EP1404968B1 - Starter for a motor vehicle - Google Patents

Abstract

The starter for a motor vehicle comprises a starter head provided with a driver (12) and a pinion (1), an electric motor (M) provided with a shaft (101) able to drive a starter-head shaft (100), an electromagnetic contactor (2) extending parallel to the electric motor (M) above it and comprising a movable core (2d), a fork (13) mounted with articulation at its top end on the movable core (2b); the driver (12) comprises a groove for receiving the bottom end of the fork (13) delimited by two flanks (121, 122) whilst the starter head is locked in rotation by means of cooperation between the fork (13) and the driver (12) for its passage from its idle position to its position of meshing with the starting ring.

Description

Field of the invention

The present invention relates to starters for motor vehicles.

State of the art

Such a starter is shown in FIG. 1 and comprises an electric motor M mounted inside a first metal yoke, an electromagnetic contactor 2 extending parallel to the electric motor M and comprising a winding 2a mounted inside the first metal yoke. a second metal head.
The two yokes are fixed, here using tie rods, on a support 4 with the interposition here of a support plate 28 of an epicyclic gear box. The support 4 is an aluminum-based casting, which is intended to be fixed to the casing of the internal combustion engine of the motor vehicle, hereinafter referred to as the heat engine. The support 4 ensures the return to earth and has a front end shaped warhead open locally for the passage of the starter ring C of the engine of the vehicle. This warhead is connected to a fastening and centering area respectively of the electric motor M, the switch 2 and the support 4 on the housing of the engine.
The warhead has at the front (left part of the figure) a support sleeve of a bearing inside which is rotatably mounted the front end of a launcher shaft 100 locally having at its outer periphery splines adapted to engage complementary splines formed at the inner periphery of a driver 12 belonging to a launcher 102 also having a pinion 1 connected by a coupling device 14, here freewheeling, to the trainer.
The shaft 100 is coaxial with the shaft 101 of the electric motor M belonging to the armature of this motor with the interposition here of a gear reducer epicyclic train between the two shafts.
The support plate 28 above carries a plastic part in the form of ring gear internally and belonging to the aforesaid gear reducer, the input gear is secured to the front end of the electric motor shaft.
The planet carrier of the gearbox is secured to the rear end of the shaft 100.

The rear end of the shaft 101 is rotatably mounted within a bearing carried by a part, said rear bearing, closing the first yoke. This first yoke internally carries an inductor, here with magnets, surrounding, with the presence of an air gap, the armature of the electric motor comprising a rotor in the form of a packet of sheets fixed on the shaft of the electric motor knurled at this effect.
This bundle of plates is provided with axial grooves for accommodating electrically conductive elements in the form of bars arranged in networks connected to the electrically conductive blades of a collector carried by the rear end of the shaft 101.
Brushes, mounted inside cages carried by the rear bearing, are intended to cooperate with the collector blades, here of the frontal type.
A series of these brushes is connected to ground via the first yoke and the support 4. A second series of these brushes is connected to a connector for receiving a cable connecting the connector to a first contact terminal of the contactor 2 secured to a cover of electrically insulating material closing the open rear end of the second yoke having at its front end a perforated bottom for the passage of an internally hollow movable core 2b. The cover also carries a second contact terminal and at least one connection for the power supply of the winding 2a.
A fixed core 2d is implanted to attach to the rear end of the second yoke and penetrates partly inside a support 2c of the winding 2a. The support 2c has a U-shaped section and therefore constitutes a pad for guiding the core 2b. A first stepped rod passes through the fixed core 2d and carries a contact plate intended to bear on the two aforementioned contact terminals having contact pads for this purpose.
The second terminal is connected to the positive terminal of the battery. The winding 2a is connected to this positive terminal of the battery via a start switch operated by the ignition key or any other device. This winding 2a is connected to ground via the second yoke and the support 4.
The first rod and the contact plate belong to a movable contact 3 which, in its rest position, is kept pressed by a cut-off spring 19 against the fixed core. The cutoff spring acts between the contact pad and the cover having a receiving housing of the breaking spring.
Another spring, said contact spring 21, of greater stiffness than that of the breaking spring, is implanted axially between the other face of the contact plate and a shoulder of the rod, passing through the fixed core 2d to present an end. .

The movable core 2b penetrates inside the second yoke and in the winding 2a. This movable core 2b extends in axial projection with respect to the front end, and the second cylinder head. The movable core 2b is subjected to the action of a return spring 18 acting between the bottom of the second yoke and a shoulder secured to the movable core centrally provided with a blind hole for the axial sliding assembly of a second rod. shoulder at its rear end for action of a spring, said spring teeth against teeth 5, acting between said shoulder and the bottom of the movable core. The spring teeth against teeth has a stiffness stronger than that of the return spring 18 and lower than that of the springs associated with the movable contact 3.
The front end of the second rod carries an axis for the hinge assembly of the upper end of an operating lever 13 of the pinion launcher 102. This lever 13 is mounted at an intermediate point 11 pivoting carried by a integral protuberance of the support plate 28 called base plate. This intermediate point 11 comprises an axial clearance called JC break set that allows to electrically disconnect the electric motor starter in the case where the pinion 1 remains entangled in the crown C starter. For starter models without a base plate, this intermediate point 11 may be carried for example by the support 4 of the starter. The lower end of the operating lever comprises two arms or branches mounted in an annular groove formed in the driver 12 so that the operating lever is fork-shaped.
More precisely, the groove of the driver is delimited by an annular bottom of axial orientation and by two annular flanks of transverse orientation perpendicular to the shaft 100.
The axial distance between the two sides depends on the thickness of the arms, usually called fingers, of the fork so that they can enter at least mounting clearance in the groove to move axially the driver when the contactor is electrically powered.

As shown in Figure 1, the switch 2, the electric motor M and the launcher are in their rest position. In this position the winding 2a and the electric motor M are not electrically powered; the aforementioned starter switch being open. The pinion 1 is at axial distance from the start ring C of the heat engine, the movable contact 3 is at a distance from the contact terminals in the form of studs, while the core 2b is at axial distance from the rod of the movable contact.
When the switch is closed by means of the ignition key, the winding 2a is electrically powered and a magnetic field is created so that the mobile core 2b moves axially toward the fixed core 2d and the movable contact and moves, by means of the operating fork, the launcher and the pinion 1 towards the ring gear C. The pinion 1 can penetrate between the teeth of the ring gear C so that it is in the meshing position with the C. The movement of the pinion 1 is limited by the cooperation of the pinion 1 with a stop 6 secured to the shaft 100. The movement of the movable core continues, it abuts against the rod of the moving contact through a washer that carries in the rear the movable core 2b for this purpose. The cutoff spring is then compressed until closing of the movable contact by contacting its plate with the contact terminals.
The electrical circuit of the electric motor M is then closed so that it rotates the shaft 100 and thus the pinion 1 via the driver and the helical splines intervening between the driver and the shaft 100. The magnetic circuit closes completely after the electrical circuit, the movable core 2b coming into contact with the fixed core 2d after compression of the contact spring. The freewheel is blocked when the electric motor is running, the engine has not yet started.
It may happen that the pinion abuts against the crown C without meshing with it. In this case, the spring 5 teeth against teeth is compressed until closing of the movable contact and supply of the electric motor which then drives in rotation the shaft 100 with penetration of the teeth of the pinion 1 in the teeth of the crown C. When the engine has started, the freewheel allows the pinion to rotate relative to the shaft 100 and thus spare the engine M.
The movable core 2b and the spring against teeth 5 increase the radial size of the contactor, which must be powerful.

• la cinématique, qui est une caractéristique intrinsèque du démarreur, exprime l'avancée du lanceur en millimètres entre l'instant où la clé de contact est tournée jusqu'au moment où le moteur électrique est mis sous tension. Cette cinématique doit être supérieure à la distance qui existe au repos entre le lanceur et la couronne C sinon le moteur électrique pourrait être mis sous tension avant même que le pignon 1 du lanceur ait pénétré dans la couronne C du moteur thermique, provoquant ainsi le fraisage de cette même couronne par le lanceur. Cette cinématique dépend de la puissance du solénoïde, comportant le bobinage 2a, de la masse du lanceur 102, de la raideur des différents ressorts présents dans le système, de la viscosité des graisses, du frottement existant entre les différents éléments en mouvement et de la température. La cinématique est difficile à optimiser étant donné le grand nombre de paramètres qui l'influencent.
• la raideur du ressort dent contre dent 5 doit être suffisante pour pousser d'une longueur suffisante le pignon du lanceur 102 dans la couronne C lorsque le pignon 1 ne se trouve plus dans une position dent contre dent. En contrepartie, cette raideur ne doit pas être trop élevée car elle est une composante du dimensionnement de la puissance du solénoïde 2a. Plus le ressort dent contre dent 5 a une raideur importante, plus le solénoïde doit créer un champ électromagnétique important. La taille du solénoïde 2a est d'autant plus grande que le champ magnétique qu'il doit créer est grand. La puissance du solénoïde dépend ainsi de la masse du lanceur 102 et de la raideur du ressort dent contre dent 5. Plus le solénoïde est puissant, plus la cinématique est faible. En effet, un solénoïde puissant est capable de vaincre la force du ressort dent contre dent de manière à réaliser le contact de puissance alors que le lanceur ne se sera pratiquement pas déplacé à cause de son inertie. Le dimensionnement du solénoïde n'est donc pas aisé et prend un temps de développement important. Il faut aussi adapter le solénoïde aux lanceurs qu'il doit mettre en mouvement ce qui à pour conséquence un manque de standardisation.
• la puissance nécessaire pour mettre en mouvement le plus petit des lanceurs est telle que le volume du solénoïde 2a est important. D'une manière générale, le diamètre des solénoïdes est voisin de 50mm pour une longueur calée au maximum sur celle du démarreur.
• en position dent contre dent, le moteur électrique est mis sous tension avant que le pignon 1 du lanceur ait pénétré dans la couronne C. Si les états de surface de la couronne C de démarrage du moteur thermique ou du pignon 1 sont dégradés, si la raideur du ressort dent contre dent est trop faible, si le moteur électrique a une trop forte accélération au départ, ce qui est souvent le cas pour les démarreurs sans réducteur, il y a un risque de ne pas voir le lanceur pénétrer suffisamment dans la couronne C et ainsi de mettre en rotation le pignon 1 devant la couronne C à grande vitesse c'est à dire provoquer un fraisage de cette couronne par le pignon 1 du lanceur provoquant ainsi une détérioration irréversible.
• lorsque le lanceur arrive en butée contre la couronne C en étant lancé par la fourchette 13 mise en déplacement par le noyau mobile 2b , celui-ci a une vitesse non négligeable et le choc est fort. Cela engendre du bruit et provoque une détérioration des surfaces en contact. Cette détérioration, au démarrage peut être une cause de fraisage.

This mode of penetration of the pinion 1 of the launcher 102 has the following drawbacks:

• the kinematics, which is an intrinsic characteristic of the starter, expresses the advance of the launcher in millimeters between the moment when the ignition key is turned until the moment when the electric motor is turned on. This kinematics must be greater than the distance that exists at rest between the launcher and the crown C otherwise the electric motor could be energized even before the pinion 1 of the launcher has penetrated into the crown C of the engine, causing the milling of the same crown by the launcher. This kinematics depends on the power of the solenoid, comprising the winding 2a, the mass of the launcher 102, the stiffness of the various springs present in the system, the viscosity of the greases, the friction existing between the various moving elements and the temperature. Kinematics is difficult to optimize given the large number of parameters that influence it.
• the stiffness of the spring tooth against tooth 5 must be sufficient to push a sufficient length of the starter pinion 102 in the crown C when the pinion 1 is no longer in a tooth against tooth position. In return, this stiffness should not be too high because it is a component of the sizing of the power of the solenoid 2a. The stronger the spring against tooth 5, the greater the solenoid must create a large electromagnetic field. The size of the solenoid 2a is all the greater as the magnetic field it has to create is large. The power of the solenoid thus depends on the mass of the launcher 102 and the stiffness of the spring tooth against tooth 5. The stronger the solenoid, the lower the kinematics. Indeed, a powerful solenoid is able to overcome the force of the tooth against tooth spring so as to achieve the power contact while the launcher will not have moved substantially because of its inertia. Sizing of the solenoid is not easy and takes a significant development time. It is also necessary to adapt the solenoid to the launchers that it must set in motion which results in a lack of standardization.
• the power required to set the smallest pitchers in motion is such that the volume of the solenoid 2a is large. In general, the diameter of solenoids is close to 50mm for a length set at most on that of the starter.
• in the tooth against tooth position, the electric motor is energized before the pinion 1 of the launcher has penetrated into the ring gear C. If the surface states of the starting ring gear C of the heat engine or the pinion 1 are degraded, if the stiffness of the tooth against tooth spring is too weak, if the electric motor has too much initial acceleration, which is often the case for starters without reducer, there is a risk of not seeing the launcher penetrate sufficiently into the crown C and thus to rotate the pinion 1 in front of the crown C at high speed, ie cause a milling of this crown by the pinion 1 of the launcher thereby causing irreversible deterioration.
• when the thrower comes into abutment against the crown C being thrown by the fork 13 moved by the movable core 2b, it has a significant speed and shock is strong. This generates noise and causes deterioration of the surfaces in contact. This deterioration at startup can be a cause of milling.

Document FR A 2,174,421 discloses a double contact solution for generating a pre-rotation of the electric motor. The system is provided with a solenoid and comprises a coil electrically connected, on the one hand, to the switch actuated by the ignition key and to a fixed contact positioned on the fixed core of the solenoid and, on the other hand, via the contact plate of the movable contact to a second fixed contact disposed diametrically opposite the first contact on the fixed core and itself directly electrically connected to the electric motor. In the nominal position of rest, the contact plate rests on the two aforementioned contacts so that when the switch is closed by actuating the ignition key, the powering of the electric motor is performed by passing a current through the contacts. contacts via the wafer and an electrical resistance. The electric motor starts a pre-rotation at low speed while the movable core is moved under the action of the magnetic field created by the coil. After engagement of the pinion in the crown C, the moving core, during its displacement, comes into contact with a spring, independent piece and distant from the movable core of a length calculated so that there is contact between the two parts only when the pinion meshes with the crown. The contact pad, secured to the action of the spring, starts moving, and disconnects the first two contacts, cutting the power of the electric motor. At the end of translation of the movable core, the wafer comes into contact with two other contacts that allow the closing of the power circuit and power under full load the electric motor. The disadvantages of this principle are of two types. Firstly, the breaking of the power supply of the electric motor when the contact plate moves and then the level of the intensity (about 70A) which passes through the first two contacts, the coil and the the switch actuated by the ignition key to perform the pre-rotation of the electric motor. This intensity value is not acceptable at the switch, in fact, the maximum value allowed is of the order of 50A.

US Pat. No. 4,418,289 shows a double-stage contactor solution similar to the solution of document FR A 2,174,421. This solution has two contact pads coming into contact with two series of contact. The electrical diagram is identical to the point that the resistive coil is in this case a pure resistor placed outside the solenoid. The two plates are not brought back simultaneously during the deactivation by the contact key of the solenoid of the contactor.

US Pat. No. 5,814,896 presents a solution in which the contactor is coaxial with the starter body and is placed at the rear of the apparatus. The double contact system is provided by a single-contact plate placed on a movable axis integral with the movable core, which is actuated by a cable running the entire length of the electric motor and connected to the launcher. The second contact is made by a movable contact connected to a spring type "clothes peg" whose other end is connected to the movable axis. This contact comes into contact with the battery terminal as well as the contact plate. The disadvantage of this solution is the sequential shutdown of the two power circuits.

Document US Pat. No. 2,342,632 discloses a starter in which there is provision for the rotational locking of the starter gear to advance it towards the starter ring of the engine by screwing the driver onto the helical teeth carried by the shaft carrying the starter gear. the sprocket of the thrower. The rotational locking is achieved by a needle operated by a solenoid perpendicular to the trainer. This embodiment is bulky radially.

These solutions are satisfactory, however the applicant wondered if it was not yet possible to further reduce the electromagnetic power of the contactor to further reduce its outer diameter.

Object of the invention

In order to remedy these drawbacks, the invention proposes a starter for a motor vehicle with a heat engine and an engine start ring. thermal device comprising a launcher, equipped with a trainer and a pinion, adapted to move from a retracted position of rest to an advanced meshing position with the starter ring of the engine of the motor vehicle, an electric motor equipped with a shaft adapted to drive a launcher shaft associated with the launcher, complementary helical splines intervening locally between the inner periphery of the driver and the outer periphery of the launcher shaft, an electromagnetic contactor extending parallel to the electric motor at the above it and having a movable core, a fork mounted to articulate at its upper end on the movable core and at an intermediate point on a support of the electric motor and the contactor, wherein the trainer comprises a receiving groove the lower end of the fork delimited by two flanks and in which means are provided to make turning the electric motor at a slow speed in a first phase and then at full power, characterized in that the launcher is locked in rotation by means of cooperation between the fork and the driver for its passage from its rest position to its position d meshing with the starter ring.

• lesdits moyens sont des moyens de blocage en rotation à coopération de formes.
• lesdits moyens sont des moyens de blocage en rotation du type à frottement.
• lors de l'alimentation électrique du contacteur, la fourchette coopère avec le flanc, dit flanc avant de la gorge de réception de la fourchette ; ledit avant étant doté d'ondulations circonférentielles.
• la fourchette présente des branches avec des ondulations de forme complémentaire à celles du flanc avant.
• lesdits moyens sont du type à dents de loup.
• le flanc avant de la gorge de réception de la fourchette comporte des crans et des bosses, tandis que la fourchette présente des doigts saillants coopérant avec les crans pour le blocage en rotation du lanceur
• le flanc avant de la gorge de réception de la fourchette coopère avec une bague de la fourchette montée coulissante axialement sur le fût de l'entraîneur.
• la bague est montée à articulation sur le corps de la fourchette et est actionnée par le corps de la fourchette.
• la fourchette comporte à son extrémité, qui coopère avec la gorge de l'entraîneur, au moins un patin, qui coopère avec un rebord situé à la périphérie de l'entraîneur lorsque le lanceur engrène avec la couronne de démarrage du moteur du véhicule automobile.
• lesdits moyens sont débrayables.
• le support comporte une partie avant en tôle globalement en forme d'ogive.
• la partie avant se raccorde à une bride de fixation et de centrage.
• le support en tôle est obtenu par déformation de matière, telle qu'un emboutissage, et la bride est d'un seul tenant avec la partie avant.
• le moteur électrique et le contacteur comportent chacun une culasse solidaire de l'autre culasse.
• les deux culasses appartiennent à une même pièce.
• la ou les deux culasses sont fermées du côté opposé au support par une pièce commune formant le palier arrière du moteur électrique.
• les moyens prévus pour faire tourner le moteur électrique en pré-rotation puis à pleine puissance, comportent deux plaquettes portées par le noyau mobile, la première plaquette, utilisée lors de la pré-rotation, est reliée à deux contacts, le premier contact est relié à la bobine résistive, le deuxième contact est relié à la borne positive de la batterie, puis lors de la pleine puissance, la deuxième plaquette est reliée à deux contacts, le troisième contact est relié à la bobine résistive et au moteur électrique, le quatrième contact est relié à la borne positive de la batterie.
• une plaquette de contact est admise à basculer autour du deuxième contact fixe pour coopérer avec un autre contact fixe décalé axialement et relié à la borne positive de la batterie pour alimenter le moteur électrique.
• l'axe mobile comporte une lamelle dotée d'une surépaisseur locale qui entraîne les plaquettes de contacts lors du retour de l'axe mobile après ouverture du circuit de commande.
• le contacteur électromagnétique comporte, au moins une plaquette apte à évoluer en rotation autour de l'axe mobile pour la mise en pré-rotation puis à pleine puissance du moteur électrique.
• la plaquette comporte deux plots reliés électriquement, un premier plot continuellement relié électriquement avec un contact relié à la tension de la batterie, un deuxième plot relié à un contact lors de la mise en pré-rotation du moteur, ce deuxième plot venant ensuite en contact avec un troisième contact, après rotation de ladite plaquette, pour fournir la pleine puissance au démarreur, les deuxième et troisième contacts étant reliés entre eux par la bobine résistive de pré-rotation, le contact étant relié au moteur électrique.
• le pignon du lanceur est relié à l'entraîneur par un dispositif d'attelage à embrayage conique.
• la ou les culasses sont rapportées par sertissage sur le support.
• la pré-rotation est réalisée en fournissant suffisamment de courant électrique au moteur électrique par l'entremise de la bobine d'appel sans utiliser d'élément résistif tel qu'une bobine résistive de pré-rotation. Dans ce cas, la fourchette est utilisée pour le blocage en rotation du lanceur et avantageusement pour aider le lanceur à se diriger vers la couronne de démarrage du moteur thermique.

Thus, thanks to the rotational locking of the launcher and to these means, it is possible to further reduce the power of the electromagnetic contactor and its radial size, thanks to a supply of energy from the electric motor.
In addition we take advantage of the existing place between the sides of the groove which allows not to increase the axial size beyond measure.
In addition, the fork becomes a predominantly follower fork.
According to other features of the invention:

• said means are rotational locking means cooperating forms.
• said means are rotational locking means of the friction type.
• during the power supply of the contactor, the fork cooperates with the sidewall, said front flank of the fork receiving groove; said front being provided with circumferential corrugations.
• the fork has branches with corrugations of complementary shape to those of the front flank.
• said means are of the wolf teeth type.
• the front flank of the fork receiving groove has notches and bumps, while the fork has projecting fingers cooperating with the notches for the rotational locking of the launcher
• the leading edge of the receiving groove of the fork cooperates with a ring of the fork slidably mounted axially on the shaft of the trainer.
• the ring is hingedly mounted on the body of the fork and is actuated by the body of the fork.
• the fork has at its end, which cooperates with the groove of the coach, at least one pad, which cooperates with a flange located at the periphery of the coach when the launcher meshes with the starter ring of the engine of the motor vehicle.
• said means are disengageable.
• the support comprises a generally sheet-shaped front part in the form of an ogive.
• the front part is connected to a fixing and centering flange.
• the sheet metal support is obtained by deformation of material, such as stamping, and the flange is in one piece with the front part.
• the electric motor and the contactor each comprise a yoke integral with the other yoke.
• the two yokes belong to the same coin.
• the one or both yokes are closed on the side opposite the support by a common part forming the rear bearing of the electric motor.
• the means provided for rotating the electric motor in pre-rotation and at full power, comprise two plates carried by the movable core, the first plate, used during the pre-rotation, is connected to two contacts, the first contact is connected at the resistive coil, the second contact is connected to the positive terminal of the battery, then at full power, the second plate is connected to two contacts, the third contact is connected to the resistive coil and the electric motor, the fourth contact is connected to the positive terminal of the battery.
• a contact plate is allowed to switch around the second fixed contact to cooperate with another fixed contact offset axially and connected to the positive terminal of the battery for powering the electric motor.
• the movable axis comprises a plate with a local extra thickness which drives the contact plates during the return of the movable axis after opening of the control circuit.
• the electromagnetic contactor comprises at least one wafer adapted to rotate in rotation about the movable axis for pre-rotating and then at full power of the electric motor.
• the wafer comprises two pads electrically connected, a first pad continuously electrically connected to a contact connected to the battery voltage, a second pad connected to a contact when the motor is pre-rotated, this second pad then comes into contact with a third contact, after rotation of said wafer, to provide full power to the starter, the second and third contacts being interconnected by the resistive coil of pre-rotation, the contact being connected to the electric motor.
• the starter pinion is connected to the driver by a conical clutch coupling device.
• the yoke (s) are crimped onto the support.
• pre-rotation is achieved by supplying sufficient electrical power to the electric motor through the call coil without using a resistive element such as a resistive pre-rotation coil. In this case, the fork is used for locking the launcher in rotation and advantageously to help the launcher to move towards the starting ring of the engine.

Brief description of the drawings

• la figure 1 est une vue en coupe axiale d'un démarreur de l'art antérieur ;
• la figure 2 est un schéma du circuit d'alimentation du moteur électrique du démarreur selon l'invention ;
• la figure 3 est une vue analogue à la figure 1 pour un premier exemple de réalisation selon l'invention ;
• la figure 4 est une vue analogue à la figure 3 pour un deuxième exemple de réalisation selon l'invention ;
• la figure 5 est une vue en perspective du support de démarreur des figures 3 et 4 ;
• - la figure 6 est une vue en perspective d'une culasse unique équipant les démarreurs des figures 3 et 4 ;
• les figures 7a, 7b sont des vues en perspective, selon des angles différents, d'un démarreur équipé d'un support et d'une culasse unique de la figure 6 ;
• les figures 8 et 9 sont des vues partielles en coupe montrant l'assemblage du support ou du palier arrière avec la culasse unique pour deux modes de réalisation ;
• la figure 10 est une vue locale du palier arrière assemblé avec la culasse unique pour un troisième exemple d'assemblage du palier arrière avec la culasse unique d'assemblage de la figure 6 ;
• la figure 11 est une vue partielle en coupe axiale du mode de réalisation de la figure 10 ;
• la figure 12 est une vue en coupe selon la ligne 12-12 de la figure 10 ;
• la figure 13 est une vue analogue à la figure 10 pour un quatrième mode d'assemblage du palier arrière avec la culasse unique ;
• la figure 14 est une vue partielle en coupe axiale pour un cinquième mode d'assemblage du palier arrière avec la culasse unique ;
• les figures 15 et 16 sont des vues analogues à la figure 13 pour un sixième et septième mode d'assemblage de la culasse unique avec le palier arrière ;
• la figure 17 est une vue en coupe pour un huitième mode d'assemblage de la culasse unique avec le palier arrière ;
• la figure 18 est une vue de dessus de la figure 17 ;
• la figure 19 est une vue en coupe axiale pour un neuvième mode d'assemblage du palier arrière avec la culasse unique ;
• les figures 20,21,23 sont des vues analogues à la figure 19 pour respectivement un dixième, onzième et un douzième mode d'assemblage de la culasse unique avec le palier arrière ;
• les figures 22 et 24 sont des vues selon les flèches 22 et 24 de la figure 23 ;
• la figure 25 est une vue schématique d'un mode de réalisation d'un lanceur de démarreur associé avec le contacteur selon l'invention ;
• les figures 26 et 27 sont deux vues en coupe axiale de deux variantes de réalisation de la figure 25 ;
• la figure 28 est une vue de face de la rondelle élastique équipant les lanceurs des figures 26 et 27.
• les figures 29 et 30 illustrent en perspective chacune un mode de réalisation de la fourchette selon l'invention.
• les figures 31 et 32 illustrent en perspective chacune un mode de réalisation de l'entraîneur comportant des moyens de blocage en rotation.
• La figure 33 est une vue d'un démarreur comportant un dispositif de blocage en rotation de son entraîneur associé à une bague.
• La figure 34 est une vue partielle en coupe d'un relais comportant une plaquette basculante.
• Les figures 35 et 36 sont deux vues , respectivement en coupe axiale et de face, présentant un relais comportant une plaquette tournante.
• La figure 37 est une vue en coupe complète d'un contacteur électromagnétique selon un mode de réalisation de l'invention.
• Les figures 38a à 38c représentent des exemples de réalisation des moyens de blocage en rotation.
• Les figures 39 et 40 illustrent, respectivement en coupe axiale et de manière schématique, d'autres modes de réalisation de la pré-rotation selon l'invention.

The following description illustrates the invention with reference to the accompanying drawings in which:

• Figure 1 is an axial sectional view of a starter of the prior art;
• Figure 2 is a diagram of the power supply circuit of the electric motor of the starter according to the invention;
• Figure 3 is a view similar to Figure 1 for a first embodiment of the invention;
• Figure 4 is a view similar to Figure 3 for a second embodiment of the invention;
• Figure 5 is a perspective view of the starter support of Figures 3 and 4;
• - Figure 6 is a perspective view of a single yoke equipping the starters of Figures 3 and 4;
• Figures 7a, 7b are perspective views, at different angles, of a starter equipped with a support and a single yoke of Figure 6;
• Figures 8 and 9 are partial sectional views showing the assembly of the support or the rear bearing with the single cylinder head for two embodiments;
• Figure 10 is a local view of the rear bearing assembled with the single yoke for a third example of assembly of the rear bearing with the single assembly yoke of Figure 6;
• Figure 11 is a partial view in axial section of the embodiment of Figure 10;
• Figure 12 is a sectional view along the line 12-12 of Figure 10;
• Figure 13 is a view similar to Figure 10 for a fourth mode of assembly of the rear bearing with the single yoke;
• Figure 14 is a partial view in axial section for a fifth mode of assembly of the rear bearing with the single yoke;
• Figures 15 and 16 are views similar to Figure 13 for a sixth and seventh mode of assembly of the single yoke with the rear bearing;
• Fig. 17 is a sectional view for an eighth method of assembling the single yoke with the rear bearing;
• Figure 18 is a top view of Figure 17;
• Figure 19 is an axial sectional view for a ninth mode of assembly of the rear bearing with the single cylinder head;
• Figures 20,21,23 are views similar to Figure 19 for respectively a tenth, eleventh and a twelfth mode of assembly of the single yoke with the rear bearing;
• Figures 22 and 24 are views according to the arrows 22 and 24 of Figure 23;
• Figure 25 is a schematic view of an embodiment of a starter starter associated with the contactor according to the invention;
• Figures 26 and 27 are two views in axial section of two embodiments of Figure 25;
• Figure 28 is a front view of the spring washer equipping the launchers of Figures 26 and 27.
• Figures 29 and 30 illustrate in perspective each an embodiment of the range of the invention.
• Figures 31 and 32 illustrate in perspective each an embodiment of the trainer having rotational locking means.
• Figure 33 is a view of a starter having a locking device in rotation of its trainer associated with a ring.
• Figure 34 is a partial sectional view of a relay having a tilting plate.
• Figures 35 and 36 are two views, respectively in axial section and front, having a relay having a rotating plate.
• Figure 37 is a full sectional view of an electromagnetic contactor according to one embodiment of the invention.
• Figures 38a to 38c show embodiments of the rotation locking means.
• Figures 39 and 40 illustrate, respectively in axial section and schematically, other embodiments of the pre-rotation according to the invention.

Description of Preferential Embodiments

In the illustrated figures the common elements will be assigned the same reference signs and the front-to-back direction corresponds to the direction going from the left part to the right part of FIGS. 1, 3 and 4.

In FIGS. 3 and 4, the starter comprises, as in FIG. 1, a support 4 which comprises, first means for fixing and centering the electromagnetic contactor, second fixing and centering means for the electric motor M extending parallel to the contactor and below it. The support 4 also comprises third means for fixing and centering the starter on the casing of the engine of the motor vehicle so that the pinion 1 of the launcher meshes reliably with the starter ring C of the heat engine; said crown here belonging to a rigidly or resiliently rotating flywheel of the crankshaft of the heat engine or internal combustion engine.
The support 4 is metallic and ensures the return to ground. It is economical because it is obtained here by deformation of material, for example by stamping.
The electric motor M has a constitution similar to that of Figure 1 except for the assembly of the brushes and the collector blade.

Here the brushes are radially oriented and are carried internally by the metal cylinder head of the electric motor and the collector is of axial orientation. Four brooms are provided here. Two brushes, called negative brushes, are connected to ground via the yoke 25 and the support 4. Two brushes, called positive brushes, are connected to the positive terminal of the battery via the contactor 2.
These figures are shown schematically at 27 a broom-cage assembly.
Here the shaft 101 of the electric motor is also the shaft 100 of the launcher and therefore carries the working stopper 6.
The rear bearing 26 is made of plastic and, according to one characteristic, is also the rear bearing of the contactor. The yokes of the contactor 2 and the electric motor M are integral with each other. Advantageously, the two yokes belong to one and the same continuous part 25 as can be seen in FIG.
The connection cable between the contactor and the positive brushes is removed as described below. The starter is thus less expensive because it has fewer components.
The fork 13 is, as in FIG. 1, hingedly mounted at an intermediate point 11 on the support 4. The fork 13 is hingedly mounted at its upper end directly on the movable core 2b of the contactor 2 and penetrates at its lower end. , as in Figure 1, in a groove of the driver 12 belonging to the pinion launcher 102.

According to a characteristic of the invention, a starter of the type indicated above is characterized in that the driver 12 is provided with means for locking it in rotation during its passage from its rest position to its meshing position with the start crown.

According to a first embodiment, as shown in Figures 3 and 4, the locking in rotation is achieved by a fork 13 made of rigid material preferably. A rotational locking device therefore intervenes between the launcher and the fork.

Thus according to the invention the launcher is locked in rotation by means of cooperation between the fork 13 and the coach 12 for its passage of its rest position (Figures 3 and 4) at its meshing position, via its pinion, with the starter ring.

These co-operating means, which in FIGS. 3 and 4 are means for locking in rotation in the form of co-operation, are located at the level of the fingers situated at the base of the fork 13 and at the level of the rear face of the driver. More precisely, the branches or arms of the fork are received in a groove of the driver 12 delimited by the sidewalls 121, 122, respectively front and rear, transverse to the axis of the shaft 101.
In the rest state the fingers of the fork 13 are supported on the smooth rear flank 122 of the receiving groove. The branches of the fork are corrugated for finger formation as visible at 22. The front flank 121 has, for receiving the fingers 22, circumferential corrugations 21 as shown in Figures 3 and 38c. As a variant, the front flank 121 may have other form-forming means, for example in the form of saw teeth (FIG. 38a), wolf teeth (FIG. 38b) or corrugated teeth (FIG. 38c); the branches of the fork presenting means complementary to those of the sidewall 121. In general, the fork cooperates with the sidewall 121 and has branches with corrugations of shape complementary to that of the sidewall 121.
In another embodiment, the rotational locking means may consist of plane friction arranged on the one hand on the driver and on the other hand on the fork.
Alternatively, as illustrated in Figures 31 and 32, the circumferential corrugations 21 are formed of notches 320 and bumps 321. The notches 320 are of complementary shapes to those of the fingers 22 of the branches 293 of the fork 13 as shown in Figure 31 The protruding fingers penetrate the notches 320.

Figure 33 illustrates a variant of the rotational locking device of the launcher. In this embodiment, the inner periphery of the fork comprises a ring and the fingers 22 of the fork 13 are offset on the ring 15 slidably mounted axially on the barrel-shaped tubular portion of the driver. This ring 15 is hingedly mounted on the inner end of the rod-shaped body 292 the fork by means of a pivoting means 291 comprising for example a pivot carried by the rod 292 and received in a clevis of the ring 15. The ring 15 is actuated by the body 292 of the fork for its axial displacement on the shaft of the trainer. Alternatively, the pivoting means comprises a game JC (not shown) performing the previously described cutoff function.
In this embodiment, the fork 13 therefore does not comprise arms but a rod 292 having at its lower end the means 291 for pivoting with the ring 15.
This embodiment of rotation locking device carried by a ring 15 has the advantage of having a perfect connection between the ring 15 and the coach throughout the translation of the launcher which is not the case with the fork which pivots around its axis thus favoring the teeth of the fork to leave the notches of the coach.

In a variant, a ratchet and ratchet device can be envisaged.

In general, the rotational locking of the launcher is achieved by friction, with the aid of magnets, by cooperation of shapes or by any other means.

Of course, the shapes that cooperate with each other are not limited to the embodiments described above.

Thus, according to the invention the rotational locking of the launcher consists of means which cooperate with each other rigidly. Indeed, the locking device in rotation (wolf teeth, friction, magnets ...), the fork and the shaft of the movable axis are parts derived from rigid materials that can not present a deformation of material under the effect of the force exerted by the attraction of the mobile core.

An advantage according to the invention is to realize a rotational locking with a reduced number of components, these components being mainly known components in the field of starters, including the fork, the movable axis and the groove of the trainer in which the fingers of the fork are lodged.

Thus, in a simple and economical manner, a rotational locking is achieved which makes it possible to obtain an electromagnetic contactor of reduced size, in particular as regards the mobile core, because the force which makes it possible to advance the Forward thrower is provided by the electric motor in its pre-rotation regime.
The force exerted by the fork on the launcher is very small. It will be appreciated that the mobile core is simplified.

In order to put the electric motor M in pre-rotation before applying to it full power, the relay constituted by the electromagnetic contactor must comprise a device which allows, on the one hand, to implement the pre-rotation of the electric motor under low power, then, to apply the same power to the same engine and, on the other hand, when opening the key this contact, to simultaneously turn off the full power and pre-rotation of the electric motor. It is important to be able to deactivate these two modes of operation simultaneously, especially in the case where the pinion remains locked in the starter ring. In this case, the device according to the invention must allow through the JC cutoff game, to disconnect the full power simultaneously with the pre-rotation to completely turn off the electric motor M.

In a first embodiment, the means for rotating slowly the electric motor and then at full power comprise two contact pads mounted on a movable axis integral with the movable core and two pairs of contacts.

In Figure 2 is shown schematically the electric circuit of the starter. It comprises a holding winding 37, a call winding 36, a call coil and pre-rotation 39, two contact pads P1 and P2 electrically conductive intended to come respectively in contact with a first series of contacts having two contacts C1 and C2 and with a second series of contacts having two contacts C3 and C4, the electric motor M and the start switch 35 electrically connected to the positive terminal of the battery. The electric motor M and the holding coil 37 are electrically connected to ground, while the contacts C2 and C4 are electrically connected, respectively by lines 33, 34, to the positive terminal of the battery. The call coils 36 and hold 37 surround the mobile core 2b. Advantageously, the pre-rotation coil 39 also surrounds the mobile core 2b. This pre-rotation coil 39 is advantageously electrically connected to the contact C1 of the first series of contacts and the electric motor M, while the contact C3 is electrically connected to the electric motor.
The plates P1 and P2 are carried by the movable core 2b of FIG. 3. In this FIG. 3 the winding 2a comprises the coils 37 and 36 of FIG. 2 connected in series with the coil 39 in the form of an electrical resistance.

With this arrangement, the switch 35 is closed, the motor rotates at a slow speed from the closing of the first switch constituted by the first plate P1 and the first series of contacts C1, C2.

With the movement of the moving core continuing, the second contact pad P2 comes into contact with the second series of contacts C3, C4, one of which is electrically connected to the electric motor and the other electrically to the positive terminal of the battery so that that the electric motor runs at full power.

Sets J1 and J2 are calculated so that the first contact of the wafer P1 with the contacts C1, C2 takes place during the catching of the breaking clearance JC by the movable core and the second contact of the wafer P2 with the contacts C3. , C4 is performed when the movable core is relative to the fixed gear 2d (Figure 3) almost zero air gap, which ensures good penetration of the pinion in the starter ring.

The return of the pads when opening the motor control circuit M and the relay constituted by the electromagnetic contactor must be done simultaneously to not leave the armature under tension, even with a low intensity. For this, as shown in Figure 37, a clip is used for the first contact pad. This clip is made by performing in the movable axis 40, by means of a removal of material in this axis, a strip 23 provided with a local extra thickness. When the moving axis advances, the contact plate P1 comes into contact with the contacts C1 and C2. It hangs while the movable axis continues its axial stroke backward. The extra thickness of the blade 23 arrives at the platelet P1. The strip 23 lowers, leaving the passage to the plate P1 which then crosses the allowance here located in the middle of the tongue, then gets up after. The clip is then in position to function.
When returning, that is to say when the moving axis is moving forward, the extra thickness abuts against the plate P1. The axial force to be provided to bend again the strip 23 being greater than the force provided by the contact spring 20 of the wafer, said wafer is forced to follow the movement of the movable axis forward and thus disconnects electrically contacts C1 and C2. The wafer then abuts against the fixed core 2d of the solenoid and, the force exerted by the return spring 17,18 of the movable core being greater than the disengaging force, the sipe lowers and the extra thickness returns from the other side of the plate in its nominal position of rest. Advantageously, this clip makes it possible to electrically disconnect the electric motor, in particular at a slow pre-rotation speed, in the case where the pinion remains locked in the starting ring C of the internal combustion engine. This is possible thanks to the JC break set which allows a forward displacement of the movable axis even if the pinion remains meshed in the starter ring.

FIG. 3 illustrates a starter comprising a contactor provided with two contact pads P1 and P2 as previously described. In this embodiment, the movable core 2b is staggered in diameter and has a larger diameter portion protruding outside the coil 2a. This core, like that of FIG. 37, is simplified with respect to that of FIG. 1 and consists of a simple economic step rod with reduced radial dimensions guided by the support 2c of the coil 2a forming a solenoid.
A return spring 18 acts between the winding support and a shoulder of the front part of the core 2b. This spring replaces the return spring 18 of Figure 1. The first portion of larger diameter penetrates inside the coil 2a and is extended by a second portion of smaller diameter around which is mounted a contact spring 20 of plate P1 bearing on the change in diameter between the first and second portions of the movable core and on the first electrically conductive contact pad P1 axially fixed on an attached stop 54, such as a circlip, mounted at the rear end of the second portion extended by a third portion, of smaller diameter than the second portion, around which is mounted a contact spring 21 bearing on the stop 54 and the second plate P2 fixed axially on an end stop 38 reported to the rear end of the mobile core. The electrically conductive pads can therefore move relatively with respect to the core 2b. In particular, the plate P1, axially wedged against the stop 54, is pushed back by the action of the spring 20 which is wedged axially forward against a shoulder of the movable core. So, when the movable core moves backwards, the plate P1 moves backwards, under the effect of the contact spring 20, to abut against the contacts C1 and C2. A recess 60 is provided in the fixed core 2d to allow the passage of the contact spring 20 of the first plate P1.

Thus when the plate P1 is in contact with the contacts C1, C2 the core 2b moves axially by compressing the spring 20. It is the same for the plate P2, the contact spring 21 being compressed under the action of the displacement towards the back of the staged mobile core. After opening the switch 35 associated with the ignition key, the springs 21, 20 and 18 exert a permanent action.
The screw 131 is connected to the positive terminal of the battery and is in electrical connection with an electrical track having a perpendicular return constituting the contact C2. Similarly, the contact C1 belongs to an electrical track connected to the positive brushes of the electric motor M.
Note the presence (not visible) of a screw located in the same horizontal plane as the screw 131 connected firstly to the switch (ignition key) and secondly to the winding of the contactor.
The contact C3 also belongs to an electrical track connected to the positive brushes, the contact C2 is electrically connected, on the one hand, to an electrical resistance to turn the electric motor at low speed in the first place and, on the other hand, at contact C4 connected to the positive terminal of the battery.

Figure 37 illustrates more precisely a complete relay incorporating an electromagnetic contactor having two plates. In this embodiment, two contact plates P1 and P2 are fixed on a movable plastic axis 40 on which they can move in translation. This movable axis 40 and for example fixed by clipping or gluing or welding on the mobile core 2b. This movable core may have a cylindrical or square section. In the case of a square section, the mobile core is made economically from a stack of sheets. Springs 20 and 21 hold the plates against shoulders made in the axis. The pads have cylindrical central openings of a diameter equivalent to that of the shoulders to make possible the mounting. Then they are fixed by deformation of the opening which reduces along an axis the diameter making the opening oblong shape. Flats made in the axis allow this deformation.

The movable axis is integral with the movable core and the assembly can move in translation along the longitudinal axis of the contactor forming a relay. A core return spring 18 is positioned at the front between a shoulder secured to the movable core 2b and a washer 2'd integral with the winding support 2a. It makes it possible to return the mobile core to its rest position and to keep it in this position after the relay control circuit has been cut off. The fork is positioned between two flanks of the movable core. It is, at rest, resting on one of the flanks and distant from the second flank of a distance called JC break game.

Positioned between the fork and the washer 2'd, the lever spring 17 makes it possible, on the one hand, to return the fork to its rest position after cutting off the control circuit, and on the other hand to keep the launcher in the position of rest. The springs 17 and 18 are dissociated because the spring 17 has a greater stiffness because the launcher can exert a strong thrust on the fork during sudden decelerations of the vehicle. It is impossible to put a stiffness on the spring 18 equivalent to that of the spring 17 because the winding is not dimensioned, initially, to counter the axial force created by the spring 17 on the fork. The springs 17, 18 allow aforementioned manner a disengagement of the plate P1.

As shown in Figure 29, the fork 13, here rigid plastic metal variant, below its axis of rotation 11, separates into two branches 293 in the image of a fork. Both ends of this fork have fingers 22 which have a particular shape, here cylindrical, and which can fit into the complementary shape 21 located on the outer face of the coach. These forms, arranged on the coach, are comparable to notches whose purpose is, when the fork is engaged in the coach, to block the launcher in rotation. On the other hand, if the thrower has the necessary torque, the coach can jump the notches by rolling back the fork.

In FIG. 37, in the aforementioned manner, a strip 23 provided with an extra thickness is created on the movable axis in order to fulfill a clip function with the plate P1 which will make it possible to bring back at the same time, when the circuit is opened. control, the two plates P1 and P2.

The double contact is made, firstly by contacting the plate P1 with the contacts C1 and C2, and secondly by contact of the wafer P2 with the contacts C3 and C4. The springs 20 and 21 serving respectively crushing springs for the wafers to ensure good contact.

The contact C4 is connected to the battery terminal and is connected to the contact C2 via a wired type electrical connection 29. The contact C1 is electrically connected to the resistive pre-rotation coil by an electrical connection means 30. The contact C1 is electrically connected to the contact C3 by an electrical connection means 32. The contact C3 is also connected to the electric motor by connecting means 49.

The contacts C1 and C2 are electrically connected to a resistive pre-rotation coil with a resistance close to 150 mohms in order to limit the passage of current to a value between 50 and 80A to ensure sufficient pre-rotation of the motor electric.

This resistive pre-rotation coil is placed on top of the other two coils conventionally encountered in all the contactors, namely the call coil 36 and the hold coil 37.

In a second embodiment visible in FIG. 34, a single plate P0 is used as well as a single pair of contacts C5 and C6 which are offset axially with respect to each other along the axis of the relay. The contact C5 ensures the pre-rotation of the electric motor M and the contact C6 feeds the same motor at full power. C6 contact and connected to the battery. In an exemplary embodiment, the pre-rotation resistive coil 39 is connected to C6 via an electrical connection 48, for example of the wired type. Advantageously, the contact C5 is connected directly to the electric motor by an electrical connection means 49. This embodiment has the advantage of not using external connection terminals and an external connection wire. This avoids sealing problems at the external terminals and also helps to reduce the size of the starter and its cost and weight.

The contact plate in a first phase is perpendicular to the movable core and moves in contact with a contact connected to the resistor until it comes to contact of the contact connected to the positive terminal of the battery via the start switch.

The resistive coil 39, also used as a call coil, is electrically connected to the contact pad P0 by an electrical connection means 31 which is for example welded to the wafer P0. This connecting means 31 may consist of a wire coming directly from the winding 39. In a variant, this connecting means 31 may consist of a spring plated on the circumference of the wafer P0.
When the coil 39 of the solenoid is energized, the movable core 2b is attracted and the movable axis 40 is set in motion. The contact pad P0 contacts the contact C5, thus closing the supply circuit of the armature at low intensity to perform a pre-rotation of the electric motor.
The movable core 2b continues its travel and the movable axis 40, via the contact spring 16 of the wafer, presses the wafer P0 which pivots around the contact C5. When the movable core 2b has almost reached the end of travel, the plate P0 comes into contact with the contact C6, closing the power circuit and short-circuiting the pre-rotation circuit.
The same clipping system that used in the previous solution with a slat (not shown) opens the two power circuits simultaneously during the return of the movable core in its rest position.

FIG. 4 illustrates a starter comprising a contactor provided with a pivoting contact pad P0 as described above. In this embodiment, the pre-rotation resistor is here in the form of a resistive coil 39 wound next to the winding 2a of attraction of the movable core 2b.

In this embodiment, the resistive coil 39 surrounds the first large diameter portion of the movable core while the second smaller diameter section of the movable core is surrounded by the holding and calling coil 2a. In another embodiment, the reverse configuration can be realized.

The second portion of the movable core 2b is longer without spring, while the first portion of this core is shorter and is surrounded by a return spring 18.

The third portion is surrounded by a spring 16 acting on the wafer P0 which is here unique, a third spring 24 (visible in Figure 34) acts between the outer periphery of the wafer and the fixed core 2d of the coil 2a.

In a third embodiment visible in FIGS. 35 and 36, a contact pad P3 is mounted on a mobile pin 40 integral with the movable core and having at its outer periphery helical splines 50 cooperating with complementary helical splines made at the inner periphery. of the P3 wafer. Axis 40 projects radially a stop 53 for wafer P3.
At rest, the contact plate P3 is held pressed against a shoulder 51 of the body of the solenoid 2a by an elastic washer 52 integral with the movable axis 40. The plate P3 has a special shape as shown in Figure 36. It comprises two circular sectors, one of which is of greater circumferential extent, is intended to cooperate with the contact C7 and the other with the contact C8 or C9 axially of the same height. C7 and C9 contacts are diametrically opposed

As the movable core advances, the wafer driven by the movable axis and held by the stop 53, follows the translational movement backwards. It abuts on the first contact C7, which is connected to the battery of the vehicle, and on the contact C8, itself electrically connected to C9 by the resistive pre-rotation coil 39 thus closing the first power contact since the contact C9 is directly connected to the electric motor.
The movable core continues to advance, and as the plate P3 is blocked - axially, it starts to rotate on itself thanks to the aforementioned grooves and comes into contact C7 and C9 while remaining in contact with C8 via the coil 39 pre-rotation so as not to create a break in current. In this position, the resistive coil 39 is short-circuited which allows to directly power the electric motor M starter at full power.
The contact crushing force is produced by the axial thrust force of the movable core and echoed by the grooves.
During the return of the movable core, the movable axis pulls with it the wafer which withdraws at once from the contacts C7 and C9, thus opening the power circuit without closing the first circuit between C7 and C8. The electric motor M is thus cut off from any power supply.

The wafer then comes into abutment against the shoulder 51 of the body of the solenoid. Being blocked in translation, the plate P3 is rotated under the pressure of the spring washer 52 which forces the plate P3 to return to its initial position by screwing on the helical teeth 50.

To facilitate the rotation of the plate P3 and to avoid possible jamming of this plate in the grooves of the movable axis given the small thickness of the plate and therefore the tooth, it is possible to envisage a plastic sleeve coming from take on the splines of the movable axis and itself having splines.

In Figures 29 and 30 is shown a preferred embodiment of the fork 13 according to the invention. This fork comprises an axis of rotation 11 carried for example by the support 4 of the starter. Under the effect of the action of the electromagnetic contactor, the fork 13 rotates in rotation about this axis 11. This fork comprises a body 292 in the form of rod making a rigid connection between the axis of rotation 11 and two arms or branch These two arms are advantageously circular in shape. These two arms each carry a tooth 22, finger-shaped, facing forward. The tooth presents forwards a shape 295 preferably circular adapted to cooperate with the notches 320 shown in Figures 31 and 32. The teeth or fingers 22 are in the form of a cylindrical stud. The lower part of the arms 293 is advantageously provided with shoes 290. These pads are in the form of a protuberance oriented towards the front as for the teeth 22, that is to say facing the launcher. The forward end portion of the most advanced shoe 296 may be flat as shown in Figures 29-31. In another embodiment, this end portion of the shoe may be bulged. Alternatively, the fork may have only one shoe 290. At its upper end, the fork 13 has two lugs 297, perpendicular to the main axis of the fork carried by the two branches 298 used for the hinge assembly with the movable axis 40 secured to the movable core of the contactor. These two ears 297 serve to support the return spring 17 of the fork 13.

Figure 30 shows the fork 13 associated with the movable axis 40 secured to the movable core 2b, here of generally rectangular section. The mobile 40-core mobile axis assembly has at its front end an H-shape perpendicular to the axis of the mobile axis 40-moving core assembly and delimiting a 300 obviously intended to receive the two branches 298 of the fork 13 for its hinge assembly. This recess 300 has an axial length greater than the thickness of the branches 298 of the fork so as to leave a clearance JC, which plays the role of cut-off game in case of blockage of the pinion in the starter ring. The branches of the H of the front end of the movable 40-movable mobile axis assembly protrude to define in particular a rear shoulder 301 rear face 301.

According to one embodiment, the rear face 301 of the rear shoulder of the recess 300 constitutes the forward stop of the return spring 18 of the movable core and the rear face 302 of the ears 297 of the fork 13 constitutes the front stop of the spring. 17 of the fork.
In the previous figures the launcher comprises, as in Figure 1, a driver coupled by a freewheel coupling device to the pinion 1.
Advantageously, the weight of the launcher can be further reduced by the use of a coupling device with a conical clutch as described, for example, in document FR 01 08607 filed on June 29, 2001. This coupling device is more economical and lighter than that of the freewheel type, will be described hereinafter in Figures 25 to 28.
This device reduces the weight of the launcher, as well as the number of these components and the axial size of the launcher.
In all cases the range 13 becomes a predominantly follower fork.
Because of the reduction in the radial size of the launcher, the two yokes can be secured to one another advantageously in one piece (Figure 5).
The support 4 can be simplified.
As a variant (FIGS. 25 to 28), thanks to the invention, it is possible to use, in the aforementioned manner, a light launcher, which is less bulky and has fewer components.
In these figures there is provided a conical clutch coupling device 7 (FIG. 25) for coupling the pinion 1 to the driver 12. The conical clutch 7 comprises (FIGS. 26 and 27) a first frustoconical friction surface 8, said first surface, integral with the pinion 1 and a second frustoconical friction surface 8 ', said second surface, of complementary shape to the first surface 8 and integral with the driver 12. The coupling device comprises, on the one hand, a hollow-shaped coupling piece having a bottom extended by an annular skirt directed axially towards one of the pinion 1 - drive 12 elements and, on the other hand, elastic means 10 axially acting on a first abutment integral with the coupling piece for action on a second abutment 4 'integral with one of the pinion elements 1 - coach 12. The elastic means 10 are carried by the skirt 1b (Figure 26) or 12b (Figure 27) of the coupling piece. This skirt, on the one hand, internally carries one of the first and second surfaces 8, 8 'and, on the other hand, is, via the bottom of the coupling piece, integral with one of the pinion elements 1 - launcher 12, which is associated with the surface 8, 8 'carried internally by the skirt, more precisely by the inner periphery thereof.
Here the contact diameter of the first surface 8 with the second surface 8 'is greater than the diameter of the head circle of the teeth of the pinion.
In these figures the first or the second surface 8, 8 'carried by the skirt 1b, 12b is longer axially than the other second or first surface 8', 8.
The elastic means 10 are carried by the free end of the skirt 1b, 12b and extend in axial projection with respect to said other second or first surface 8 ', 8.
The axial end of larger diameter of said other surface 8 ', 8 is delimited by a transverse shoulder carrying the second abutment 4' for axially compressing implantation of elastic means with axial action 10 between this second abutment 4 'and a first abutment carried by the free end of the skirt of the coupling piece.
The transverse shoulder is extended at its inner periphery by an annular bearing surface 4 "generally of axial orientation delimiting with said shoulder a removal of material to accommodate at least part of the elastic means with axial action 10.
The elastic means with axial action here have a shape of circlips and are received in a groove made at the inner periphery of the free end of the skirt.
These resilient means have alternately claws for engaging resiliently with the inner periphery of the free end of the skirt of the coupling piece as described in the document FR 01 08607 cited above for more details.
In Figure 28 the resilient means axial action 10 comprise tongues 10b deformable axially and extending circumferentially.
The tabs 10b are axially arched and comprise a washer 10a. In FIG. 28, the elastic means with axial action 10 comprise a washer 10a surrounding the elastic tongues 10b. These elastic tabs connect to the inner periphery of the washer 10a in favor of rooting zones 10d.The tabs 10b consist of annular sector-shaped arms extending circumferentially cantilevered on either side of a zone of rooting 10d. The washer 10a has a radial slot 10g symmetrically affecting one of the two rooting zones 10d; four arms 10b being provided at the rate of two arms per zone 10b.
Alternatively the first stop is formed by a circlip or a snap ring mounted in a groove formed at the inner periphery of the free end of the skirt. The elastic means 10 may then consist of at least one Belleville washer or at least one corrugated washer see in a frustoconical coil spring bearing against the circlip or the ring for action on the coach (Figure 26) or on the pinion (figure 27) for controlled tightening of surfaces 8,8 '.
In another embodiment, the first abutment is attached to the free end of the skirt.
In all cases, the elastic means with axial action comprise an elastic washer.
In these figures the free end of the skirt consists of a tubular extension.

In Figure 26 the skirt of the coupling piece is frustoconical.
Advantageously for evacuation of dust and separation of surfaces 8,8 'one of the first and second friction surfaces 8,8' has for contact with the other surface of the grooves and at least one first and second friction surface 8.8 'is alternatively constituted by a friction lining.
In Figure 26 the pinion 1 is integral with the generally bell-shaped coupling piece and the coupling piece is fixed on the pinion.

In Figure 27 the structures were inverted so that the coupling piece is secured to the launcher 12 which therefore has an outer skirt 12 b of cylindrical shape at its outer periphery.
As a result, the trainer is in an embodiment obtained by molding being for example plastic. In this case the corrugations 21 are easily obtained by molding from the leading edge 121. In FIG. 25, the decomposition of the forces is shown when the pinion 1 is in contact with the working abutment 6.

More precisely, the initial pressure of the elastic means between the stops produces a frictional torque between the driver and the pinion, which is always, by construction, greater than the torque required for screwing and advancing the launcher on the shaft 100.
This condition allows the self-priming movement of the launcher between its rest position and its advanced position against the work stop, 6 at the beginning of the driving phase of the vehicle engine via the starter ring. When the pinion reaches the stop 6 there is compression of the surfaces 8, 8 'against each other with a blockage
This blockage of movement between the pinion and the driver depends in particular on the angles and diameters of the frustoconical friction surfaces.
As can be seen in FIG. 25, during the driving of the internal combustion engine of the motor vehicle by the electric motor of the starter the torque Cd - generated by the starter at the output shaft 100 carrying the driver 12 and converted by the helical spline device 9 intervening between the driver 2 and the shaft 100 - creates an axial force Fa.
This force Fa is itself decomposed at the level of the frustoconical friction surfaces to create a normal contact force Fc, which generates a tangential force Ft to the frustoconical surfaces 8, 8 'as a function of the coefficient of friction between these surfaces. The value of this force Ft multiplied by the average contact radius of the frustoconical friction surfaces determines the torque Ce transmitted by the conical clutch 7.
In order for the pinion to behave normally without slipping, the relation Ce> Cd must always remain true.
All this depends on the applications because the coefficient of proportionality between Cd and Fa depends on the angle of inclination of the grooves 9, the average radius of these splines and the coefficient of sliding between the output shaft 100 and the driver.
The coefficient of proportionality between F and Fc depends on the angle of the cone between the two frustoconical friction surfaces.
The value of Ft is related to Fc and to the coefficient of friction fc between the two materials of the frustoconical friction surfaces of the clutch 7. To avoid any jamming, the tangent relation (a)>f'c, in where a is the value of the half-angle at the top of the contact cone between the frustoconical friction surfaces and the coefficient of adhesion.
All these values are calculated according to mechanics formulas known per se and depend on the applications.
These formulas involve the coefficient of friction between the splines of the shaft and the driver, the mean radius of the grooves, the cone angle of the surfaces 8,8 'and the coefficient of friction thereof. All this influences the choice of materials of the coach, the skirt and the pinion.
When the engine of the vehicle has started, the pinion 1 rotates faster than the output shaft 100 which allows the unscrewing of the launcher on the shaft 100. The previously transmitted axial force disappears and there remains only the residual torque low due to the elastic means 10 which is transmitted to the electric motor of the starter. During this short overspeed phase the clutch behaves like a freewheel device with relative movement between the surfaces 8,8 '. The average contact diameter between the two surfaces 8, 8 'is therefore also a friction diameter in the event of overspeed.

• lorsque l'on actionne la clé de contact, constituant l'interrupteur 35 de la figure 2, le bobinage 2a, composé du bobinage d'appel 36 et du bobinage de maintien 37 monté en série avec le moteur électrique M, est alimenté créant un champ magnétique faible suffisant pour vaincre l'effort exercé par le ressort de rappel 18. Il en résulte que le noyau mobile 2b se déplace en direction du noyau fixe 2d tout en comprimant, en premier lieu le ressort de rappel 18 du noyau et le ressort de rappel 17 de la fourchette 13.
• le noyau mobile rattrape le jeu de coupure JC en comprimant le ressort de rappel 18. Pendant la phase de rattrapage du jeu de coupure, la fourchette 13 demeure immobile car elle est maintenue en place par le ressort 17 de rappel de fourchette, la raideur de ce ressort 17 de rappel de fourchette étant supérieure à celle du ressort 18 de rappel du noyau. La fourchette 13, montée à articulation sur l'extrémité avant saillante du noyau 2b, se déplace et bascule autour de son point d'articulation 11 porté par exemple par le support 4.
  En se déplaçant vers l'arrière, le noyau mobile déplace la première plaquette de contact P1 contre la première série de contact C1, C2 ce qui a pour effet de mettre sous tension la bobine 39 d'appel et de pré-rotation du relais créant des efforts d'attraction du noyau mobile supplémentaires.

Figures 31 and 32 illustrate a conical clutch launcher having rotational locking means according to the invention.
In all cases the pitcher has a trainer with a groove for receiving the fork. In the figures, the driver 12 comprises a front flange of transverse orientation, advantageously of annular shape, pierced centrally for passage of the launcher shaft 100 associated with the launcher. This flange is extended rearward by a barrel-shaped tubular portion surrounding the shaft 100 and having locally at its inner periphery the helical grooves, better visible in Figure 25, for cooperation with complementary helical grooves arranged locally at the external periphery of the shaft 100. The tubular portion carries, for example axial solidarity, a washer, not referenced in Figures 3 and 4, the front face constitutes the flank 122 of the receiving groove of the lower end of the fork 13. The other side 121 of this annular groove is constituted by the rear face of the front flange of the driver. In a variant, the flank 122 and its associated washer have been molded with the driver (FIG. 27). The bottom of the groove is axially oriented and is annular in shape. This bottom belongs to the tubular portion on which are mounted to overlap the arms of the fork or sliding the ring 15 of the fork.
In Figure 27 the front flange is extended forward at its outer periphery by the skirt 12b. In Figure 26 the flange is massive and is extended forward by the span 4 "In the freewheel variants the flange is extended at its outer periphery forwards by a cylindrical skirt internally constituting a track for the rollers of the freewheel.
The starter of FIGS. 2, 3 and 37 comprising a contactor provided with two contact pads P1 and P2 operates in the following manner.

• when the ignition key, constituting the switch 35 of FIG. 2, is actuated, the winding 2a, consisting of the call winding 36 and the holding winding 37 connected in series with the electric motor M, is energized creating a weak magnetic field sufficient to overcome the force exerted by the return spring 18. As a result, the movable core 2b moves towards the fixed core 2d while compressing, in the first place the return spring 18 of the core and the spring 17 of the range 13.
• the movable core catches the breaking clearance JC by compressing the return spring 18. During the catching up phase of the cutting clearance, the fork 13 remains stationary because it is held in place by the fork return spring 17, the stiffness of this fork return spring 17 being greater than that of the return spring 18 of the core. The fork 13, hingedly mounted on the projecting front end of the core 2b, moves and tilts around its hinge point 11 carried for example by the support 4.
  By moving backwards, the movable core moves the first contact pad P1 against the first contact series C1, C2 which has the effect of energizing the coil of call and pre-rotation of the relay creating additional mobile core attraction efforts.

• lors de la mise en rotation de l'induit pendant la pré-rotation, le noyau mobile vient tirer la fourchette 13 qui pivote autour de son axe pour venir en contact avec la face externe de l'entraîneur munie de crans.
• sous l'effet de la rotation de l'arbre d'induit 100, le lanceur 102, bloqué en rotation par les dents ou doigts 22 de la fourchette insérés dans les crans 320 de l'entraîneur, se met en mouvement de translation. Cette translation est opérée grâce aux cannelures hélicoïdales portées par l'arbre d'induit 102 qui agissent comme une vis sans fin. De préférence l'angle des cannelures hélicoïdales, référencées en 9 à la figure 25, est compris entre 18° et 25°. Bien entendu on peut augmenter cet angle pour avoir des inclinaisons de l'ordre de 45°.

This coil 39 call and pre-rotation has an electrical resistance which limits the current flowing in the electric motor to a value preferably between 40 and 80 amperes. This additional pre-rotation coil 39 is wound for example around the other two call coils 36 and 37 in the contactor. Thus, means are provided for, following a start command by closing the start switch, rotate the electric motor at low speed before turning it to full power.

• during the rotation of the armature during pre-rotation, the movable core pulls the fork 13 which pivots about its axis to come into contact with the outer face of the trainer provided with notches.
• under the effect of the rotation of the armature shaft 100, the launcher 102, locked in rotation by the teeth or fingers 22 of the fork inserted into the notches 320 of the trainer, starts translational movement. This translation is operated by the helical grooves carried by the armature shaft 102 which act as a worm. Preferably the angle of the helical grooves, referenced at 9 in Figure 25, is between 18 ° and 25 °. Of course we can increase this angle to have inclinations of the order of 45 °.

Thanks to the rotational locking of the launcher and these means, one can reduce the electromagnetic power and the radial size of the contactor, thanks to an energy supply of the electric motor.

• la fourchette, toujours attirée par le noyau mobile, suit la progression du lanceur et reste donc en contact avec l'entraîneur, le bloquant toujours en rotation. La fourchette est suiveuse et ne contribue pas au déplacement du lanceur vers l'avant.
  En variante, la fourchette en plus de son rôle de blocage en rotation du lanceur peut également participer au déplacement vers l'avant du lanceur par un apport d'une force au niveau des ses doigts résultant du déplacement du noyau mobile vers l'arrière.
• le pignon arrive alors au niveau de la couronne C du moteur thermique.
• si le pignon via ses dents peut pénétrer directement dans la couronne C, plus précisément dans les dents de celle-ci, pour engrener avec la couronne C, alors le lanceur continue sa progression jusqu'à ce que le noyau mobile arrive en butée contre le noyau fixe.
• le pignon peut également se trouver en position dent contre dent contre la couronne. Dans ce cas, le pignon est bloqué en translation et en rotation. Dans cette position, l'induit fournit un couple proportionnel au courant d'intensité faible car le démarreur est toujours dans la phase de pré6rotation. Ainsi, le moteur électrique exerce un couple de rotation sur le pignon et le lanceur par l'intermédiaire des cannelures portées par l'arbre d'induit 100. Etant bloqué en translation, l'entraîneur va tourner de manière à repousser la fourchette 13 vers l'arrière qui n'est plus apte à bloquer en rotation l'entraîneur. La fourchette peut être repoussée en arrière car le bobinage 2a du contacteur présente une force inférieure à la force exercée par les crans sur la fourchette. Lorsque le pignon en tournant, trouve une ouverture dans la couronne du moteur, il y pénètre poussé par l'effort axial de la fourchette généré par l'attraction du noyau mobile par le solénoïde 2a.
  La valeur de l'intensité à faire passer dans le premier circuit de puissance est dimensionnée pour que le pignon entre en rotation en phase dent/dent, c'est-à-dire que l'induit ait le couple nécessaire pour que le pignon fasse sauter les crans et repousser la fourchette en arrière. La valeur de cette intensité est fonction de l'angle des cannelures hélicoïdales, de la forme des crans et du dimensionnement du solénoïde 2a.
  Ainsi, si avant d'engrener avec la couronne C, le pignon bute contre la couronne C, le pignon se met à exercer un couple sur les crans tel que les dents 22 vont sauter des crans en faisant reculer la fourchette 13. Le pignon peut alors tourner et pénétrer dans la couronne. Le mouvement se fait à faible vitesse du fait de la rotation à vitesse lente du moteur électrique. Les usures sont ainsi réduites du fait du faible choc que réalise le pignon lorsqu'il entre en contact avec la couronne grâce à sa faible vitesse axiale.
  Les moyens de coopération entre le lanceur et la fourchette, qui forment dans les figures illustrées des moyens de blocage en rotation, sont donc du type débrayable ; le lanceur étant mobile en translation et fixe en rotation durant le mouvement précité, tandis que l'arbre de lanceur 100 est mobile en rotation et fixe en translation ce qui permet au lanceur d'avancer axialement via les cannelures hélicoïdales précitées.
  Le contacteur 2 devient ainsi une pièce de dimension réduite et sa spécification devient indépendante du dimensionnement du lanceur.
• une fois que le pignon 1 a réussi à s'introduire dans la couronne C sous l'effet de la rotation d'induit, il poursuit sa course vers l'avant sous l'effet de la rotation de l'induit.
• au niveau du relais, le noyau mobile arrive en butée contre le noyau fixe ce qui a pour effet, d'une part de fermer le contact de puissance entre C3 et C4 par l'intermédiaire de la deuxième plaquette et d'autre part, de désengager la fourchette des crans du lanceur. Le pignon peut arriver en fin de course contre la butée de l'arbre tout en étant libérer de la fourchette. Le blocage en rotation est ainsi débrayable lorsque le pignon 1 vient en butée contre la couronne de démarrage.
• le contact de puissance C3 et C4 étant fermé par l'intermédiaire de la deuxième plaquette, l'induit du moteur électrique est alors alimenté sous pleine puissance. Il peut dès lors entraîner la couronne C pour assurer le démarrage du moteur thermique.
• lors d'une décompression du moteur thermique durant la phase de démarrage, la couronne C devient menante par rapport au pignon lanceur. Cette phase est appelée phase de roue libre durant laquelle le pignon a tendance à se revisser sur les dentures hélicoïdales ce qui a pour effet de le reculer.
• les deux patins 290 prévus à la base de la fourchette ont pour fonction d'éviter un recul trop important du lanceur lors de la phase de roue libre pendant laquelle le pignon à tendance à se revisser comme décrit précédemment. En l'absence de ces patins 290, ce recul aurait pour conséquence de mettre en contact les crans de l'entraîneur avec les doigts de la fourchette ce qui provoquerait une usure ainsi qu'un bruit. Ces patins viennent (figure31) en appui sur un rebord 310 situé à la périphérie de l'entraîneur. La forme des bras de la fourchette qui supporte ces doigts et ces patins est telle que les patins ne peuvent être en contact avec l'entraîneur que lorsque la fourchette se trouve être en position de pivotement ou de rotation maximale.

The size and weight of the launcher have a smaller impact on the sizing of the contactor, compared to a conventional contactor, so that one can choose with fewer constraints the launcher, which can be lighter or heavier.

• the fork, always attracted by the movable core, follows the progress of the thrower and therefore remains in contact with the coach, always blocking it in rotation. The fork is follower and does not contribute to the forward movement of the launcher.
  As a variant, the fork in addition to its role of locking the launcher in rotation may also participate in the forward movement of the launcher by a force input at its fingers resulting from the displacement of the movable core towards the rear.
• the pinion then arrives at the crown C of the engine.
• if the pinion via its teeth can penetrate directly into the crown C, more precisely in the teeth thereof, to mesh with the crown C, then the launcher continues its progression until the movable core abuts against the fixed core.
• the pinion may also be in the tooth against tooth position against the crown. In this case, the pinion is locked in translation and in rotation. In this position, the armature provides a torque proportional to the low intensity current because the starter is still in the pre-rotation phase. Thus, the electric motor exerts a rotational torque on the pinion and the launcher via the splines carried by the armature shaft 100. Being locked in translation, the driver will turn so as to push the fork 13 towards the rear which is no longer able to lock in rotation the coach. The fork can be pushed back because the coil 2a of the contactor has a lower force than the force exerted by the notches on the fork. When the pinion turning, finds an opening in the motor ring, it enters pushed by the axial force of the fork generated by the attraction of the movable core by the solenoid 2a.
  The value of the intensity to be passed in the first power circuit is dimensioned so that the pinion rotates in phase tooth / tooth, that is to say that the armature has the necessary torque for the pinion to make skip the notches and push the fork back. The value of this intensity is a function of the angle of the helical grooves, the shape of the notches and the dimensioning of the solenoid 2a.
  Thus, if before meshing with the crown C, the pinion abuts against the crown C, the pinion begins to exert a torque on the notches such that the teeth 22 will jump notches by rolling back the fork 13. The pinion can then turn and enter the crown. The movement is at low speed due to the slow speed rotation of the electric motor. The wear is thus reduced because of the low impact that the pinion makes when it comes into contact with the crown due to its low axial speed.
  The means of cooperation between the launcher and the fork, which form in the figures illustrated means for locking in rotation, are therefore of the disengageable type; the launcher being movable in translation and fixed in rotation during the aforementioned movement, while the launcher shaft 100 is rotatable and fixed in translation which allows the launcher to advance axially via the aforementioned helical grooves.
  The contactor 2 thus becomes a part of reduced size and its specification becomes independent of the design of the launcher.
• once the pinion 1 has managed to get into the crown C under the effect of armature rotation, it continues its course forward under the effect of the rotation of the armature.
• at the relay, the movable core abuts against the fixed core, which has the effect, on the one hand, of closing the power contact between C3 and C4 via the second wafer and on the other hand, disengage the fork from the launcher notches. The pinion can reach the end of the race against the stop of the shaft while being released from the fork. The locking in rotation is thus disengageable when the pinion 1 abuts against the starter ring.
• the power contact C3 and C4 being closed via the second wafer, the armature of the electric motor is then powered under full power. It can therefore drive the crown C to start the engine.
• during a decompression of the engine during the start-up phase, the crown C becomes driving relative to the starter pinion. This phase is called freewheeling phase during which the pinion tends to screw on the helical teeth which has the effect of backward.
• the two shoes 290 provided at the base of the fork have the function of avoiding too great a recoil of the launcher during the freewheeling phase during which the pinion tends to screw as previously described. In the absence of these shoes 290, this recoil would have the effect of bringing the notches of the coach into contact with the fingers of the fork which would cause wear and noise. These pads come (Figure31) bearing on a flange 310 located on the periphery of the coach. The shape of the arms of the fork that supports these fingers and pads is such that the pads can be in contact with the coach when the fork is in the pivoting position or maximum rotation.

After opening the switch using the ignition key, the coil 2a is de-energized which has the effect of canceling the attractive force on the mobile core 2b. Fork return spring 17 assisted springs 18, 20 and 21 respectively pressing the fork and the movable core 2b forces the movable core to disengage and resume its rest position. The movable axis 40, integral with the core, draws with it the wafer P2. The excess thickness of the strip 23 abuts on one face of the plate P1. The angle of the slope of this excess thickness is dimensioned (about 40 °) so that the force required for the sipe to sag is greater than the resistance force to the contact opening produced between the plate P1 and the contacts C1 and C2. Thus, the plate P1 will follow the moving axis and the two power circuits will open simultaneously. When the plate P1 arrives at the fixed core, it is stopped while the moving axis always moves back. The coverslip then collapses, the force required for this collapse is provided by the springs 18 and 21. The extra thickness passes on the other side of the wafer and the coverslip resumes its initial position with respect to the wafer P1.

Thus, the rotational locking of the launcher and the management of the tooth against tooth position are performed by the notching system arranged on the one hand, on the rear face of the driver and on the other hand, on the front end of the the base of the fork. The launcher is returned to its rest position by means of the fork and the re-screwing during the freewheel phase on the splines of the armature shaft. The rest position is maintained by the return spring 17 located between the relay and the fork, just as in a traditional device.

The relay is no longer dimensioned to develop a thrust force. It is not very dependent on the mass of the launcher. It is sized to overcome, in the initial position, the effort exerted by the return spring 17 on the movable core. Subsequently, the solenoid 2a will have the power to overcome the springs 18 of the launcher, and crush 20, 21 of the contact pads in the variants where they are present. The mass gain of copper, magnetic materials, bulk, cost and development time are the direct advantages of this undersizing.

It is good to note that the act of turning the armature allows to catch all functional games and when the pinion passes for the ^1st time her marriage to the crown - approach phase - there are no shock as a conventional starter which requires less the mechanics of the starter.

Thus, in accordance with the present invention, the relay constituted by the electromagnetic contactor comprising the call, hold and pre-rotation coils is no longer dimensioned to develop a forward thrust force of the coach for the purposes meshing of the pinion in the crown C of the engine. Its dimensioning is little dependent on the mass of the launcher. It is dimensioned only to be able to overcome the effort exerted by the return springs on the mobile core when the solenoid is energized. It must also be dimensioned to allow the launcher to rotate when the pinion is in the tooth-to-tooth position by a rearward movement of the fork that can disengage from the wolf teeth by a slight displacement of the movable core forward. .

The gain in mass of copper, magnetic materials, bulk, cost and development time are the direct advantages of this under-sized contactor according to the present invention. Another advantage of this invention is that the starter does not have additional parts for the implementation of a contactor and a trainer according to the invention.
However, penetration of the launcher by pre-rotation of the armature may require the establishment in the relay of a two-contact switching system, in the case where the pre-rotation intensity exceeds the limit given by the control system (ignition key), one to let a low power (current limited to 80 amperes), the other to let all the power available.

According to another embodiment, a starter without spring against tooth and pre-rotation device can be envisaged. Thus, upon activation of the ignition key, all the power is allocated to the armature. A single contact relay would be sufficient. In this embodiment without tooth-to-tooth spring, it is the strong acceleration of the armature at startup that would advance the launcher itself by inertia coming to screw on the helical grooves of the armature shaft without locking in rotation by a fork. The problem of the tooth against tooth would no longer appear thanks to the permanent rotation of the pinion during its forward stroke by screwing on the armature shaft. We find in this variant the principle of starting the inertia starters.

Figures 39 and 40 illustrate another embodiment of the pre-rotation according to the invention.

In this embodiment, as shown in FIG. 40, during the closing of the switch 35, a current is passed through the holding coil 37 and the calling coil 36. This current, in particular that passing through the call coil 36, must be sufficient to activate the electric motor M in a pre-rotation movement that is to say that it must be sufficient to allow the electric motor M to overcome the friction forces that appear during the starting the starter. These friction forces appear for example at the splines cooperating with the launcher, at the fork bearing against the throat of the coach and in particular depends on the forms of the means of cooperation between the teeth of the fork and the inner face of the throat of the trainer for its locking in rotation as described above.
As soon as the contact pad P0 comes into contact with the power pads C1 and C2, the electric motor is activated at full power and the holding coil remains active while the call coil 36 is short-circuited.

FIG. 39 illustrates a contactor allowing efficient pre-rotation and which uses only a call coil 36 and hold 37 without using an additional resistive element such as a call and pre-rotation coil 39 as described. previously. Such a contactor has the advantage of using only two springs, namely a return spring 18 of the core and a contact spring 20 to ensure good contact between the contact pad P0 and the power pads C1 and C2.

In such a contactor, it is no longer necessary to have a spring tooth against tooth against the crown because this configuration is now managed by the fork and the pre-rotation. In this case, as described above, the pinion is locked in translation and in rotation. In this position, the armature provides a torque proportional to the low intensity current because the starter is still in the pre-rotation phase. Thus, the electric motor exerts a rotational torque on the pinion and the launcher via the splines carried by the armature shaft 100. Being locked in translation, the driver will turn so as to push the fork 13 towards the rear which is no longer able to lock in rotation the coach. The fork can be pushed back because the coil 2a of the contactor has a lower force than the force exerted by the notches on the fork 13. When the pinion turning, found an opening in the motor ring, it enters the pushed by the axial force of the fork generated by the attraction of the movable core by the solenoid 2a.

Similarly, in such a contactor, it is no longer necessary to use a breaking spring because the movable core 2b has a movable axis 40 which is integral with it in translation (hitched axis) so that it is the spring of reminder 18 which acts as a breaking spring.

The fork 13 is identical to that described in FIGS. 3, 4, 29 and 30 and allows a rotational locking of a launcher similar to that described in FIGS. 3, 4, 31, 32, 33.

Advantageously, during the pre-rotation, in addition to the rotation locking function of the launcher, the fork also helps the launcher to move forward thanks to the force exerted to the rear by the mobile core 2b under the effect of the magnetic field created by the current flowing in the solenoid 2a. This promotes the movement of the launcher by reducing the risk of jamming at the flutes.

The connection terminal of the electric motor of Figure 1 is replaced by an internal connection.
This is made possible by the fact that the rear bearing 26 is made of plastic so that the electric tracks are obtained by the overmoulding technique.
The rear bearing has a receiving sleeve of the rear end of the shaft 101. This sleeve internally carries a bearing in which is mounted rotatably the rear end of the shaft 101. The resistance 39, for example aluminum, is wound and is connected to the contacts C1 and C2.
In FIG. 3, the resistor is wound around windings 36 and 37.

As a result, the two yokes can belong to the same room or be integral with each other. The support 4 can be obtained by deformation of material being for example stamped sheet. It then comprises a fastening and centering flange instead of the deeper fixing zone of FIG. 1. The rear bearing of the electric motor advantageously constitutes the closing plate of the contactor. The rear bearing is then, in one embodiment, equipped with one or more electrical tracks, for example by overmolding. This or these tracks connect at least one fixed contact to the electric motor so that the cable of FIG. 1 can be removed.

The rear bearing 26 is attached by clipping 29 on the yoke 25 and closes it on the side opposite the support 4. For example the yoke 25 has holes and the bearing 26 of the elastically deformable tongues each carrying a lug with a ramp.
When we put the tongues of the bearing 26 in the cylinder head, they retract downwards thanks to the ramps protruding lugs. When the lugs arrive in front of the holes, the tabs unfold and the lugs go into the holes. Several pins and holes are provided.
The yoke 25 has the shape shown in FIG. 6 and has two receiving recesses respectively of the electric motor M and the contactor 2.
Here the yoke 25 is formed in favor of a closed metal strip, for example of generally oval shape, which is deformed using jaws in contact with removable cores delimiting the cavities.
The strip can be opened at the origin and closed by buttoning as described in US-A-4 309 815 or by welding. The cylinder head is made of magnetic material, for example sheet metal.
In a variant, the two yokes are fixed to one another, for example by welding.
The support 4 is made of sheet metal and is obtained by deformation of material without recovery operation, only the anticorrosion surface treatment being optionally performed.
For example, pre-coated sheets may be used. The support 4 (FIG. 5) is made by stamping and comprises a nose-shaped front portion 43 with a sleeve 42 internally bearing a support bearing of the front end of the launcher. The nose 43 has an opening 44. for the passage of the starter ring.
The warhead is connected at the rear to a fastening flange 45 of transverse orientation, that is to say perpendicular to the axis of rotation XX of the shaft 100-101.
The simple-shaped flange replaces the more complex attachment zone of FIG. 1. Rigidizing ribs 47 are present between the flange 45 and the nose 43.
41 hollow studs are made for fixing and centering of the support on the housing of the engine of the vehicle and thus constitute the aforementioned third fastening and centering means.
46 shows a spherical cap for creating a clearance from the front end of the movable core 2b of the contactor 2 whose number of springs is reduced compared to that of Figure 1. The fixed core 2d, 2d is also simplified since it consists of a simple plate without frustoconical portion as in Figure 1. It is the same for the mobile core 2b.
A support washer is provided for the support of the return spring 18.
The first means of fixing and centering the support 4 are used for fixing the yoke 25.
Alternatively the ogive 43 is pressed sheet metal and the flange 43 aluminum.
The yoke 25 can be stamped to form hollow fitting means for penetration of tabs from the cylinder head and formation of centering means.
Here the yoke 25 is fixed by crimping on the support 4 as visible for example in Figures 8 to 24.
These embodiments are also applicable to the fixing of the cylinder head on the rear bearing.
These solutions are economical because it avoids having recourse as in Figure 1 to an expensive screwdriver investment point of view if one wants to take into account precise screwing parameters.
In addition, this type of screw or tie assembly is cumbersome and poses additional constraints in the automation of assembly stations (distribution of long or small parts, little space for the passage of the heads of the screwdrivers). Moreover, the cycle time of a screwing operation is traditionally long.

In Figures 8 to 24 we do not find these disadvantages. In these figures is deformed a portion of the cylinder head 25 to immobilize the other components so that the size of the starter is reduced. Thus the support 4 or the bearing 26 may have holes traversed axially by tabs of the cylinder head whose free ends are folded in contact with the support or the bearing.
Reference 28 in Figure 3 symbolizes such an assembly.

As a variant (FIG. 8), the support 4 or the bearing 26 have cavities 70, for example in the form of recesses, in which are bent the beaks 71, 72 obtained by cutting into the cylinder head 25. The beaks rest on the lateral edges of the hollows thus achieving angular indexing and a rotational stop.

In FIG. 9 the two beaks meet to form a band of material 73 which is deformed in the cavity 70.

In Figures 10 to 12 there is formed such a web of material but the recess 170 extends parallel to the axis X-X of the shaft 101, instead of being perpendicular thereto. The band 73 is formed with recesses 74,75 vis-à-vis. Axial and radial fixation is thus obtained without the need for casing.

In FIG. 14, the wall of the piece 26 (or alternatively 4) is locally deformed at 373 by pushing it inside the hollow 270 by means of a punch here of prismatic shape in a conical or cylindrical variant. the structures can be reversed, the yoke being locally deformed to penetrate into the recess 70, 170, 270 forming a cavity so that the bearing 26 can be made of plastic.

In FIG. 13, a local deformation of material is represented by means of a cylindrical punch showing a deformation of material 273 penetrating, for example, in the recess 270.

As an alternative to FIG. 15, only one recess 470 is provided, the upper part of FIG. 10, that is to say the recess 74 being eliminated. In a variant of FIG. 16, the recess 470 of FIG. 15 is open and two tabs 471, 472 are formed, the reference 473 being a solid part.
Alternatively in the figures in Figure 17 instead of crossing a hole, the axial tabs 77 pass through a recess 76 in the form of a notch and the pre-cut side edges 77 'of the tabs, for example of the yoke 25, are folded to the contact lateral edges of the notches made in the support or the bearing.
As a variant, the lateral edges 77 'consist of protuberances connected to one another by a removal of material and the protuberances are crushed.
Alternatively Figure 19 is a casing. The bearing 26 has for example bearing protrusions 79 for the lower face of the yoke 25.
The piece 26 has a flange 78 folded radially by crimping or folding in contact with the upper face of the yoke 25.

In a variant (FIG. 20), the flange is axially deformed at 178 in contact with the upper face of the yoke 25. As a variant FIG. 21, it is formed using a punch a cut in the collar with an inclined leg 278 folded in contact with the upper face of the cylinder head.
As a variant, an inclined lug 378 (FIGS. 22 to 24) is folded in contact with the upper face of the yoke 25.
All that has just been described is applicable to the flange 45 of the support 4.
The coupling device between the driver 12 and the pinion comprises in an exemplary embodiment a freewheel. This free wheel uses a large number of components due in particular to the presence of rollers each subjected to the action of a spring. The conical clutch coupling device allows a great simplification above.

Thanks to the invention and the rotational locking of the driver promotes the movement of the launcher by reducing the risk of jamming at the flutes. In connection with the previous figures we arrive at the most compact solution possible with a significant reduction in the number of components and weight. The solution is simple and economical.
Of course, the present invention is not limited to the described embodiments. In particular, the variant support is of the type of FIG. 1 and the two yokes can be distinct. A gear reducer is alternatively interposed between the two shafts and / or a cable is provided between the motor M and the contactor as in Figure 1.
The inductor of the electric motor M as a variant comprises a winding. Tie rods can connect the support to the rear bearing. The alternative brushes are axially oriented as in FIG.
Of course, the embodiments described above are also suitable for starters with inductors with magnets or coils, direct drive or with internal gear and ogive support or pinion type outgoing.

Claims (23)

1. Starter for a motor vehicle with a thermal engine and a starting ring of the thermal engine, comprising a starter head, provided with a driver (12) and a pinion (1), able to pass from a retracted idle position to an advanced position of meshing with the starting ring (C) of the motor vehicle thermal engine, an electric motor (M) provided with a shaft (101) able to drive a starter-head shaft (100) associated with the starter head (12), complementary helical flutes (9) acting locally between the internal periphery of the driver (12) and the external periphery of the starter-head shaft (100), an electromagnetic contactor (2) extending parallel to the electric motor (M) above it and comprising a movable core (2d), a fork (13) mounted for articulation at its top end on the movable core (2b) and at an intermediate point (11) on a support (4) of the electric motor (M) and electromagnetic contactor (2), in which the driver (12) comprises a groove for receiving the bottom end of the fork (13) delimited by two flanks (121, 122) and in which means are provided for making the electric motor turn at a slow speed in a first so-called pre-rotation phase and then at full power, characterised in that the starter head is rotationally locked by means of cooperation between the fork (13) and the driver (12) for its passage from its idle position to its position of meshing with the starting ring.
2. Starter according to Claim 1, characterised in that the cooperation means d are means of locking in rotation with cooperation of shapes.
3. Starter according to Claim 1, characterised in that the cooperation means are of the friction type.
4. Starter according to Claim 2, characterised in that, when the electromagnetic contactor (2) is supplied electrically, the fork (13) cooperates with the flank (121), referred to as the front flank of the fork reception groove (13), and in that the said front flank (121) is provided with circumferential corrugations (21).
5. Starter according to Claim 4, characterised in that the fork (13) has arms (293) with corrugations of complementary shape to those on the front flank (121).
6. Starter according to Claim 2, characterised in that the means of locking in rotation are of the ratchet tooth type.
7. Starter according to Claim 2, characterised in that the front flank (121) of the reception groove of the fork (13) comprises notches (320) and protrusions (321), whilst the fork (13) has projecting fingers (22) cooperating with the notches (320) for the rotational locking of the starter head.
8. Starter according to Claim 1, characterised in that the front flank (121) of the fork (13) reception groove cooperates with a ring (15) mounted so as to slide axially on the barrel of the driver.
9. Starter according to the preceding claim, characterised in that the ring (15) is mounted for articulation on the body (292) of the fork (13).
10. Starter according to Claim 1, characterised in that the fork (13) has at its end which cooperates with the groove of the driver at least one shoe (290) which cooperates with a rim (310) situated at the periphery of the driver when the starter head is meshed in the starting ring of the motor vehicle engine.
11. Starter according to Claim 1, characterised in that the cooperation means are disengageable.
12. Starter according to Claim 1, characterised in that the support (4) has a front part (43) made from sheet metal roughly in the shape of an ogive.
13. Starter according to Claim 12, characterised in that the front part is connected to a fixing and centring flange (45).
14. Starter according to Claim 13, characterised in that the sheet-metal support (4) is obtained by deformation of material, such as pressing, and in that the flange (45) is made in a single piece with the front part (43).
15. Starter according to Claim 1, characterised in that the electric motor (M) and contactor (2) each have a casing fixed to the other casing.
16. Starter according to Claim 15, characterised in that the two casings belong to one and the same piece (25).
17. Starter according to Claim 16, characterised in that the casing or two casings are closed on the opposite side to the support by a common piece (26) forming the rear bearing of the electric motor (M).
18. Starter according to Claim 1, characterised in that the means provided for making the electric motor (M) turn in pre-rotation and then at full power comprise two plates (P1, P2) carried by the movable core (2b), the first plate (P1), used during pre-rotation, is connected to two contacts (C1, C2), the first contact (C1) is connected to the resistive coil (39), the second contact (C2) is connected to the positive terminal of the battery, and then, during full power, the second plate (P2) is connected to two contacts (C3, C4), the third contact (C3) is connected to the resistive coil (39) and to the electric motor (M), and the fourth contact (C4) is connected to the positive terminal of the battery.
19. Starter according to Claim 1, characterised in that a contact plate (P0) is allowed to rock about the second fixed contact (C5) in order to cooperate with another fixed contact (C6) offset axially and connected to the positive terminal of the battery in order to supply the electric motor.
20. Starter according to Claim 18 or 19, characterised in that the movable shaft (23) comprises a blade (23) provided with a local protrusion which drives the contact plates (P0, P1) when the movable shaft (40) returns after opening of the control circuit of the contactor (2).
21. Starter according to Claim 1, characterised in that the electromagnetic contactor (2) comprises at least one plate (P3) able to rotate about the movable shaft (40) for putting the electric motor (M) in pre-rotation and then at full power.
22. Starter according to Claim 21, characterised in that the plate (P3) has two electrically connected studs, a first stud continuously electrically connected with a contact (C7) connected to the battery voltage, a second stud connected to a contact (C8) when the motor is pre-rotated, this second stud then coming into contact with a third contact (C9), after rotation of the said plate (P3), in order to provide full power to the starter, the second and third contacts (C8, C9) being connected together by the pre-rotation resistive coil (39), the contact (C9) being connected to the electric motor (M).
23. Starter according to Claim 1, characterised in that the pinion (1) of the starter head is connected to the driver by a device for coupling to the conical clutch.

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