On note qu'à partir de l'instant t1, la vitesse du moteur à combustion Nm et la vitesse du démarreur Nd sont différentes.The heat engine then continues its acceleration movement until the Low Dead Point, subsequently called PMB. A compression phase appears in the next cylinder of the ignition sequence, resulting in a slowing of the crankshaft. At the same time, the electric motor of the starter, no longer having a load to transmit, sees its speed increase according to the conventional laws of ramping to idle electric motors. When the sprocket speed becomes equal to that of the starter output shaft, the freewheel or conical clutch locks, and the starter again provides a torque to the engine. The compression cylinder torque causes the starter to slow down, delivering a higher and higher torque until TDC, and so on until the first explosions appear. Note that from time t1, the speed of the combustion engine N m and the starter speed N d are different.

Le démarreur est donc tantôt menant, tantôt mené. Au début de chaque période d'entraînement, se produit un rattrapage des jeux angulaires, et du jeu axial entre le pignon et la butée. Ce rattrapage de jeu se traduit par un choc et une émission de bruit. De plus, la charge de l'engrenage pignon/couronne augmente jusqu'au PMH, et ces variations de charge se traduisent également par une émission de bruit. Sur la figure 1, l'intervalle RL correspond à la période de roue libre, et l'intervalle EN correspond à la période d'entraînement.The starter is sometimes leading, sometimes led. At the beginning of each training period, there is a catching of the angular clearances, and axial play between the pinion and the stop. This catch-up game results in a shock and a noise emission. In addition, the load of the pinion / crown gear increases to TDC, and these load variations also result in noise emission. On the figure 1 the interval RL corresponds to the freewheeling period, and the interval EN corresponds to the training period.

Objet de l'inventionObject of the invention

L'objet de l'invention consiste à supprimer le rattrapage de jeu des éléments de transmission pour réduire le bruit du lanceur du démarreur durant la période d'entraînement du moteur thermique.The object of the invention is to eliminate the backlash of play of the transmission elements to reduce the noise of the starter launcher during the drive period of the engine.

Le dispositif selon l'invention est caractérisé en ce que le lanceur est équipé d'un dispositif élastique en torsion agencé pour stocker de l'énergie pendant les phases de compression du moteur thermique, et la restituer pendant les phases de décompression et en ce que le dispositif élastique en torsion est décalé axialement par rapport au dispositif de transmission de couple débrayable.The device according to the invention is characterized in that the launcher is equipped with a torsionally elastic device arranged to store energy during the compression phases of the heat engine, and to restore it during the decompression phases and in that the torsionally elastic device is offset axially relative to the disengageable torque transmission device.

Le rattrapage de jeu est évité, car la présence du dispositif élastique en torsion permet de maintenir en contact les flancs des dents du pignon contre les flancs de la couronne de démarrage. L'énergie est restituée lors des phases de décompression, contrairement aux dispositifs connus de l'art antérieur qui absorbent de l'énergie.Playback is avoided because the presence of the torsionally elastic device makes it possible to keep the flanks of the teeth of the pinion in contact with the flanks of the starter ring. The energy is restored during the decompression phases, unlike the known devices of the prior art that absorb energy.

Plus précisément le dispositif élastique en torsion, dans un premier temps, se comprime durant les phases de compression du moteur thermique du véhicule, puis, dans un deuxième temps, restitue l'énergie accumulée pour donner une accélération angulaire au pignon supérieure à celle du vilebrequin du moteur thermique du véhicule.More specifically, the torsionally elastic device, at first, is compressed during the compression phases of the engine of the vehicle, then, in a second step, restores the accumulated energy to give an angular acceleration to the upper gear to that of the crankshaft. the engine of the vehicle.

Ce dispositif élastique en torsion pour un encombrement radial donné peut avoir une grande taille du fait qu'il est décalé axialement par rapport au dispositif de transmission de couple débrayable.This torsionally elastic device for a given radial space can have a large size because it is offset axially relative to the disengageable torque transmission device.

Cette disposition permet de conserver et de ménager la roue libre ou l'embrayage conique et donc d'augmenter la durée de vie du démarreur tout en réduisant les bruits.This arrangement makes it possible to preserve and protect the freewheel or the conical clutch and thus to increase the life of the starter while reducing the noise.

Le dispositif élastique en torsion comporte avantageusement un ressort spirale accroché spirale entourant coaxialement l'arbre de sortie, en étant accroché entre un boîtier de la roue libre ou de l'embrayage conique et une partie solidaire du pignon ou de l'entraîneur.The torsionally resilient device advantageously comprises a spiral spring spiral wound coaxially surrounding the output shaft, being hooked between a housing of the freewheel or the conical clutch and a portion integral with the pinion or the driver.

Cette disposition permet d'emmagasiner beaucoup d'énergie et autorise un grand débattement angulaire, entre les parties entre lesquelles intervient le ressort spiral. Ce débattement est plus important qu'avec une solution faisant intervenir des éléments élastiquement déformables, par exemple en élastomère. Il est possible d'obtenir des débattements supérieurs à 120°, c'est-à-dire supérieurs au décale angulaire relatif maximum instantané entre le pignon et la couronne dentée.This arrangement allows to store a lot of energy and allows a large angular movement between the parts between which intervenes the spiral spring. This travel is greater than with a solution involving elastically deformable elements, for example elastomer. It is possible to obtain deflections greater than 120 °, that is to say greater than the maximum instantaneous relative angular shift between the pinion and the ring gear.

Selon un mode de réalisation préférentiel, le dispositif élastique en torsion est logé entre le pignon et le dispositif de transmission de couple débrayable, tel qu'un dispositif à roue libre ou à embrayage conique.According to a preferred embodiment, the torsionally resilient device is housed between the pinion and the disengageable torque transmission device, such as a freewheel or conical clutch device.

Ce dispositif élastique en torsion comporte un ressort spirale entourant coaxialement l'arbre de sortie, en étant accroché entre un boîtier de la roue libre ou de l'embrayage conique et un prolongement tubulaire du pignon.This torsionally resilient device comprises a spiral spring coaxially surrounding the output shaft, being hooked between a housing of the freewheel or the conical clutch and a tubular extension of the pinion.

On notera que le dispositif élastique de torsion n'est pas directement en prise avec l'arbre du moteur électrique du démarreur.Note that the elastic torsion device is not directly engaged with the electric motor shaft of the starter.

Ce mode de réalisation préférentiel est simple, fiable et économique car il comporte un nombre minimum de pièces et permet de simplifier le pignon dépourvu de piste pour un dispositif à roue libre ou embrayage conique. L'entraîneur est également simplifié car la piste ou la surface de frottement interne du dispositif de transmission de couple débrayable est avantageusement solidaire de l'entraîneur en sorte que le boîtier associé à ce dispositif de transmission de couple est distinct de l'entraîneur et du pignon et est de fabrication simple.This preferred embodiment is simple, reliable and economical because it comprises a minimum number of parts and simplifies the pinion devoid of track for a freewheel device or conical clutch. The driver is also simplified because the track or the internal friction surface of the disengageable torque transmission device is advantageously secured to the driver so that the housing associated with the torque transmission device is distinct from the driver and the driver. pinion and is of simple manufacture.

Ce mode de réalisation préférentiel permet également de diminuer encore le diamètre interne du ressort spiral, qui ainsi pour un diamètre externe donné peut emmagasiner le maximum d'énergie.This preferred embodiment also makes it possible to further reduce the internal diameter of the spiral spring, which thus for a given external diameter can store the maximum energy.

En outre on obtient des temps de réponse plus rapides que dans un mode de réalisation à montage du dispositif élastique en torsion à l'arrière du dispositif de transmission de couple débrayable agencé alors entre le pignon et le dispositif de torsion. En effet on réduit les inerties en logeant le dispositif élastique de torsion entre le pignon et le dispositif de transmission de couple débrayable du lanceur.In addition, faster response times are achieved than in an embodiment of mounting the torsionally resilient device at the rear of the disengageable torque transmission device then arranged between the pinion and the torsion device. In fact the inertia is reduced by housing the elastic torsion device between the pinion and the disengageable torque transmission device launcher.

De plus cela permet aisément d'équiper le lanceur d'un dispositif de transmission de couple débrayable à roue libre ou à embrayage conique.In addition, it makes it easy to equip the launcher with a disengageable torque transmission device with freewheel or conical clutch.

Selon une caractéristique de l'invention, le ressort spiral est emprisonné de manière simple, fiable et économique dans un compartiment du boîtier au moyen d'un disque de fermeture solidaire du pignon.According to a characteristic of the invention, the spiral spring is imprisoned simply, reliably and economically in a compartment of the housing by means of a closing disc secured to the pinion.

D'autres caractéristiques peuvent être utilisées seules ou en combinaison :

  • le disque de fermeture comporte au moins un secteur protubérant logé dans une découpe du boîtier, laquelle possède une largeur angulaire supérieure à l'angle du secteur pour que le débattement angulaire du disque par rapport au boîtier corresponde à la différence entre les deux angles ;
  • le ressort est précontraint de manière à exercer un couple de rappel tendant à ramener le secteur du disque contre une butée du boîtier pour obtenir un positionnement angulaire prédéterminé du pignon par rapport au boîtier lorsque le démarreur est à l'état de repos ;
  • le boîtier est doté d'un deuxième compartiment de logement des galets de la roue libre ou des surface tronconiques de l'embrayage conique ;
  • le boîtier est centré et guidé sur l'arbre de sortie par l'intermédiaire d'une bague autolubrifiante pour autoriser les mouvements rotatifs de translation et de rotation du lanceur.
Other features can be used alone or in combination:
  • the closure disk comprises at least one protruding sector housed in a housing cutout, which has an angular width greater than the sector angle so that the angular displacement of the disk relative to the housing corresponds to the difference between the two angles;
  • the spring is prestressed so as to exert a return torque tending to bring the sector of the disc against a stop of the housing to obtain a predetermined angular positioning of the pinion relative to the housing when the starter is in the idle state;
  • the housing is provided with a second housing compartment of the freewheel rollers or frustoconical surfaces of the conical clutch;
  • the housing is centered and guided on the output shaft by means of a self-lubricating ring to allow rotary movements of translation and rotation of the launcher.

Description sommaire des dessinsBrief description of the drawings

D'autres avantages et caractéristiques ressortiront plus clairement de la description qui va suivre d'un mode de réalisation de l'invention donné à titre d'exemple non limitatif, et représenté aux dessins annexés, dans lesquels :

  • la figure 1 représente le cycle de compression et de décompression dans un cylindre de moteur à combustion au cours du démarrage ;
  • la figure 2 est une demi-vue en coupe d'un lanceur de démarreur selon l'invention ;
  • la figure 3 montre une vue en coupe du boîtier du lanceur de la figure 2 ;
  • la figure 4 est une vue de profil de la figure 3 ;
  • la figure 5 est une vue en coupe selon la ligne 5-5 de la figure 3 ;
  • la figure 6 montre une vue en perspective du ressort spirale constituant le dispositif élastique en torsion ;
  • la figure 7 représente une vue en élévation du disque de fermeture du boîtier du lanceur ;
  • la figure 8 montre une vue en coupe de l'ensemble pignon et disque de fermeture ;
  • la figure 9 illustre le couple engendré par le ressort spirale en fonction de la position relative du pignon par rapport au boîtier.
Other advantages and features will emerge more clearly from the following description of an embodiment of the invention given by way of non-limiting example, and represented in the accompanying drawings, in which:
  • the figure 1 represents the compression and decompression cycle in a combustion engine cylinder during start-up;
  • the figure 2 is a half-sectional view of a starter launcher according to the invention;
  • the figure 3 shows a sectional view of the launcher casing of the figure 2 ;
  • the figure 4 is a profile view of the figure 3 ;
  • the figure 5 is a sectional view along line 5-5 of the figure 3 ;
  • the figure 6 shows a perspective view of the spiral spring constituting the elastic torsion device;
  • the figure 7 is an elevational view of the closure disc of the caster of the launcher;
  • the figure 8 shows a sectional view of the pinion and closure disk assembly;
  • the figure 9 illustrates the torque generated by the spiral spring as a function of the relative position of the pinion relative to the housing.

Description d'un mode de réalisation préférentiel.Description of a Preferred Embodiment

En référence aux figures 2 à 8, le lanceur 10 comporte un pignon 12 et un dispositif de transmission de couple débrayable ici à roue libre 14, lequel est composée d'un entraîneur 16 et d'un boîtier 17, ici de forme annulaire, délimitant ici un logement pour des galets 19.With reference to Figures 2 to 8 , the launcher 10 comprises a pinion 12 and a torque-free disengageable torque transmission device 14, which is composed of a driver 16 and a housing 17, here of annular shape, delimiting here a housing for rollers 19 .

L'entraîneur 16 est équipé, de manière précitée, de cannelures 16a hélicoïdales coopérant avec des cannelures 16b complémentaires de l'arbre de sortie 18 destiné à être entraîné en rotation par le moteur électrique du démarreur.The trainer 16 is equipped, as mentioned above, with helical splines 16a cooperating with complementary splines 16b of the output shaft 18 intended to be rotated by the electric motor of the starter.

Cet arbre 18 est dans une forme de réalisation d'un seul tenant avec l'arbre de sortie du moteur électrique ou en variante distinct de l'arbre de sortie du moteur électrique ; un réducteur à train épicycloïdal intervenant par exemple alors entre les deux arbres.This shaft 18 is in an integral embodiment with the output shaft of the electric motor or alternatively separate from the output shaft of the electric motor; an epicyclic gear train then intervening for example between the two shafts.

La structure des cannelures 16a, 16b permet la liaison en rotation et le déplacement axial du lanceur 10. Un alésage 20 est ménagé dans l'entraîneur 16 pour assurer le centrage de la piste cylindrique 22 de la roue libre 14 sur l'arbre 18. Les cannelures 16a appartiennent à une douille d'entraînement (non référencée) prolongeant axialement vers l'arrière, en direction opposée au pignon 12, la piste 22 formée à la faveur d'une protubérance que présente l'entraîneur localement à sa périphérie externe .The structure of the splines 16a, 16b allows the connection in rotation and the axial displacement of the launcher 10. A bore 20 is formed in the driver 16 to ensure the centering of the track cylindrical 22 of the freewheel 14 on the shaft 18. The grooves 16a belong to a drive sleeve (not referenced) extending axially rearward, in the opposite direction to the pinion 12, the track 22 formed in favor of a protrusion that presents the coach locally at its outer periphery.

Le boîtier 17 possède est creusé à sa périphérie externe pour formation de rampes 24 inclinées, constituant des cames, provoquant d'une manière connue, le coincement des galets 19 dans un sens de rotation de l'arbre 18, et le déblocage des galets 19 en sens inverse. Ce boîtier est centré et guidé sur l'arbre 18 par l'intermédiaire d'une bague autolubrifiante 26 permettant les mouvements relatifs de translation et de rotation. Le boîtier 17 comporte également des logements épaulés pour des ressorts de pression agissant de manière connue sur les galets 19 pour coincer ceux-ci entre la piste 22 et les rampes 24. Pour plus de précisions on se reportera par exemple à la page 323 (figure 6. 13) du document " Electrische Systeme im Kraftfahrzeug" de 1995 (Vogel Fachbuch XP 002220045 ).The housing 17 is hollowed out at its outer periphery for forming ramps 24 inclined, constituting cams, causing in a known manner, the jamming of the rollers 19 in a direction of rotation of the shaft 18, and the release of the rollers 19 reverse. This housing is centered and guided on the shaft 18 by means of a self-lubricating ring 26 allowing the relative movements of translation and rotation. The housing 17 also comprises shoulders for pressure springs acting in known manner on the rollers 19 to wedge them between the track 22 and the ramps 24. For more details, see for example on page 323 ( figure 6 . 13) of the document Electrische Systeme im Kraftfahrzeug "from 1995 (Vogel Fachbuch XP 002220045 ).

Un dispositif élastique en torsion 28 est, selon l'invention, monté au sein du lanceur de manière décalé axialement par rapport au dispositif de transmission de couple débrayable. Ce dispositif stocke l'énergie pendant les phases de compression du moteur thermique du véhicule automobile et restitue cette énergie pendant les phases de décompression de ce moteur thermique.A torsionally elastic device 28 is, according to the invention, mounted within the launcher axially offset with respect to the disengageable torque transmission device. This device stores the energy during the compression phases of the engine of the motor vehicle and restores this energy during the decompression phases of the engine.

Avantageusement ce dispositif 28 consiste en un ressort spirale accroché entre le boîtier 17 et une partie appartenant au pignon ou à l'entraîneur. Ce ressort est logé dans un compartiment du boîtier 17.Advantageously, this device 28 consists of a spiral spring hooked between the housing 17 and a part belonging to the pinion or to the driver. This spring is housed in a housing compartment 17.

Ce dispositif 28 est dans un mode de réalisation disposé entre le boîtier 17 et l'entraîneur 16.This device 28 is in one embodiment disposed between the housing 17 and the driver 16.

Ce dispositif est disposé dans l'exemple de réalisation représenté entre le pignon 12 et la roue libre 14. Le boîtier 17 se prolonge sur le côté gauche par une douille tubulaire 30, délimitant un compartiment 31 de réception d'un ressort spirale 32 constituant ledit dispositif élastique en torsion 28.This device is arranged in the exemplary embodiment shown between the pinion 12 and the freewheel 14. The housing 17 extends on the left side by a tubular sleeve 30, delimiting a compartment 31 for receiving a spiral spring 32 constituting said elastic torsion device 28.

Le ressort spirale 32 est doté d'un évidement 34 sur l'extrémité de sa spire extérieure permettant à celle-ci de faire une liaison en rotation avec une languette 36 de forme complémentaire disposée dans la douille 30 du boîtier 17. L'arrêt en rotation doit être au moins unidirectionnel dans le sens de compression du ressort 32. Dans l'exemple présenté aux figures 3 à 6, l'évidement 34 présente une section rectangulaire dans laquelle se place l'extrémité de la languette 36 de la douille 30. Il est clair que les parties mâle et femelle de la liaison peuvent être inversées.The spiral spring 32 is provided with a recess 34 on the end of its outer turn allowing it to make a connection in rotation with a tab of complementary shape disposed in the sleeve 30 of the housing 17. The stop rotation must be at least unidirectional in the compression direction of the spring 32. In the example presented to Figures 3 to 6 , the recess 34 has a rectangular section in which is placed the end of the tongue 36 of the sleeve 30. It is clear that the male and female parts of the connection can be reversed.

D'autres systèmes de fixation peuvent être envisagés pour l'assemblage du ressort 32 au boîtier 17, notamment par rivetage, soudage, ou utilisation d'une pièce intermédiaire d'accrochage.Other fastening systems may be envisaged for assembling the spring 32 to the casing 17, in particular by riveting, welding, or using an intermediate fastening piece.

L'autre extrémité sur la spire intérieure est pourvue d'un ergot 38 permettant un accrochage au moins dans le sens de rotation nécessaire à la compression du ressort spirale 32.The other end on the inner turn is provided with a lug 38 allowing attachment at least in the direction of rotation necessary for the compression of the spiral spring 32.

L'ergot 38 est formé par un pliage radial vers l'intérieur du ruban constitutif du ressort 32. Cette extrémité coudée se loge dans une lumière 33 aménagée dans le prolongement tubulaire 40 du pignon 12.The lug 38 is formed by a radially inward folding of the ribbon constituting the spring 32. This bent end is housed in a slot 33 formed in the tubular extension 40 of the pinion 12.

Un disque 42 de fermeture s'étend entre la douille 30 et le prolongement 40 pour emprisonner le ressort spiral 32 dans le compartiment 31. Le disque 42 est fixé sur le pignon 12 par soudage, rivetage ou tout autre moyen de fixation connu.A closure disc 42 extends between the bushing 30 and the extension 40 to trap the spiral spring 32 in the compartment 31. The disc 42 is fixed to the pinion 12 by welding, riveting or any other known fastening means.

Sur les figures 3, 4, 7 et 8, la partie extérieure du disque 42, d'une épaisseur e1, possède un diamètre D1 sensiblement égal au diamètre extérieur D2 de la douille tubulaire 30. Deux évidements circulaires 44 ramènent localement le diamètre extérieur à une valeur D3 inférieure au diamètre intérieur D4 de la douille 30 (figure 3), de manière à former deux secteurs 46 protubérants d'angle A et diamétralement opposés. Chaque secteur est délimité par deux faces 54 et 50 ici radiales (figure 7).On the Figures 3, 4 , 7 and 8 , the outer part of the disk 42, of a thickness e1, has a diameter D1 substantially equal to the outside diameter D2 of the tubular bushing 30. Two circular recesses 44 locally bring the outside diameter to a value D3 less than the inside diameter D4 of the bushing 30 ( figure 3 ), so as to form two protruding sectors 46 of angle A and diametrically opposed. Each sector is delimited by two faces 54 and 50 here radial ( figure 7 ).

L'extrémité de la douille 30 comporte des découpes 48 destinées à recevoir les secteurs 46 du disque 42. Chaque découpe 48 est délimitée par deux faces 52 et 56, ici radiales, de la douille 30 et présente une profondeur e2 légèrement supérieure à l'épaisseur e1 du disque 42, et une largeur angulaire B > A. Le disque 42 peut donc avoir un débattement angulaire d= B-A par rapport au boîtier 17. Les faces 50 et 54 d'un secteur 46 sont destinées à venir en contact respectivement avec les faces 52 et 56 de la douille 30 du boîtier 17.The end of the sleeve 30 has cutouts 48 intended to receive the sectors 46 of the disc 42. Each cutout 48 is delimited by two faces 52 and 56, here radial, of the bushing 30 and has a depth e2 slightly greater than the thickness e1 of the disc 42, and an angular width B> A. The disc 42 can therefore have an angular displacement d = BA relative to the housing 17. The faces 50 and 54 of a sector 46 are intended to come into contact respectively with the faces 52 and 56 of the bushing 30 of the housing 17.

Le ressort 32 qui est précontraint, exerce un couple Co tendant à ramener la face 50 du disque 42 contre la face 52 du boîtier 17, de manière à positionner angulairement le pignon 12 par rapport au boîtier 17 lorsque le démarreur est au repos.The spring 32 which is prestressed, exerts a torque C o tending to bring the face 50 of the disk 42 against the face 52 of the housing 17, so as to angularly position the pinion 12 relative to the housing 17 when the starter is at rest.

Un capot 55 (figure 2) est constitué d'un tube en matière déformable, comportant deux extrémités rabattues qui ferment le boîtier 17 en emprisonnant tous les constituants du lanceur 10. Le capot est en contact par sa périphérie interne avec la périphérie externe cylindrique du boîtier 17 comprenant la périphérie externe de la douille 30. Ce capot 55 a une extrémité rabattue qui sert de maintien à un disque 142 fermant le dispositif à roue libre 14 et servant d'appui à l'organe de commande, tel qu'un levier, précité.A hood 55 ( figure 2 ) consists of a tube of deformable material, comprising two folded ends which close the housing 17 by trapping all the components of the launcher 10. The cover is in contact by its inner periphery with the cylindrical outer periphery of the housing 17 comprising the outer periphery of the sleeve 30. This cover 55 has a folded end which serves to hold a disk 142 closing the freewheel device 14 and serving as a support for the control member, such as a lever, mentioned above.

La figure 9 illustre le couple engendré par le ressort spirale 32 en fonction de la position PA relative du pignon 12 par rapport au boîtier 17. Dès que le couple C exercé par le démarreur dépasse la valeur Cm, le ressort 32 commence à se comprimer, et le pignon 12 tourne par rapport au boîtier 17 avec un angle croissant. Si le couple maximal au passage de compression atteint la valeur CM, le pignon 12 fait un déplacement Amax par rapport au boîtier 17.The figure 9 illustrates the torque generated by the spiral spring 32 as a function of the relative position PA of the pinion 12 relative to the housing 17. As soon as the torque C exerted by the starter exceeds the value C m , the spring 32 begins to compress, and the pinion 12 rotates relative to the housing 17 with an increasing angle. If the maximum torque at the compression passage reaches the value C M , the pinion 12 makes a displacement A max relative to the housing 17.

Lors de la décompression, le ressort 32 restitue de l'énergie en accélérant la vitesse du pignon 12, lequel a une très faible inertie par rapport au moteur électrique du démarreur. Au début de la compression suivante, le ressort 32 s'est détendu jusqu'à l'angle Am correspondant à un couple Cm fourni par le ressort. L'énergie fournie au pignon 12 est représentée schématiquement par l'aire du trapèze PQRS.During decompression, the spring 32 restores energy by accelerating the speed of the pinion 12, which has a very low inertia compared to the electric motor of the starter. At the beginning of the next compression, the spring 32 has expanded to the angle A m corresponding to a torque C m provided by the spring. The energy supplied to the pinion 12 is schematically represented by the area of the trapezium PQRS.

Il en résulte un contact permanent du pignon 12 contre la couronne dentée du moteur à combustion. Pour éviter tout choc contre la face d'appui 50 du disque 42, il faut que Am soit supérieur à 0 en fin de chaque décompression.This results in permanent contact of the pinion 12 against the ring gear of the combustion engine. To avoid any shock against the bearing surface 50 of the disk 42, A m must be greater than 0 at the end of each decompression.

Pour les conditions normales de fonctionnement du démarreur, il faut que d soit supérieur à Am afin de ne pas avoir de choc important de la face 54 contre la face 56 du boîtier 17.For the normal operating conditions of the starter, d must be greater than A m in order not to have a significant impact of the face 54 against the face 56 of the housing 17.

En fin de démarrage, le ressort 32 revient à sa position de repos ramenant la face 50 du disque 42 contre le boîtier 17. Un élément élastique peut être interposé entre les deux faces d'appui pour réduire le bruit de fin de démarrage. Dès le retour au repos du ressort 32, la roue libre 14 entre en action pour permettre le différentiel de vitesse entre le pignon 12 entraîné par le moteur thermique et l'arbre 18 du démarreur.At the end of starting, the spring 32 returns to its rest position bringing the face 50 of the disk 42 against the housing 17. An elastic element can be interposed between the two bearing faces to reduce the end-of-start noise. Upon return to rest of the spring 32, the freewheel 14 comes into action to allow the speed differential between the pinion 12 driven by the engine and the shaft 18 of the starter.

Bien entendu la présente invention n'est pas limitée à l'exemple de réalisation décrit. Ainsi la piste 22 et les rampes 24 sont en variante de forme tronconique pour former un embrayage conique à surface de frottement tronconiques comme décrit par exemple dans les documents FR A 2 772 433 ou FR A 2 827 915 . Dans ce cas les galets sont supprimés ainsi que les ressorts de pression associés aux galets et l'entraîneur peut être en matière plastique. Cet entraîneur a alors avantageusement la forme de celui de la figure 3 du document FR A 2 827 915 , l'organe de commande du lanceur étant alors associé à l'entraîneur. Les surfaces de frottement tronconiques complémentaires peuvent être rapportées.Of course, the present invention is not limited to the embodiment described. Thus, the track 22 and the ramps 24 are alternatively frustoconical in shape to form a conical clutch with frustoconical friction surface as described for example in the documents FR A 2,772,433 or FR A 2,827,915 . In this case the rollers are removed and the pressure springs associated with the rollers and the driver may be plastic. This coach then has the advantage of the shape of figure 3 of the document FR A 2,827,915 the launcher control member is then associated with the trainer. Complementary frustoconical friction surfaces can be reported.

Il ressort de ce qui précède que la périphérie externe du boîtier 17 comporte à sa périphérie externe dans un mode de réalisation la douille 30 et une paroi de forme tronconique portant à sa périphérie interne une des surfaces de frottement tronconique de l'embrayage conique. Par exemple en considérant la figure 8 du document FR A 2 827 915 , on voit alors que le ressort 32 selon l'invention serait monté dans un logement délimité par la paroi la de cette figure 8 et par la douille 30 de la figure 2 selon l'invention, le ressort 32 agissant entre le boîtier et le prolongement 40 du pignon.It follows from the foregoing that the outer periphery of the housing 17 has at its outer periphery in one embodiment the sleeve 30 and a frustoconical wall having at its inner periphery one of the frustoconical friction surfaces of the conical clutch. For example, considering the figure 8 of the document FR A 2,827,915 , it is then seen that the spring 32 according to the invention would be mounted in a housing delimited by the wall la of this figure 8 and by the sleeve 30 of the figure 2 according to the invention, the spring 32 acting between the housing and the extension 40 of the pinion.

Ainsi qu'il ressort de la description et des dessins le boîtier 17 présente une paroi annulaire 117 d'orientation transversale par rapport à l'axe de symétrie axial de la figure 2. Cette paroi 117 est trouée centralement pour centrage du boîtier sur la douille 26 épaulée à cet effet La douille 26 s'étend en saillie axiale par rapport à la paroi 117 en sorte que l'entraîneur peut venir en contact avec celle-ci.. Le bord du trou central de la paroi 117 est épaulé pour venir en contact avec l'épaulement de la douille (figure 2). Cette paroi 117 délimite deux logements s'étendant de part et d'autre de celle-ci. L'un des logements est dédié au ressort 32 et l'autre a la roue libre ou à l'embrayage conique.As can be seen from the description and the drawings, the housing 17 has an annular wall 117 of transverse orientation with respect to the axis of axial symmetry of the figure 2 . This wall 117 is centrally perforated for centering the housing on the sleeve 26 shouldered for this purpose The sleeve 26 extends axially projecting relative to the wall 117 so that the trainer can come into contact therewith. edge of the central hole of the wall 117 is supported to come into contact with the shoulder of the sleeve ( figure 2 ). This wall 117 defines two housings extending on either side thereof. One of the housings is dedicated to the spring 32 and the other has the freewheel or the conical clutch.

L'un des logements, celui du ressort 32, peut être donc du type standard et l'autre adaptable en fonction des applications (roue libre ou embrayage conique).One of the housing, that of the spring 32, can be of the standard type and the other adaptable depending on applications (free wheel or conical clutch).

On appréciera que l'entraîneur 16 et le pignon 12 de la figure 2 ont une forme simple du fait que la paroi 117 est distincte de l'entraîneur et du pignon.It will be appreciated that the coach 16 and the pinion 12 of the figure 2 have a simple shape because the wall 117 is separate from the driver and the pinion.

Dans tous les cas le pignon 12 avec son prolongement tubulaire 40 peut être en matériau fritté ou en tout autre matière appropriée du fait que le dispositif élastique de torsion intervient entre le pignon et le dispositif de transmission de couple débrayable à roue libre ou à embrayage conique.In all cases the pinion 12 with its tubular extension 40 may be of sintered material or any other suitable material because the elastic torsion device intervenes between the pinion and the disengageable torque transmission device freewheel or conical clutch .

Bien entendu en variante le pignon 12 est en matériau fritté rapporté sur une douille à laquelle appartient le prolongement 40.Of course, in a variant, the pinion 12 is made of sintered material attached to a socket to which the extension 40 belongs.

Claims (10)

  1. Electric starter equipped with an output shaft (18) and a launcher (10) to drive a toothed ring of the flywheel of a thermal engine of a vehicle, the said launcher comprising:
    - a pinion (12) which can slide axially on the rotary output shaft (18), between a position of rest in which it is disengaged from the ring, and an active position of work in which it engages with the said ring;
    - a free wheel (14) transmission device which is associated with a control unit,
    characterised in that the launcher (10) is equipped with a resilient torsion device (28) which is designed to store energy during the compression stages of the thermal engine, and to return it during the decompression stages of the thermal engine, and in that the resilient torsion device (28) is disposed between the pinion (12) and the free wheel (14), and comprises a spiral spring (32) which surrounds the output shaft (18) coaxially.
  2. Electric starter according to claim 1, characterised in that the spiral spring (32) is accommodated between the pinion (12) and the free wheel (14) in a first annular compartment (31) of a case (17).
  3. Electric starter according to claim 2, characterised in that the spiral spring (32) is fastened between the case (17) and a tubular extension (40) of the pinion (12), whilst surrounding the output shaft (18) coaxially.
  4. Electric starter according to claim 3, characterised in that the spiral spring (32) is trapped in the first compartment (31) of the case (17) by means of a closure disc (42) which is integral with the pinion (12).
  5. Electric starter according to claim 4, characterised in that the closure disc (42) comprises at least one protruding segment (46) with a predetermined angle (A), which is accommodated in a cut-out (48) in the case (17), the said cut-out having an angular width (B) which is greater than the angle (A), such that the angular clearance of the disc (42) relative to the case (17) corresponds to the difference between the said angles (A and B).
  6. Electric starter according to claim 5, characterised in that the spring (32) is prestressed, such as to exert a return moment which tends to bring the segment (46) of the disc (42) back against a stop of the case (17), in order to obtain a predetermined angular positioning of the pinion (12) relative to the case (17), when the starter is in the rest state.
  7. Electric starter according to one of the preceding claims, characterised in that the case (17) is provided with a second compartment to accommodate rollers (19) of the free wheel.
  8. Electric starter according to claim 7, taken in combination with claim 6, characterised in that the first compartment (31) is delimited by a tubular sleeve (30) which extends the case (17) in the direction of the pinion (12), and in that the cut-out (48) and the stop are provided in the tubular sleeve (30).
  9. Electric starter according to claim 8, taken in combination with claim 3, characterised in that the outer turn of the spiral spring (32) is provided with a recess (34) in which a tongue (36) of the tubular sleeve (30) is placed, in order to act as a stop in rotation, at least in the direction of compression of the spiral spring (32), and in that the inner turn of the spiral spring (32) has a lug (38) which is accommodated in an aperture (33) in the tubular extension (40) of the pinion (12), for fastening at least in the direction necessary for the compression of the spiral spring (32).
  10. Electric starter according to claim 8 or claim 9, characterised in that the case (17) is centred and guided on the output shaft (18) by means of a self-lubricating ring (26), in order to permit the rotary movements of translation and rotation of the launcher (10).
EP03722671A 2002-02-28 2003-02-25 Starter, particularly for a motor vehicle, provided with a torque-accumulating bendix gear Expired - Lifetime EP1478844B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0202535 2002-02-28
FR0202535A FR2837532B1 (en) 2002-02-28 2002-02-28 STARTER EQUIPPED WITH A TORQUE ACCUMULATOR LAUNCHER
PCT/FR2003/000602 WO2003072935A1 (en) 2002-02-28 2003-02-25 Starter, particularly for a motor vehicle, provided with a torque-accumulating bendix gear

Publications (2)

Publication Number Publication Date
EP1478844A1 EP1478844A1 (en) 2004-11-24
EP1478844B1 true EP1478844B1 (en) 2008-04-23

Family

ID=27763526

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03722671A Expired - Lifetime EP1478844B1 (en) 2002-02-28 2003-02-25 Starter, particularly for a motor vehicle, provided with a torque-accumulating bendix gear

Country Status (6)

Country Link
EP (1) EP1478844B1 (en)
KR (1) KR20040091077A (en)
AT (1) ATE393311T1 (en)
DE (1) DE60320536T2 (en)
FR (1) FR2837532B1 (en)
WO (1) WO2003072935A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4003633B2 (en) * 2002-12-13 2007-11-07 株式会社デンソー Engine starter
DE102008054965B4 (en) * 2008-12-19 2018-08-23 Seg Automotive Germany Gmbh Method and device for start-stop systems of internal combustion engines in motor vehicles
DE102009045248A1 (en) * 2009-10-01 2011-04-07 Robert Bosch Gmbh Noise-optimized starting device
JP6379603B2 (en) 2014-04-04 2018-08-29 株式会社デンソー Engine starter
DE102015214373A1 (en) * 2015-07-29 2017-02-02 Bayerische Motoren Werke Ag Starter with starter clutch

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2159514A (en) * 1936-04-07 1939-05-23 Arthur H Abell Starter for engines
US3616700A (en) * 1969-10-31 1971-11-02 Bendix Corp Roll clutch starter drive with shock absorber
FR2751803B1 (en) 1996-07-26 2003-06-13 Valeo Equip Electr Moteur STARTER OF A MOTOR VEHICLE WITH REDUCER COMPRISING A DAMPING DEVICE
FR2754857B1 (en) 1996-10-23 1998-11-27 Valeo Equip Electr Moteur MOTOR VEHICLE STARTER COMPRISING A GEAR WITHOUT FREE WHEEL
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
FR2772433B1 (en) 1997-12-17 2000-02-04 Valeo Equip Electr Moteur MOTOR VEHICLE STARTER COMPRISING AN IMPROVED LAUNCHER

Also Published As

Publication number Publication date
DE60320536D1 (en) 2008-06-05
DE60320536T2 (en) 2009-03-26
ATE393311T1 (en) 2008-05-15
EP1478844A1 (en) 2004-11-24
WO2003072935A1 (en) 2003-09-04
FR2837532B1 (en) 2005-12-02
FR2837532A1 (en) 2003-09-26
KR20040091077A (en) 2004-10-27

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