EP2547896A2

EP2547896A2 - Combustion engine starter with a pinion protruding from the housing of the starter

Info

Publication number: EP2547896A2
Application number: EP11713005A
Authority: EP
Inventors: Guillaume Seillier; Laurent Boisserenq
Original assignee: Valeo Equipements Electriques Moteur SAS
Current assignee: Valeo Equipements Electriques Moteur SAS
Priority date: 2010-03-19
Filing date: 2011-03-15
Publication date: 2013-01-23
Anticipated expiration: 2031-03-15
Also published as: CN102812234B; WO2011114052A2; FR2957638A1; FR2957638B1; EP2547896B1; JP2013522529A; US20130091967A1; WO2011114052A3; US9080543B2; CN102812234A

Abstract

The combustion engine starter with output pinion (18) comprises a front bearing (12) provided with a front face (120) having an opening (312), a drive assembly equipped with a bush (26) passing through the opening (312) and bearing the output pinion (18) outside the front bearing (12), complementary splines (67,167) which act between the front end of the bush (26) and at the internal periphery of the output pinion (18), a groove (64, 164) which interrupts the splines (67) of the bush (26) in order to mount a stop (60, 160) for immobilizing the pinion, a play-compensating spring (61) urging the pinion into contact with the stop (60, 160) formed by a spring ring which has a height greater than its thickness and which is housed with radial clearance at least partially in an annular recess (62) made in the front face (183) of the pinion (18); the internal periphery of the spring ring (60, 160) being mounted in the groove (64, 164) in the bush (26). Application: combustion engine starter of a motor vehicle.

Description

Thermal Motor Starter with Outgoing Pinion Field of the Invention

The present invention relates to a thermal engine starter with an outgoing pinion starter, in particular for a motor vehicle.

State of the art

Such a starter is described, for example, in documents FR 2 745 855 and US Pat. No. 4,818,889 to which reference will be made for further details.

This starter comprises a housing inside which is housed an electric motor, whose shaft is intended to drive in rotation a starter output shaft carrying a gear meshing belonging to a launcher comprising an outgoing gear, which is arranged to the outside of the housing.

Depending on the application, the output shaft of the starter is, as in FR 2,745,885, confused with the shaft of the electric motor, or as in US 4,818,889 separate from the shaft of the electric motor.

The conventional starter housing has a front bearing configured to attach the starter to a fixed portion, a cylinder head, and a rear bearing for rotatably mounting the rear end of the electric motor shaft.

The yoke carries the inductor, such as magnets or windings, the electric motor surrounding a wound armature integral with the shaft of the engine. This yoke is interposed axially between the front and rear bearings. In documents FR 2 745 855 and US Pat. No. 4,818,889, the launcher has a metal bush having a front end passing through an opening of the front bearing and the pinion is located outside the front bearing on the front end of this socket. A freewheel roller is interposed between the driver and the rear end of the sleeve. The driver is configured to engage the starter output shaft via a spline and helical complementary groove connection. When the electric motor rotates, the launcher and the pinion can thus move axially and in rotation because the starter output shaft carries the helical meshing drive.

This pinion in the advanced position is intended to engage with the teeth of a ring gear start connected directly or elastically to the crankshaft of the engine to start.

In the document FR 2 745 885 the pinion is integral with the front end of the sleeve so that the number of teeth of the pinion is limited and the pinion is in the same material as the sleeve constituting the cylindrical main body of the pinion.

In US 4,818,889, these disadvantages do not exist because the pinion is distinct from the bushing having a nose at its front end. The pinion is rotatably connected to the nose by a connection with complementary splines occurring between the outer periphery of the nose and the inner periphery of the pinion. This connection allows axial movement of the pinion relative to the socket. A stop is provided to limit the axial movement of the pinion, as well as a snap ring to axially immobilize the abutment in combination with a catch-up spring games resting on a shoulder of the nose to axially bias the pinion in contact with stop. This spring is compressed during assembly of the stop and the ring. The rod is received in a housing and in a semi-cylindrical groove respectively formed in the abutment and in the nose.

Three additional pieces are used to bring back the pinion. In document US 2002/0047269 there is also provided an additional piece for retaining an elastic ring, namely a lid mounted in a groove made in an extra thickness, that has the front pinion. Axial play exists between the cover and the front end of the socket. The pinion is further configured at the rear to have an extra thickness adjacent to a stop in the sleeve. This stop prevents inclination of the pinion relative to the socket. In all cases, the axial bulk is increased.

It is desirable to reduce the number of parts and reduce

axial size. Object of the invention

The present invention aims to meet this desire.

According to the invention, a heat engine starter with a centrally perforated pinion gear, in particular for a motor vehicle, comprising a casing provided with a front bearing provided with a front face provided with an opening, a launcher having a socket having a front end passing through the opening of the front bearing and carrying the pinion protruding outside the front bearing, complementary splines belonging respectively to the outer periphery of the front end of the bushing and to the inner periphery of the outgoing gear, a groove; interrupting the splines of the bushing for mounting an axially immobilizing pinion of the pinion, a catch spring of the games urging the pinion in contact with the stop, in which, on the one hand, the front end of the sleeve presents a shoulder for supporting the rear end of the spring and secondly, the pinion has at the rear a blind housing for mounting the spring, is characterized in the abutment is constituted by an elastic ring of height greater than its thickness, in that the elastic ring is housed with radial clearance at least partly in an annular recess made in the front face of the pinion and in that the periphery internal ring is mounted in the throat of the socket.

Thanks to the invention reduces the number of parts for the assembly of the pinion with the sleeve; the ring of the prior art being removed. The stop is simplified because it consists of an elastic ring less solid than the abutment of the prior art and of greater diameter.

In addition, the solution, on the one hand, is less bulky axially due to the mounting of the elastic ring at least partly in the recess and on the other hand, avoids ejection of the stop under the effect of the centrifugal force. by cooperation of the elastic ring with the outer rim of the chambering.

The solution is robust and reliable because it avoids disconnection of the pinion relative to the socket.

Moreover the manufacture of the pinion and the socket is easy.

The outer diameter of the pinion can have the desired value.

Thanks to the invention can therefore increase the size and the number of teeth of the pinion, for example to drive and accompany the engine at higher speed or to have a better operating point.

The resistance of the pinion is not unduly weakened and reduced

axial size.

According to other characteristics taken separately or in combination:

- The outer periphery of the elastic ring is housed entirely in the recess;

the elastic ring is split;

the elastic ring is a circlip;

the elastic ring has resilient tabs inclined at its inner periphery;

the outer diameter of the elastic ring is greater than the external diameter of the catch-up spring of the games;

the opening of the front bearing is constituted by the internal bore of a sleeve of the front bearing directed in the opposite direction to the pinion;

- the sides of the throat are parallel.

In all cases, an elastic ring of the standard type that is economical and not conditioned by the effects of the centrifugal force is used. The speed of rotation of the starter is not conditioned by the deformation and / or the opening of the elastic ring.

The material of the elastic ring or its configuration is not conditioned by the speed of rotation of the starter.

Other features and advantages of the invention will appear on reading the following description with reference to the accompanying drawings.

Brief description of the drawings

- Figure 1 is a partial perspective view, with local cutaway material, a thermal motor starter equipped with a pinion output according to a first embodiment of the invention, said pinion being in the retracted position of rest;

- Figure 2 is a partial half view in axial section of the starter of Figure 1;

- Figure 3 is a perspective view of the elastic ring of Figures 1 and 2 mounted in the recess of the pinion;

Figure 4 is a front view showing the outgoing pinion assembled at the free end of the launcher for a second embodiment of the invention;

FIG. 5 is a partial sectional view of the assembly of FIG. 4. Description of embodiments of the invention

In figs 1 to 5 the elements common to the invention and to those of document FR 2 745 855 will be assigned the same reference signs.

In Figures 1 and 2 we see the front end of the starter 10 of a combustion engine of a motor vehicle.

Thus have seen in 12 the front bearing of the housing of this starter 10, in 26 the front part of the starter of the starter, in 18 the pinion coming out of the starter of the starter. starter 10, 36 the smooth axial front end of the electric motor shaft of the starter, the axis is referenced XX in Figure 2.

The pinion 18 is said pinion coming out because it is located outside the housing 12. In the following description an orientation of the rear to the front corresponds in Figure 1 to a right-to-left orientation.

In the remainder of the description the transverse, axial and radial orientations will be defined with respect to the axis XX, which is the axis of axial symmetry of the portion 26 and the end 36. This axis also defines the center of an opening 312 made in the front face 120 of the front bearing 12.

In the figures, the shaft of the electric motor, the rear end of the launcher and the link with splines and helical grooves are not modified.

complementary between the shaft of the electric motor and the trainer of this document FR 2 745 855.

The front portion 26 of the launcher is therefore a main body of great hardness because the rear end of this body forms a track for the rollers of the free wheel intervening between the body and the launcher coach.

In the figures and in FR 2,745,855 this body is cylindrical in shape of axis X-X of axial symmetry. This body 26 is internally hollow for receiving the end 36 of the shaft of the electric motor, thus penetrating the body 26.

This cylindrical body 26 is metallic and therefore consists of a sleeve, which according to a characteristic is distinct from the pinion 18.

The front end of the bushing 26 passes through, as described hereinafter, the opening 312 of the bearing 12, which opens into the front face 120 of the bearing 12. The front bearing 12 is of hollow form and is configured to be fixed on a fixed part and to carry an electromagnetic contactor (not visible). Here it is metallic, for example aluminum to obtain the desired shapes. The pinion 18 is arranged to be movable in rotation and axially between a rest position visible in FIGS. 1 and 2, and an advanced position, in which the pinion meshes with the starter ring 1 18 (FIG. 2) integral with a flange, such as a flywheel, connected rigidly or

elastically to the crankshaft of the engine to start it.

The axial displacements of the pinion are here controlled by a fork, called fork in the document FR 2,745,855, acting on the coach of the launcher. This fork is articulated at an intermediate point on the front bearing 12 of the housing. A splined connection and helical grooves

complementary intervenes between the shaft of the electric motor and the coach of the launcher surrounding locally this tree.

For more details, see document FR 2 745 855.

The fork is intended to be actuated by the electromagnetic contactor described for example in the documents WO 2004/088126 and WO 03/002870 to which reference will be made for more details; these documents also show the electric motor as well as the rear bearing and the yoke of the starter. This range is connected, in known manner and visible for example in FIG. 6 of document WO 2004/088126, at its end

superior to the movable core of the contactor configured to act on a push rod-shaped, carrying a movable plate-shaped contact, arranged to come into contact with two power supply terminals for powering the electric motor of the starter in order to rotate the starter ring 1 18 of the engine of the motor vehicle when the pinion 18 and the sleeve 26 are in the advanced position and engaged with this ring. One of the terminals is intended to be electrically connected to the positive terminal of the battery of the motor vehicle. The other terminal is intended to be electrically connected to the electric motor of the starter. The contactor also comprises a fixed core, at least one coil and springs, in particular return to return the movable core in the rest position. When the driver acts on the ignition key or introduces a starter card, the closing of a contact and a

powering the coil of the contactor so that the movable core is moved towards the fixed core and moves the fork and the pusher. At the end of a given stroke the movable contact comes into electrical contact with the terminals and the electric motor is electrically powered and rotates the output shaft of the starter.

The bushing 26 is guided axially by bearing means 137, 37 'acting, on the one hand, between the bushing 26 and the bearing 12 and, on the other hand, between the bushing 26 and the smooth end 36 of the shaft of the electric motor housed in the bushing 26. The bearing means 37 'intervening between the smooth outer periphery of the axial end 36 and the stepped internal periphery in diameter of the bushing 26 may consist of bushings, as in the FR documents.

2,745,885 and 4,818,889.

The bearing means 137 acting between the outer periphery of the bushing 26, also staggered in diameter, and the front bearing 12 may consist of a ball bearing as in US Pat. No. 4,818,889, in a roller bearing or in a bearing such as in document FR 2 745 855.

The bearing means 37 ', 137 here consist of axial needle roller bearings of the sleeve 26. It all depends on the applications.

As best seen in Figures 1 and 2, the sleeve 26 has a front end 126, 127, which passes through the opening 312 of the front bearing 12 and which carries the pinion 18 outward of the front bearing 12. This pinion 18 is pierced centrally. The edge of the hole constitutes the inner periphery of the pinion 18.

The mounting of the pinion 18 on this front end 126, 127 comprises: - Complementary grooves 67, 167 respectively belonging to the outer periphery of the front end of the sleeve and the inner periphery of the outgoing pinion;

a stop 60 of axial immobilization of the pinion 18;

- A groove 64 interrupting the grooves 67 of the sleeve for mounting the stop 60;

a spring 61 for catching up the clearances urging the pinion 18 in contact with the stop 60;

a shoulder 130 belonging to the front end of the bushing for supporting the rear end of the spring 61;

a blind housing 261 for mounting the catch spring 61, which the pinion 18 has at the rear.

The spring 61 consists in the embodiment of Figure 2 in a coil spring, also called coil spring.

In FIGS. 1 to 5 this assembly involves an abutment 60, 160 and a spring 61. The front end 126, 127 of the sleeve 26 is staggered in diameter. More precisely, this front end of the bushing 26 has a first section 127 extended axially by a second section 126 of reduced external diameter with respect to that of the first section 127. This second section 126 belongs to the free end of the casing 26 of the launcher .

The front face 128 of this section 126 is closed (Figures 1 and 2).

As a variant, the second section 126 is internally closed at the front by a washer as in FIG. 1 of document FR 2 745 855.

According to one characteristic, the pinion 18 is attached to the second section 126. The front face 128 of this section 126 extends in axial projection with respect to the front face 183 of the pinion 18.

All these configurations are made possible because the pinion 18 is, according to a feature, centrally and distinct hole of the sleeve 26 being mounted and attached to the second section 126 by the above assembly. The outer diameter of the pinion 18 is here greater than the outer diameter of the sleeve 26, that is to say the outer diameter of the first section 127.

In this embodiment, the diameter of the root circle of the pinion 18 is greater than the external diameter of the first section 127. The number of teeth of the pinion 18 is therefore not imposed by the size of the sleeve 26.

The second section 126 is intended to extend outside the starter housing. In this embodiment it is implanted for the most part outside the front bearing 12 when the pinion 18 is in the rest position. When the pinion 18 moves axially and in rotation from its rest position to its advanced meshing position with the ring 1 18, the second section 126 is allowed to extend entirely outside the front bearing 12 and the first section 127 partly outside this bearing 12.

The front end 126, 127 of the bushing thus passes through the front bearing 12.

The outer diameter of this second section 126 is smaller than the outer diameter of the first section 127.

The internal diameter of the first section 127 is greater than the internal diameter of the second section 126.

The outer diameter of the second section 126 is greater than the internal diameter of the first section 127.

These arrangements make it possible to have the quantity of material required for mounting the pinion 18 on the second section 126.

This also allows mounting of the needle bearings 37 ', 137.

The needle bearing 137 for axial guiding of the bushing 26 intervenes between the outer periphery of the first section 127 and the internal periphery stepped in diameter with a sleeve 1 12, which the front bearing 12 has centrally. The bearing 12 is thus centrally perforated. , thanks to the internal bore 312 of the sleeve 1 12, for passage of the sections 127, 126 of the sleeve 26 and the smooth front portion 36. The sleeve 1 12 is directed axially inwardly of the bearing 12, c opposite direction to the pinion 18. This makes it possible to obtain the desired size for the pinion 18, while having a front bearing with a front face 120 provided with an opening 312, which does not determine the size of the pinion because the sleeve January 12 is directed inwards. In the retracted position of rest (Figure 1) the pinion 18 is in contact with a bearing carried by the front bearing 12 and the spring 61 is not fully compressed; its turns not being joined. In the embodiment shown, this support consists of a washer 181 mounted in an annular transverse housing 212 formed in the front face 120 of the bearing 12 around the opening 312.

This opening 312 and this housing affect an orientation wall

axial transverse that presents the front face 120 of the bearing 12 of hollow form as visible in Figures 1 and 2.

In this embodiment of Figure 2 the washer 181 is housed

entirely in the housing 212 for reducing the axial size. In a variant, it is mounted for the most part in this housing 212. In a variant, it is bonded to the front face 120 of the bearing 12.

The rear face of the pinion 18 is closed by a washer 180 attached to the rear face of the pinion having an annular notch (not referenced) for this purpose. This produces a tight contact when the pinion 18 is in the rest position, the washers 180, 181 then being in contact with each other. Note that in Figure 3 the washer 180 is not yet reported to the rear of the pinion 18

The washer 181 is in an elastomeric embodiment for reducing noise. The washer 180 is rigid.

The housing 212 is of cylindrical shape. It is delimited by a face

of transverse orientation relative to the axis XX of the sleeve 26 and the end 36. This face is extended at its outer periphery by an axially oriented face relative to the axis XX for centering the washer 181 . The housing 212 is centrally perforated because the internal bore 312 of the sleeve 1 12 opens into this housing 212 for mounting the washer 181. In a variant, the washer 181 is omitted and the transverse face of the housing 212 is machined to constitute the support of the rear end of the pinion 18. In a variant, the front face 120 of the bearing 12 is machined to form the support of the end. rear of the pinion 18. The direct contact between the pinion 18 and the transverse face of the housing 212, more or less deep, or the front face 120 of the bearing 12, reduces the length of the chain of dimensions.

Due to the presence of the washer 180, a blind recess therefore exists between two consecutive teeth of the pinion 18. These recesses open at the front face 183 of the pinion 18.

In a variant, the washer 180 is integral with the pinion 18.

Of course, alternatively, the washer 180 is removed.

The teeth of the pinion 18 are chamfered at the front face 183 of the pinion 18.

The pinion 18 is in one embodiment in the same material as that of the sleeve 26 here metal.

In a variant, the material of the pinion 18 is different from that of the sleeve 26. In one embodiment, the pinion 18 is made of sintered material.

This is made possible because the pinion 18 is mounted on the section 126 by a splined mounting 67, 167. This mounting of the pinion 18 on the section 126 of the sleeve 26 involves, according to one feature, a simplified stop under the form of an elastic ring 60, 160.

According to one characteristic, the height of this elastic ring 60, 160 is greater than its thickness.

The grooves 67, 167 are made in a complementary manner

respectively at the outer periphery of the second section 126 of the sleeve 26 and the inner periphery of the pinion 18 centrally perforated for the passage of the second section 126 chamfered free end. The grooves 67, 167 are axially oriented, that is to say straight splines, for mounting with possibility of axial displacement of the pinion 18 relative to the second section 126 and rotational connection therewith. This elastic ring 60, 160 is, according to a feature housed with radial clearance at least partly in an annular recess 62 formed in the front face 183 of the pinion 18. The recess 62 is of transverse orientation.

In FIGS. 2 and 5 the outer periphery of the ring 60, 160 is housed entirely in the recess 62. The front face 183 of the pinion 18 is thus cut to form the recess 62, locally decreasing the thickness of the pinion 18. inner periphery of the recess 62 is delimited by the central hole of the pinion 18.

The grooves 167 open at the front in the recess 62 at the inner periphery of this recess 62, which is axially reduced in size because the height of the elastic ring 60, 160 is greater than its thickness. In all cases the resistance of the pinion is not unduly weakened. The pinion is simplified compared to that of the US document

2002/0047269 because it does not have extra thickness. It is also lighter.

This arrangement reduces the axial size of the assembly of the pinion 18 on the portion 126 of the front end of the sleeve 26. In addition, the number of parts is not increased. The inner periphery of the elastic ring 60, 160 is, according to a

characteristic, mounted in a groove 64, 164 made in the grooves 67 of the second section 126.

The grooves 64, 164 are located in the vicinity of the front face 1 28 of the second section 126.

The grooves 67 are thus interrupted at the front by the groove 64, 164.

The groove 64, 164 holds the ring 60, 160 axially, which is thus a locking and axial locking ring of the pinion 18. Note that the flanks of the groove 64, 164 are in Figures 2 and 5 parallel and are perpendicular to the axis XX that is to say transverse orientation.

The grooves 67, 167 open respectively in the front face 128 of the section 126 and in the recess 62 of the front face 183 of the pinion 18.

The rear end of the second section 126 is delimited by the front face 130 of the first section 127. The rear end of the second section 126 is provided with a groove 129 adjacent to the front face 130 of the section 127.

More precisely

The pinion 18 has centrally a cylindrical housing of axial orientation 261. Housing 261 is one-eyed. It opens at the rear of the pinion 18 being delimited by a cylindrical wall of axial orientation relative to the axis X-X. This wall is delimited at the front by a wall of form

generally semi-cylindrical for supporting the front end of the coil spring 61 mounted in the housing 261.

The rear end of the spring 61 bears on the front face 130 of the first section 127.

The front face 130 of the first section 127 thus constitutes a bearing shoulder for the rear end of the spring 61, which here is a catch spring games games biasing the pinion 18 in contact with the stop 60, 160.

The groove 129 is in a characteristic axially offset forwardly with respect to the front face 130 of the section 127 for centering the rear turn of the spring 61 and thus the rear end of the spring 61.

Thus the second section 126 has a groove 129 whose rear end is close to the front face 130 of the first section 127.

More specifically, as shown in Figure 2, a retaining surface (Not referenced) of the rear end of the spring 61 exists between the shoulder 130 and the groove 129 having a cylindrical bottom. The spring 61 being in this embodiment a helical spring, this retaining surface here has a length such that it centers the last turn of the spring 61 bearing on the shoulder 130. The semi-cylindrical wall of the housing 261 has a shape complementary to the front turn of the spring 61.

The axial length of the splines 167 of the pinion 18 is less than the axial length of the grooves 67 of the second section 126.

The grooves 67 of the section 126 open at the rear in the groove 129, whose depth is greater than or equal to the depth of the grooves 67 for machining thereof. The diameter of the bottom of the groove 129 is (FIG. 2) greater than the internal diameter of the section 127. This bottom 129 is delimited axially by two connecting flanks respectively to the retaining surface and to the flutes 67. The flank associated with the flutes 67 is inclined, while the other side associated with the retaining surface is generally of radial orientation.

The grooves 167 of the internal bore of the pinion 18 open at the front in the recess 62 and at the rear in the housing 261.

The axial length of the grooves 167 is in this embodiment greater than the axial length of the housing 261 and less than the length of the grooves 67.

The end of the section 126 extends in axial projection with respect to the front face 183 of the pinion 18.

In the embodiments of FIGS. 1 to 5, the radially oriented counterbore 62 is of annular shape and has a bottom of orientation transverse to the X-X axis. This bottom is extended at its outer periphery by a cylindrical rim axially oriented with respect to the X-X axis.

The diameter of the recess flange 62 is greater than that of the outer diameter of the elastic ring 60, 160. This diameter of the recess flange 62 is here close to the outer diameter of the ring 60, 160. A radial clearance therefore exists between this flange and the outer periphery of the elastic ring 60, 160.

A band of annular material thus exists between the outer periphery of the recess 62 formed by the recess flange 62 and the foot circle of the pinion 18.

The thickness of this band depends on the applications to have the mechanical strength required for the teeth of the pinion 18. This arrangement makes it easy to mount the ring 60, 160 in the recess 62 and in the groove 64, 164 concerned. It also makes it possible to retain radially the elastic ring 60, 160 in these overspeed of the starter. It avoids an ejection of the ring 60, 160 and disassembly of the pinion 18, knowing that this ring 60, 160 is sensitive to the phenomena of centrifugal force because its height is greater than its thickness.

The axial depth of the recess 62 is a function of the thickness of the ring 60, 160. Here the axial depth of the recess 62 is greater than or equal to the thickness of the ring 60, 160 for a good recovery of the ring. 60, 160 by the pinion 18 and a good radial retention of the ring 60, 160.

The thickness of the ring 60, 160 is smaller than the internal diameter of this ring 60, 160. The radial height of this ring 60, 160 is greater than the axial thickness of this ring.

The outer diameter of the recess 62 is greater than the diameter of the cylindrical wall of axial orientation of the housing 261 and therefore to that of the splines 67, 167. The outer diameter of the recess 62 is thus greater than the outer diameter of the spring 61 mounted in the housing 261. This spring 61 is here a helical spring type.

In both embodiments of Figures 2 and 5, the depth of the groove 64, 164 is a function of the depth of the grooves 67, 167.

The grooves 64, 164 are here deeper than the grooves 67, 167.

The spring 61 is used to compose the mounting sets and / or damping the shocks of the pinion 18, in particular when a tooth of the pinion 18 comes into contact with a tooth of the ring 1 18. This spring 61 therefore has a dual function. As can be seen in FIG. 2 in the retracted rest position of the pinion 18, the turns of the spring 61 are not contiguous; the front face of the washer 181 being offset axially forwardly relative to the shoulder 130. The spring 61 may have a great axial length while being well maintained in particular by the aforementioned restraint span. This spring 61 works in good conditions.

The spring 61 is also used to ensure the mounting of the elastic ring 60, 160 in the recess 62.

The assembly of the spring 61, the pinion 18 and the elastic ring 60, 160 is made final after assembly of the other elements of the starter. More precisely, the bushing 26 being in a position corresponding to the retracted rest position of the pinion 18 and therefore of the starter, in a first step, the spring 61 is axially threaded onto the section 126 projecting with respect to the bearing 12. This spring 61 to the end of this first step is supported on the shoulder 130 constituted by the front face 130 of the first section 127.

In a second step, the pinion 18 is axially threaded onto the section 126. At the end of this second step, the pinion abuts the spring 61.

In a third step, the pinion being by its front face 183 resting on an annular abutment centrally perforated for the passage of the elastic ring

60, 160, the electromagnetic contactor of the starter is electrically powered to move the movable core thereof and the fork.

The bushing is then moved forward. The spring 61 is compressed, the throat

64 is then accessible and recess 62 is disengaged which allows to easily mount the elastic ring in its groove 64, 164. Of course the length of the spring 61 is determined in such a way that it does not come to contiguous turn before the groove 64 is accessible.

In a fourth step, the power supply to the contactor is cut off so that the spring 61 expands and pushes the pinion axially forward so that the pinion bears against the rear face of the ring 60, 160 by the intermediate of its transverse orientation bottom of the recess 62.

The pinion then radially covers the ring 60 (FIG. 2). At the end we arrive in the position of Figure 2. The spring 61, bearing on the front face 130, pushes the pinion 18 for contact with the transverse bottom of the recess with the rear face of the ring 60, 160.

For the disassembly of the ring 60, 160 one proceeds as in the third step in order to have access to the ring 60, 160.

In the embodiment of Figures 1 to 3, the width of the groove 64 is generally equal to the thickness of the elastic ring 60.

In practice there is a set of mounting of the ring 60 in its groove 64 with parallel flanks. The inner periphery of the ring 60 is well retained by cooperation of shapes, in particular with the parallel flanks of the groove 64.

This retention is reliable because in this embodiment the groove 64 is deeper than the grooves 67. The machining of this groove 64 is easy.

It is made for example by turning.

The anchoring of the ring 60 in the groove 64 is robust.

The ring 60 of these FIGS. 1 to 3 consists of an open ring of the standard type with a slot, which separates the two circumferential ends of the ring.

In this embodiment, this split ring 60 consists of a circlip.

More specifically, the circumferential ends of the ring 60 are each provided with a hole (not referenced in FIGS. 1 and 3) for receiving the ends of the branches of a clamp, called a circlip plier, enabling the ring to be opened. and increase its diameter for mounting this ring in its groove 64 and for disassembly thereof. Thanks to the invention, the ring 60 mounted in its groove 64, is not ejected under the effect of centrifugal force even if the starter of the starter rotates at high speed because when opening it abuts on the cylindrical flange axial orientation of the recess 62. The recess allows to cover radially ring 18 and limits the opening of the elastic ring. The radial clearance between the ledge 62 and the external periphery of the ring 60 elastic, circlip-shaped, depends on the applications and in particular the speed of rotation of the starter of the starter. The solution is economical, the ring 60 of axial locking pinion 18 is a standard type part.

More precisely one could have designed a specific elastic ring of the non-standard type not opening at the maximum speed of rotation of the launcher, it could limit the maximum speed of rotation of the launcher at the opening speed of the ring elastic.

The present invention makes it possible to use an elastic ring of the standard type while not being limited at the speed of rotation of the launcher.

In a variant (FIGS. 4 and 5) the elastic ring 160 is a ring of the standard type which has resilient tabs inclined at its inner periphery. In this case the groove 164 is enlarged because it receives the elastic tabs 161. The tabs 161 are snap-fitted in the groove 164.

More specifically, the pinion being in the aforementioned position in the retracted position and the compressed spring 61, the tabs 161 are threaded onto the front end of the section 126. The tabs, due to their elasticity, deform and then relax as they arrive in the groove 164. dimensioned accordingly.

This is possible because the pinion is then in the retracted position, the groove 164 being completely disengaged.

The ring 160 can not be ejected under the action of the centrifugal force due to the presence of the recess 62; the legs can not get out of the throat 164.

In all cases, commercially available elastic rings are used economically and the recess 62 is in contact at its bottom with the rear face of the ring 60, 160. The recess flange serves as a radial abutment to limit radial expansion. of the ring.

It will be appreciated that, in the retracted rest position (FIG. 2), the pinion 18 bears directly or indirectly on the bearing 12 via the washer 181 and that this support offers a large surface area. This support, carried by the front bearing 12, in retracted rest position of the pinion, is preferably axially offset forwardly relative to the front face 130 of the section 127 constituting a support for the rear end of the spring 61. The diameter of this support is greater than that of the shoulder 130.

Of course, the present invention is not limited to the exemplary embodiments shown. Thus, alternatively, as described in US Pat. No. 4,818,889 (FIG. 1), the electric motor shaft is configured to form a pinion belonging to an epicyclic gear reducer interposed between the shaft of the electric motor and the wheel. free. In this case the connection with splines and complementary grooves occurs between a sleeve belonging to the planet carrier of the gearbox and the coach of the freewheel roller launcher.

This sleeve is engaged with the launcher driver via a link with splines and complementary helical teeth. This sleeve constitutes the output shaft of the starter.

The assembly according to the invention between the pinion and the socket of the launcher replaces in this case the assembly of Figure 1 of this document US 4,818,889.

In this case the diameter of the pinion may be limited by the sleeve directed towards the outside of the bearing and partially surrounding the pinion.

This problem does not arise in the embodiment of FIG.

In a variant, the output shaft of the starter is in the axial extension of the output shaft of the electric motor as can be seen for example in FIG. 6 of the aforementioned document WO 2004/0881.

In a variant, the sleeve 312 is extended forwardly as in the document FR 2 764 946. In this case the opening 312 affects the transverse front wall of the hollow front bearing 12. This bearing is then globally shaped warhead in the front.

A seal can therefore be provided inside the front bearing and at the level of the needle bearing as in this document FR 2 764 946. The electromagnetic contactor extends in the embodiment of Figure 1 parallel to the electric motor of the starter being carried by the front bearing 12. Alternatively there is provided a return device between the fork and the movable core of the starter so that that in this case the contactor extends to the rear of the electric motor.

The presence of the fork is not necessary, the switch may include a coil surrounding the driver of the freewheel constituting the plunger of the contactor. The starter may or may not be equipped with a speed reducer.

The freewheel of the starter is alternatively conical clutch intervening between the driver and the rear end of the socket as described for example in WO 03/002870. Assembly of the starter yoke with the front and rear bearings of the housing can be done in any way.

For example there are provided tie rods (see Figure 1 of US 4,818,889) or screws (see Figure 6 of WO 2004/088126) to assemble the rear bearing to the front bearing with intercalation of the cylinder head.

The starter can be used to drive the internal combustion engine of a passenger vehicle, a truck, an agricultural tractor or a boat.

The starter variant is a starter for a fixed internal combustion engine used for example to drive a PTO.

In FIGS. 1 to 5, the recess flange completely axially covers the outer periphery of the ring 60, 160.

In a variant, the rim of the recess covers most of the outer periphery of the ring 60, 160. Thus, in a variant, the ring 60, 160 is projecting axially with respect to the pinion 18 while being housed for the most part in the recess. The ring 60, 160 has in all cases at its outer periphery a front face which extends axially projecting with respect to the front face 183 of the pinion 18. Thanks to the invention the pinion 18 can be obtained by any appropriate means, for example by extrusion, sintering, cutting in a bar or stamping. The pinion may be mono material or bi material. For example, the splines of the pinion are alternatively in a material different from that of the sprocket teeth. Thus, in one embodiment, this pinion is obtained by bi-material sintering. This embodiment is advantageous because the toothed portion of the pinion is chosen from a grade of material adapted to the needs of the gear with the ring gear 1 18 (wear resistance, low noise noise emission), while the inner portion of the pinion including the grooves 167 and the housing 261 is selected to be adapted to the necessities of

sliding and mechanical resistance in particular for the support of the spring 61.

As a variant, the second section 126 has a hardness different from the hardness of the first section 127 to promote a good sliding of the pinion 18.

In a variant, the groove 129 is omitted, a rounded zone being provided for connecting the front face 130 of the section 127 to the section 126.

The spring 61, of the helical type in the figures, is alternatively of another type. For example, it consists alternatively in a stack of Belleville washers. The axial offset of the groove 129 relative to the shoulder 130 allows in all cases the maintenance of the rear end of the spring 61 traversed by the section 126. The sleeve is further provided because in the retracted position of rest the pinion 18 is in support directly or indirectly on the housing. This spring 61 also makes it possible to dampen impacts, particularly when a tooth of the pinion comes into contact with a tooth of the crown. It allows aforementioned manner the mounting of the elastic ring 60, 160

Claims

claims

1. Outgoing centrally perforated thermal motor starter (18), in particular for a motor vehicle, comprising a casing provided with a front bearing (12) provided with a front face (120) provided with an opening (312), a launcher having a bushing (26) having a front end (126, 127) extending through the opening (312) of the front bearing (12) and carrying the outgoing gear (18) out of the front bearing (12), complementary grooves (67,167) belonging respectively to the outer periphery of the front end of the bushing (26) and to the inner periphery of the outgoing gear (18), a groove (64, 164) interrupting the grooves (67) of the bushing (26) for mounting a stop (60, 160) for axially immobilizing the pinion, a spring for catching the clearances (61) urging the pinion in contact with the stop, in which, on the one hand, the end front of the sleeve (26) has a shoulder (130) for supporting the rear end of the spring (61) and a on the other hand, the pinion (18) has at the rear a blind housing (261) for mounting the spring (61), characterized in that the stop (60, 160) is constituted by an elastic ring of height greater than its thickness. , in that the elastic ring (60, 160) is housed with radial clearance at least partly in an annular recess (62) formed in the front face (183) of the pinion (18) and in that the internal periphery of the the elastic ring (60, 160) is mounted in the groove (61, 161) of the sleeve (26).

2. Starter according to claim 1, characterized in that the outer periphery of the elastic ring (60, 160) is housed entirely in the recess (62).

3. Start according to claim 1, characterized in that the outer periphery of the elastic ring (60, 160) is housed for the most part in the recess (62).

4. Starter according to any one of the preceding claims, characterized in that the outer diameter of the elastic ring (60, 160) is greater than the outer diameter of the play catch spring (61).

5. Starter according to any one of the preceding claims, characterized in that the front bearing (12) has a sleeve (1 12) directed in the opposite direction to the pinion (18) and in that the opening (312) of the bearing front (12) is constituted by the internal bore of the sleeve (1 12) of the front bearing (12).

6. Starter according to any one of the preceding claims, characterized in that the elastic ring (60) is split.

7. Starter according to claim 6, characterized in that the elastic ring (60) is a circlip.

8. Starter according to any one of claims 1 to 5, characterized in that the elastic ring (160) has tabs inclined at its inner periphery.

9. Starter according to any one of the preceding claims, characterized in that the flanks of the grooves (64, 164) are parallel and in that the groove (64, 164) is deeper than the grooves (67) of the socket (126).

10. Starter according to any one of the preceding claims, characterized in that the front end (127, 126) of the sleeve (26) is stepped in diameter and has a first section (127) extended axially by a second section ( 126) of smaller diameter on which are formed the grooves (67) of the sleeve (26) and in that the shoulder (130) of the sleeve (26) is constituted by the front face of the first section (127).

1 1. Starter according to Claim 10, characterized in that the second section (126) has a groove (129) whose rear end is close to the front face (130) of the first section (127) and in that the groove (129) is offset axially with respect to the shoulder (130) for centering the rear end of the spring (61).

12. Starter according to claim 1 1, characterized in that a retaining surface of the rear end of the spring (61) exists between the shoulder (130) and the groove (129).

13. Starter according to any one of claims 10 to 12, characterized in that the outer diameter of the second section (126) is greater than the inner diameter of the first section (127).

14. Starter according to any one of claims 10 to 13, characterized in that the front bearing (12) carries a support (181) for the pinion (18).

15. Starter according to claim 14, characterized in that the support is constituted by a washer (181) of elastomer mounted in an annular cross housing (212) formed in the front face of the front bearing (12).