FR2677417A1 - GEAR SYSTEM FOR COMBINATION WITH AN ENERGY CONSUMER AUXILIARY DEVICE OF A MOTOR VEHICLE. - Google Patents

Abstract

Planetary gear train (4) combined with an electric generator (6) of a motor vehicle. The planetary gear train (4) includes a freewheel (13) and a gearshift clutch (22). Thus, it is possible to vary the transmission ratio of the planetary gear train. The elements of the gear train (4) are arranged so that they overlap, at least partially, in the axial direction, thereby reducing the overall axial dimension.

Description

GEAR SYSTEM FOR COMBINATION WITH A

  ENERGY CONSUMER AUXILIARY DEVICE

MOTOR VEHICLE

  The present invention relates to a gear system intended to be combined with an auxiliary device consuming energy, of a motor vehicle. As an example of an auxiliary device consuming energy of this type, there may be mentioned a current generator. electric to be driven from the internal combustion engine of a motor vehicle. As another example of an energy-consuming auxiliary device, an air compressor or an oil pump may also be mentioned. For optimal efficiency, such devices auxiliary power consumers must be driven at a rotational speed

substantially constant.

  In operation, the internal combustion engines of motor vehicles have very different speeds. This means that the speed of rotation that an internal combustion engine transmits to an auxiliary device consuming energy.

  that it causes presents strong variations.

  It is therefore desirable to equalize the speed of rotation of the energy-consuming auxiliary devices despite variations in the speed of the internal combustion engine driving the corresponding energy-consuming auxiliary device. The German patent published under the number 35 23 999 describes a gear system combined with an electric current generator. This gear system comprises a planetary gear control mechanism combined with a free wheel and an electromagnetic clutch. gear system input is provided with a belt pulley driven by the internal combustion engine, via a belt In this type of known gear system, the belt pulley drives a planet gear carrier The sun wheel is connected to the input shaft of the generator A free wheel device is provided between the ring gear and the sun wheel The ring gear can be locked or released by the electromagnetic clutch, so that it cannot rotate , or to be able to rotate, respectively When the ring gear cannot rotate, the sun wheel is driven at an increased speed of rotation pa r in relation to the speed of rotation of the belt pulley, while the freewheel ensures the relative rotation of the sun wheel and the toothed ring When the electromagnetic clutch releases the toothed ring to let it rotate, the device forming freewheel blocks the planetary gear device so that the sun wheel turns according to the

  same speed of rotation as the belt pulley.

  In this known gear system, the elements are

  arranged substantially in three planes, side by side.

  The belt pulley is placed in a first plane, the planetary gear mechanism is provided in a second plane, and the electromagnetic clutch is located in a third plane This construction requires a lot of space, especially in the axial direction Consequently, it is difficult to place a gear system of this type, combined with a corresponding generator, in the space reserved for the engine of a modern vehicle The gear system is not closed Noises are not dampened The possibility of an oil bath is mentioned, but no explanation is provided as to how to provide this oil bath The gear ratio for direct drive operation, on one side, and fast drive operation , on the other hand, is rather high and not suitable

for some applications.

  The German patent published under number 29 51 742 describes another gear system intended to be combined with an auxiliary energy-consuming device. This gear system can also operate in direct drive mode and in fast drive mode, these modes of operation can be selected by a centrifugal clutch In this type of construction, however, the disadvantage is that the planet gears of the planetary gear system rotate continuously, even during direct drive operation. Consequently, this results in noise important when the internal combustion engine, ensuring the drive of the gears, turns at a high speed In addition, the automatic change ensured by a centrifugal clutch presents problems, particularly,

for city driving.

  The main object of the present invention is to provide a gear system which occupies as little space as possible while being adjacent to an auxiliary energy-consuming device. Another object of the present invention is to provide a gear system which the the object of the present invention is also to provide a gear system in which the elements of the planetary gear are in a position idle, when the gear system is driven at a high speed by the corresponding internal combustion engine Furthermore, when the combustion engine ensuring the drive is running at a low speed, one obtains, without jerking , a higher transmission ratio, which also constitutes another object of the present invention Furthermore, another object of the present invention lies in the fact that the syst th of gears is closed, hermetically, with respect to the surrounding space, and can be provided with a certain amount of lubricant Finally, the present invention also aims to allow the pre-assembly of substantially all the elements of the gear system so that the pre-assembled system can be combined with the corresponding energy-consuming auxiliary device, both at the manufacturing stage and at the levels of

repair and replacement.

  The present invention provides a gear system combined with an energy-consuming auxiliary device of a motor vehicle. The electrical auxiliary device comprises stator means and a primary shaft of the auxiliary device with an axis. The gear system comprises , in a substantially annular arrangement, around the axis, a driving member of the gear system, a driven member of the gear system, planetary gear means comprising a sun wheel, a ring gear, a planet gear carrier and at least one planet gear on the planet carrier The gear system further comprises freewheel means, a gear change clutch which can be controlled by external control means and a lubricant chamber containing a liquid lubricant for the lubrication of the engaging faces of the movable elements of said gear system

  relative to each other, in operation.

  The driven member of the gear system is adapted to be connected, for a common rotation, with the input shaft of the auxiliary device, substantially in alignment with respect to the latter, along the axis Les above-mentioned elements of the gear system are arranged so that they require only a minimum space by being adjacent to the energy-consuming auxiliary device, at least in the axial direction, when the gear system is combined to the device

auxiliary energy consumer.

  It has been observed that it is possible to obtain a very compact gear system if the driving member

  of the gear system was connected, with the holder

  planet gears, for the drive of the latter, if the ring gear was adapted to be connected, for its drive, continuously, to the driven member of the gear system, if the clutch change gear was adapted to be able to selectively block the solar wheel, or to release it, and thus prevent it from turning, or let it rotate, respectively,

  around the axis, relative to the stator means.

  In this case, the free wheel means allows the rotation of the driven member of the gear system relative to the driving member of the latter, in a predetermined direction of rotation, in response to the action of the clutch. shifting, preventing the sun wheel from turning relative to the stator means On the other hand, the free wheel means transmits an input torque from the driving member of the gear system to the driven member of the latter, in the predetermined direction of rotation, in response to the action of the gear change clutch, leaving the sun wheel to rotate around the axis, by

relationship to the stator means.

  This fundamental operating principle is a necessary condition so that the elements of the planetary gear and the corresponding means forming bearings can be in an idle situation during operation in direct transmission mode or 1/1. This means that, when the combustion engine is running at high speed, the planetary gear system is in

a situation of rest.

  In the aforementioned system, the driving system gear member may have the form of a gear system driving sleeve, extending, in the axial direction, through the sun wheel, and of which a first end part is adjacent to the stator means and a second part

  end is remote from the stator means.

  The driven member of the gear system may extend, axially, through the driving member of the gear system, and have a first end portion adjacent to the stator means and a second portion of far end of the stator means. The driven member of the gear system can be adapted to be fixed to the input shaft of the auxiliary device The driving member of the gear system can be fixed, in the axial direction, and mounted, for its rotation, on the driven organ of the

  gear system, around the axis.

  The planet gear carrier can be mounted, for common rotation, on the gear system driving member, adjacent to the first end portion of the gear system driving member, in the direction axial, between the sun wheel and the stator means The ring gear can be fixed on the driven member of the gear system, so as to be adjacent to the first end part of this member, using a support member for the toothed wheel placed, in the axial direction, between the planet gear carrier and the stator means The second end part of the driving system gear member can be provided with a face of setting

  grip of the drive means, around the axis.

  The engaging face of the drive means can be, for example, a belt pulley. These design features reduce

the longer the axial length.

  The space occupied, in the axial direction, can be further reduced if the first axial end part of the sun wheel is adjacent to the stator means and if its second axial end part is distant from the stator means In this case , the second axial end part of the solar wheel can be connected to the stop member of the solar wheel, with a view to its common rotation with the latter. The stop member of the solar wheel can be mounted, in view of its rotation, and fixed, in the axial direction, on an external surface, in the direction

  radial, of the driving organ of the gear system.

  This sun wheel stop member supports a first clutch part of the gear change clutch, while a second part of the gear change clutch can be fixed, or adapted to be fixed, to the stator-forming means. A design characteristic which makes it possible to further reduce the axial length consists in providing a flange member extending outwards, in the radial direction, for the stop member of the sun wheel, said flange member supporting the first part of the gearshift clutch device The first part of the gearshift clutch can engage, by friction, with the second part of the gearshift clutch The first part of the gearshift clutch gear change can move, axially, relative to the flange member, so as to engage the clutch parts without displacement

axial of the flange member.

  The gear change clutch can be an electromagnetically controlled clutch. Furthermore, it is also possible to use hydraulic clutches. In all cases, the clutch must be able to be controlled from a remote control device. of the gear system, so that the actuation of

  the clutch can be provided arbitrarily.

  When using a control device of this type, it is possible to provide a necessary hysteresis using the control device, to avoid multiple speed changes, at a predetermined speed of rotation of the member. gear system driver The second part of the gear change clutch may include an electromagnetic coil device and the first part of the electromagnetic clutch

may include a frame.

  The member forming the support of the toothed ring can be adapted to be clamped between the first end part of the driven member of the gear system and an abutment face, oriented in the axial direction, provided on the primary shaft of the auxiliary device, fixedly, in the axial direction, with respect to this shaft Clamping means which can be released can be provided to push, in the axial direction, the driven member of the gear system against the member forming the support of the ring gear and the latter against the abutment face Thus, the assembly of the gear system is completed when this system is combined with the

  auxiliary device consuming energy.

  The member forming the support of the toothed ring can be a first part of the casing of a chamber casing delimiting the lubricant chamber and in which the means forming planetary gears are housed. The first part of the casing can be adjacent to a first part d axial end of

  the sun wheel closer to the stator means.

  The chamber casing can be completed by a second casing part further from the stator means and adjacent to a second end part of the solar wheel. Thus, a compact casing can be provided around the planetary gear means. The second part housing can be placed in the axial direction between the flange member and the second end portion of

said solar wheel.

  To seal the lubricant chamber, the second housing part can be engaged, while being able to rotate, and in a manner ensuring a hermetic closure, with the stop member of the sun wheel, and this the latter can be engaged, while being rotatable, and in a manner ensuring a hermetic closure, with

  the driving organ of the gear system.

  The freewheeling means can be placed, in the radial direction, between the driving member of the gear system and the driven member of the latter, 1 1 substantially in a radial alignment relative to the sun wheel This allows, very advantageously, to obtain a construction occupying little space because the free wheels are located substantially in the same plane as the means forming planetary gears. Furthermore, the freewheeling means can be placed, in the radial direction, between an outer circumferential face, in the radial direction, of the planet gear carrier and a circumferential face, facing inward, in a radial direction, of the member forming the support of the ring gear, on the side of the latter, distant from the stator means This also makes it possible to obtain a very compact construction, particularly, if one considers that the shape of the member forming the support of the wheel can be adapted to a convex end face of an electric current generator More particularly, the free wheel means can be placed outside, in the radial direction, of the mounting pins of the

  planet gears attached to the planet gear holder.

  The driving member of the gear system can be mounted, so as to be able to rotate, on the driven member of the gear system by first bearing means, adjacent to the first end parts of the driving member. of the gear system and the driven member thereof and by second means forming bearings, adjacent to the second end portion of the driving member of the gear system and the driven member thereof. This makes it possible to obtain a very stable construction in which the belt pulley adjacent to the second end part of the driving system gear member resists the bending forces caused by tensioning the belt. upper, it is desirable to use a driven member of the gear system in the form of a sleeve, so that the primary shaft of the auxiliary energy-consuming device can extend into the driven member of the gear system, on at least part

of its axial length.

  In order to obtain a short axial construction, it may be desirable for the first bearing means to be placed substantially in a radial alignment relative to the sun wheel. At least one of the first and second bearing means may be adapted to position, in the axial direction, the driving member of the gear system and the driven member of the gear system, with respect to each other. , in the axial direction For example, the above-mentioned bearing means may be the first bearing means and these may be

  means forming ball bearings.

  In addition, the stop member of the sun wheel can be mounted, for its rotation, on the driving member of the gear system, by means forming bearings These means forming bearings ensuring the fixing of the member stop of the solar wheel on the driving system gear member can be means forming ball bearings adapted to position the stop member of the solar wheel relative to the driving system gear member . To ensure the sealed closure of the lubricant chamber, the stop member of the solar wheel can be engaged, so as to ensure a sealed closure, with the driving member of the gear system at a location further from the means forming a stator as the means forming a ball bearing fixing the stop member of the sun wheel on the driving member of the gear system. Thus, these means forming ball bearings are also

supplied with lubricant.

  The driving member of the gear system can be mounted, for rotation, on the driven member of the gear system, by at least one roller bearing means comprising a group of arranged roller members, circularly, around the axis These roller-forming members may be in direct engagement, with a view to their rolling, with the corresponding raceways formed in the driving member of the gear system and in the driven member thereof In addition, the stop member of the sun wheel can be mounted, for its rotation, on the driving member of the gear system, by at least one means forming roller bearings comprising a group of members forming rollers arranged in a circular manner around the axis In addition, this group of roller-forming members may be in direct engagement, with a view to their rolling, with the corresponding raceways formed in the driving member of the gears and in the stop member of the solar wheel. The use of the above-mentioned form of special roller bearings makes it possible to further reduce the radial and axial dimensions, compared to the use of complete traditional roller bearings, comprising members forming an inner ring and an outer ring. In this respect, the term roller member must be understood to mean both the members forming

  balls as the bodies forming cylindrical rollers.

  The sun wheel, at least said satellite pinion and the ring gear can be housed inside a lubricant chamber, which is delimited by a chamber casing and closed, in a sealed manner, by means ensuring a sealed closure. , which can pivot This chamber casing comprises means forming external casing walls, in the radial direction The gear change clutch can be, at least partially, placed outside, in the radial direction, means forming wall outer casings in the radial direction, and can overlap the latter, in the axial direction Thus, this makes it possible to further reduce the axial length. The electromagnetic clutch can be disposed substantially in the same plane as the means forming planetary gears. The lubricant chamber is preferably formed as an annular chamber around the axis and receives at least one of the planetary gear means and the free wheel means This annular chamber can rotate around the axis in response to rotation of the driving system gear unit Thus, the liquid lubricant in the lubricant chamber forms a ring of lubricant adjacent to the means forming the external walls, in the radial direction, of the lubricant chamber, in response to centrifugal forces Means lubricant transport can be placed in the lubricant chamber to transport the lubricant from the lubricant ring to the engagement faces of the corresponding elements of the gear system which are movable relative to each other. The lubricant transport means may comprise a lubricant collecting tube having an outer end, in the radial direction, and penetrating into the lubricant ring and comprising collecting means oriented in a

  substantially circumferential direction around the axis.

  This collecting tube rotates relative to the lubricant chamber so as to collect the lubricant under the effect of the shutdown pressure

  transporting the lubricant to the required places.

  The relative rotation of the lubricant ring and the collecting tube can be obtained by the fact that the lubricating chamber is delimited by a mounted chamber housing, with a view to its common rotation with the ring gear, while the collecting tube is connected to the solar wheel, for a

  joint rotation with the latter.

  According to a preferred embodiment, the collecting tube is mounted for its common rotation with the planet gear carrier and is, at least partially, placed in a space orthogonal to the axis and containing at least one said satellite gear This further reduces the

axial length.

  According to another embodiment, the transport means comprise at least one transport disc mounted for its common rotation with the satellite pinion A corresponding circumferential part of this disc, external, in the radial direction, is immersed in the ring of lubricant and a corresponding circumferential part of this disc, inside, in the radial direction, is oriented towards a location receiving lubricant droplets. immersion in the lubricant ring and sends droplets to the location receiving droplets when it reaches a position adjacent to this

  location when the satellite gear is rotated.

  This droplet location can be

  connected to locations to be lubricated.

  For example, the location receiving droplets can be provided with means forming impact faces of the droplets, the latter dispersing the droplets towards locations for engaging the relatively mobile elements of the gear system. The gear system can be pre-assembled to be combined with the auxiliary device

  energy consumer This gear system pre-

  assembled may include a shaft-forming engaging member adapted to secure by engaging with a securing portion of the input shaft of the auxiliary device. Thus, the pre-assembled gear system is maintained in a state of pre-assembly after having been combined with the energy-consuming auxiliary device by engagement of the engagement member forming a shaft with the fixing part of the input shaft of the auxiliary device Before performing this combination, the pre-assembled gear system can be fixed, a

  once pre-assembled, by a fixing member of the pre-

  assembly whose shape corresponds substantially to the fixing part of the input shaft of the device

  auxiliary This fixing device of the pre-

  assembly is engaged with the shaft member, after assembly of the gear system, to maintain the pre-assembled gear system in the pre-assembled position, during

storage and transportation.

  A part of said gear change clutch can be fixed to the stator means by an enveloping sleeve which envelops at least part of the gear system. This is possible since the belt pulley is placed at a distance from the auxiliary current-consuming device. . The enveloping sleeve can be fixed, so as to be released, by the stator means. When the enveloping sleeve is fixed relative to the stator means, it is possible to adjust the axial clearance between the first and second parts of

  the gear change clutch.

  The gear system must provide a first transmission ratio of 1/1 and a second transmission ratio of less than 1.70: 1 between the driven member of the gear system and the driving member of the latter, the driven gear system member having higher rotational speed That

  is desirable to achieve a smooth transition to-

  blows between the different operating modes.

  It is possible to control the gearshift clutch using a control member, in response to the speed of rotation of the driving member of the gear system corresponding to the speed of the internal combustion engine ensuring its drive, so that the speed of rotation of the driven member of the gear system increases in relation to the speed of rotation of the driving member of the gear system when the speed of rotation of the latter decreases and becomes lower at a predetermined speed value. However, it is not necessary to change the transmission ratio when the predetermined speed value is reached. If the auxiliary energy-consuming device is, for example, an electric current generator, supplying an electric accumulator, the ratio transmission should only increase if the accumulator is lightly charged Consequently, the increase in the speed of rotation of the driven member of the gear system, beyond the speed of rotation of the driving system member of gears, which occurs in response to the decrease in the speed of the latter becoming less than the predetermined speed of rotation value, may also occur in response to a signal representing the need to increase the speed of rotation of said auxiliary energy-consuming device. It is very desirable that all of said movable elements of the gear system be in a rest position relative to the driven member of the gear system when the latter is directly driven from the driving member of the gear system. by means of the freewheeling means In this case, lubrication is not necessary and there is no need

to ensure a flow of lubricant.

  The freewheeling means must be, at least

  partially submerged in the lubricant ring.

  The freewheeling means can, for example, be

of the clamping roller type.

  If the first housing part and the second housing part are connected to each other, the freewheel can be fixed, in the axial direction, between the first housing part and the second housing part. The means of transporting the lubricant, as defined above, may comprise means for discharging the lubricant in a position opposite to at least one bore, oriented in a substantially radial direction, of a hollow rotary element, which rotates around the axis relative to the lubricant pouring means This lubricant pouring means can be an inner end of a collecting tube or a transport disc The spilled lubricant must sometimes be transported, in a radial bore of an element hollow, for example, in a radial bore of the driving member of the sleeve-shaped gear system, in order to supply the roller bearings with lubricant, between the member forming the gear system and the driven member of the latter In addition, a lubricant flowing in a radial bore of this type, inwards, in

  in a radial direction, is subjected to centrifugal forces.

  In order to ensure inward flow in a radial direction, despite centrifugal forces of this type, it is proposed to provide the radial bore

  of an elongated section along the axis.

  The specific features of the various features of the invention are presented in

  the description which follows and form an integral part

  of the object of the present invention For a better understanding of this, its operational advantages and its specific objects are described below in the preferred embodiments of the present invention with reference to the attached figures. The present invention will now be described with reference to the embodiments illustrated in the accompanying figures, in which: FIG. 1 is a schematic view of a gear system according to the present invention; Figure 2 illustrates a longitudinal section containing the axis of the gear system according to the present invention; Figure 3 illustrates a partial section, according to Figure 2, representing a modified embodiment, and Figure 4 illustrates a partial section, according to Figure 2, representing another embodiment

modified realization.

  In FIG. 1, an electric current generator 6 comprises a stator casing 81 in which a rotor 2 is mounted for rotation. The rotor is fixed on an input shaft 1 of the generator 6 A gear system 4 is combined with the generator 6 The gear system 4 comprises a drive member of the gear system 9 on which is mounted a belt pulley 9 a for a common rotation with the latter The drive member 9 is connected to a door - satellite gears 61 in sight

  of a common rotation with the latter

  satellite pinions 61 supports a pin 8 on which is mounted, so as to be able to rotate, a satellite pinion 65 The satellite pinion 65 is engaged with a toothed crown 25 and a sun wheel 43 The toothed crown 25 is connected to a driven member of the gear system, for a common rotation therewith The driven member 5 of the gear system is connected to the input shaft 1 of the generator by coupling means 10 A freewheel device 13 is provided between the driving member 9 of the gear system and the driven member 5 of the gear system The solar wheel 43 is connected to a stop member 41 of the solar wheel The stop member 41 of the solar wheel supports a first part 87 of a

  electro- gear shifting clutch

  magnetic 22 A second part 83 of the electromagnetic clutch 22 is fixed to the stator housing

  81, via an enveloping sleeve 85.

  The clutch part 83 comprises an electro-

  magnetic which is supplied with electric current from an external control member 24 The clutch part 87 comprises an armature which is engaged, by friction, with the clutch part 83

  by excitation of the electromagnetic coil.

  The control member 24 has a first inlet 24 a and a second inlet 24 b The belt pulley 9 a is connected by a belt (not shown) to a

  output shaft of an internal combustion engine.

  When the internal combustion engine is running at a low speed, the control member 24 receives, via the input 24 a, a signal emitted by a sensor 24 c, indicating that the rotation speed of the internal combustion engine and, by Consequently, that of the driving member 9 is less than a predetermined value. In response to this signal, the clutch 83 is closed, so that the sun wheel 43 is fixed relative to the stator casing 81 Under these conditions. , the driven member 5 is driven with a higher speed of rotation, relative to the speed of rotation of the driving member 9 The free wheel 13 allows the relative rotation of the driving member 9 and the driven member 5 Thus , the input tree; of the generator 6 is driven with a relatively high speed of rotation, despite the low speed of the internal combustion engine This may be particularly necessary when an accumulator 26, powered by the generator 6, is lightly charged If the accumulator 26 is well charged, it may be unnecessary to increase the speed of rotation of the generator using the gear system Consequently, the input line 24b of the control member 24 is connected to the accumulator 26 to detect the state of the accumulator It is only when the two inputs 24 a and 24 b provide a signal to the control member 24 that the clutch 22 is energized and that the sun wheel 43 is

blocked so as not to turn.

  As soon as the speed of the internal combustion engine increases and exceeds the predetermined speed value, a deactivation signal is transmitted from the speed sensor 24 c to the control member 24 This results in deactivation clutch tension 22 Thus, the sun wheel 43 can rotate freely Under these conditions, the free wheel 13 comes into action, and transmits the rotation of the driving member 9 directly to the driven member 5 and to the shaft d input 1 of generator 1 Thus, the rotation speed of the generator is kept at a low value despite the increase in the speed of the internal combustion engine. Figure 2 illustrates the stator housing 81 of the

  generator and input shaft 1 of the latter.

  The input shaft '1 is mounted, so as to be able to rotate, in a roller bearing 28 adjacent to an end wall 30 of the stator housing. The member forming the inner ring 28 a of this ball bearing is mounted. hot on the input shaft 1 The left end of the input shaft 1 is provided with an external thread forming means 32 The driven member 5, in the form of a sleeve, surrounds the input shaft 1 and is placed in abutment against the member 21 forming a support for the toothed crown This member 21 is placed in abutment against a spacer ring 34 which itself abuts against the member forming the inner ring 28 a which is fixed on the input shaft 1 A tension member 3, with a hexagonal face 3 a, engages with the left end of the driven member 5, by means of an end flange 36 This tension member 3 is provided with an internal thread means 36 and is screwed onto the external thread means 32 of the shaft d input 1 Thus, the driven member 5, the support member 21 of the ring gear and the spacer ring 34 are clamped, in the axial direction, between the end flange 3b and the member forming ring 28 a In this way, the output member 5 is connected, for a common rotation, with the input shaft 1, and the member forming the support of the ring gear is connected, for a common rotation, with the organ

led 5 and input shaft 1.

  The driving member 9, in the form of a sleeve, is mounted, so as to be able to rotate, on the driven member 5 by a ball bearing 11 and a needle bearing 15 The balls of the needle bearing 11 are in direct engagement, with a view to their rolling, with the raceways formed in the driven member and in the driving member 9 The same applies to

  the needles of the needle bearing 15.

  The left end of the lead member 9 is closed by a cover member 17 The left end portion of the lead member 9 has the form

of a belt pulley.

  The planet gear carrier 61 is fixed on the driving member 9, for a common rotation with

  the latter, by means forming teeth 67 The holder

  planet gears 61 supports the planet gears by pins which are stabilized by another part 63 of the planetary gear carrier 61 The toothed ring 25 is fixed to the member 21 forming a support for the toothed ring, for a common rotation with this, due to the fact that a housing part 23 is bent at 23a around a flange 21a

  of the member 21 forming a support for the toothed crown.

  This member 21 is formed so as to constitute another part of the casing, so that the support 21 of the ring gear and the part of

  casing 23 form an annular chamber casing 40.

  The sun wheel 43 is supported by the planet gears 65 around the driving member 9 The sun wheel 43 is fixed, angularly, relative to the stop member 41 of the sun wheel by means forming teeth 45 L 'stop member 41 of the solar wheel is mounted, so as to be able to rotate, on the driving member 9, by means of a ball bearing 47, the balls of which are in direct engagement, with a view to their bearing, with the raceways formed in the driving member 9 and the member 41 for stopping the solar wheel This last member 41 is provided with a flange 41a extending outwardly, in a radial direction The flange 41 a supports, by means of springs 49, which can be deflected in the axial direction, the clutch part 87 provided with the frame and which can engage with a friction face 89 of the part clutch 83 comprising the electromagnetic coil The freewheel 13 is placed, in the ra direction dial, between the driven member 5 and the driving member 9 The clutch part 83 is fixed to an enveloping sleeve 85, which is itself fixed to the stator housing 81, and can be adjusted, in the axial direction, relative to the latter, to adjust the space between the clutch parts 87 and 83 Inside the chamber casing 40, an annular lubricant chamber 42 is defined The sealed closure of this annular lubricant chamber is ensured by a sealing ring 29 between the housing part 23 and the stop member 41 of the sun wheel and, in addition, by a sealing ring 31 which can rotate, provided between the stop member 41 of the solar wheel and the driving member 9 In addition, the closure of this chamber is ensured by a sealing ring 27 between the housing parts 21 and 23 In addition, the lubricant chamber 42 is closed, in a sealed manner, by a close engagement of the housing part 21 (member 21 for supporting the tooth crown e) and the driven member 5 and by the cover 17

  comprising a sealing ring 17 a.

  The lubricant chamber 42 is filled with a quantity of liquid lubricant 35 The lubricant liquid forms a ring of lubricant 35, in operation, due to centrifugal forces This ring of lubricant rotates with the casing of the

  chamber 40, that is to say, with the driven member 5.

  The sealing rings 29 and 31 are arranged radially inwards of the lubricant ring 35, so that they are not subjected to the pressure of the lubricant resulting from the forces

  centrifugal A lubricant collecting tube 19 is fixed to the or-

  gane 41 for stopping the solar wheel and having an outer end

  higher, in the radial direction, with an opening 18 oriented in a circumferential direction, around the axis A When the member 41 for stopping the solar wheel cannot enter into rotation, due to the tensioning of the clutch 22, the lubricant ring rotates relative to the collecting tube 19, which does not rotate, so that a stopping pressure builds up inside the collecting tube 19 The pressurized lubricant flows in the collecting tube 19, inwards, in a radial direction, and through a radial bore 44 of the member 41 for stopping the solar wheel,

  ball bearing direction 47 In addition, the lubricant pressu-

  risé hits the leading member 9 The leading member 9 is provided with radial bores 16 Consequently, a jet of lubricant is periodically sent through the radial bore 16, in the radial space between the leading member 9 and the driven member 5 The lubricant inside this radial space can flow towards the ball bearing 11, the needle bearing 15 and the free wheel 13 A step 37 prevents the lubricant collected in the area of the bearing with needles 15 to flow back under the effect of centrifugal forces A disc 14 and a step 39 prevent the lubricant arriving at the free wheel 13 from backing up Thus, this ensures sufficient lubrication of all the means forming the bearings and of the free wheel In addition, the inner teeth, in the radial direction, of the ring gear 25 are immersed in the ring of lubricant 35, so that the engagement faces of the planet gears 65 and the

  gear 25 are also lubricated.

  The bores 16 have an elongated section in the circumferential direction. This configuration makes it possible to reduce the backflow of the lubricant, caused by centrifugal forces, through the bore 16, so that the lubricant flows through the bore 16, inwards, in a radial direction When the clutch 22 is released, the driven member 5 and the driving member 9 rotate as a single device In this situation, no relative movement occurs between the ring gear 25 and the sun wheel 43, neither between the stop member 41 of the sun wheel and the driving member 9, nor between the driving member 9 and the driven member 5 No pressure

  stop accumulates in the collecting tube 19.

  However, this is not necessary, since no

lubrication is not required.

  Before combining the gear system 4 with the generator 6, the pre-assembled gear system 4 is held in the pre-assembled position, as shown in FIG. 2, by a fixing bolt penetrating into the driven member 5 from the left side of FIG. 2, and screwed into the internal threading means 36 of the tension member 3 This fixing bolt has a part forming a head engaging with the member 21 forming the support of the

  ring gear and pressing against the driven member 5.

  It should be noted that the clutch 22 and the planetary gear are very close to each other in the axial direction. It should also be noted that the ball bearing 11 and the free wheel 13 are located substantially in the same plane as the planetary gear The direct engagement of ball and needle bearings with adjacent parts allows to further reduce the axial and radial dimensions The gear system can be combined with a generator of conventional design in which the driving shaft 1 is provided with a simple belt pulley The above mentioned design makes it possible to obtain an axial length of the generator and of the combined gear system which is not substantially greater than that of a corresponding conventional generator , with a belt pulley

  directly attached to the input shaft 1.

  The sealing rings 31 and 29 can be

  present in the form of sealing lips.

  In operation, a high speed of rotation according to a transmission ratio of 1: 1, the lubricant is substantially contained inside the chamber

  annular 42 which prevents any leakage of liquid.

  In the embodiment of FIG. 3, the member 21 forming the support of the toothed ring is connected to the toothed ring 25 by means forming teeth 46 and is fixed, in the axial direction, by a fixing ring 48 The wheel free 13 is placed inside the lubricant chamber 42, so that the free wheel 13 is immersed, at least partially, in the lubricant ring not shown In this embodiment, the member 21 forming support of the ring gear has a shape adapted to the convex shape of the end wall 30 of the generator, as illustrated in FIG. 2 Thus, the freewheel 13 can be placed in a transition zone between a flange portion 21 c and a part 21 d carrying the ring gear of the member 21 forming a support for the ring gear Thus, no useful axial space is occupied by the location of the freewheel 13 The pinion

  satellite 65 is combined with a transport disk 71.

  This transport disc 71 rotates with the satellite pinion 65 and is mounted by internal teeth on the

  outer teeth of the satellite gear 65 The circumferential part

  tial, external in the radial direction, of the transport disc 71 is immersed in the ring of lubricant (not illustrated) Thus, this transport disc 71 is moistened with lubricant This lubricant is propelled, from the transport disc 71, by the centrifugal forces The droplets are propelled through, the radial bore 16, elongated, in the axial direction These droplets are scattered at the level of the external circumferential face of the driven member 5 and are directed towards the ball bearing 11 and the bearing with needles 15 (illustrated only in FIG. 2) This conical face 9 c of the driving member 9 allows the accumulation of a quantity of

  lubricant in the needle bearing area 15.

  If a certain quantity of lubricant is collected near the conical face 9c, the lubricant can flow through the substantially radial bore 50, towards the outside, in a radial direction, in the direction of the ball bearing 54 and in the direction of a needle bearing 52 added between the driving member 9 and the stop member 41 of the sun wheel. It should also be noted that, in this embodiment, the sun wheel 43 is fixed, in the radial direction and circumferentially, at

  the stop member 41 of the solar wheel.

  The lubricant can flow back into a radial groove 77 provided in the planet gear carrier 61 and covered with a cover plate 73 fixed to the planet gear carrier 61 This reflux of the lubricant ensures the lubrication of a needle bearing 75 by the through which the satellite pinion 65 is fixed to the journal 8 The high speed of rotation of the satellite pinions 65 ensures reliable lubrication of all the bearings Again, it should be noted that the bearings 11 and 47 are close to each other other, in the axial direction, so

  that we can minimize the axial dimension.

  The immersion of the freewheel 13 in the lubricant ring avoids noise and ensures a

  efficient lubrication of the freewheel.

  In the embodiment of FIG. 4, a collecting tube 19 is also used with a collecting spout 18 oriented in a substantially circumferential direction in order to collect the lubricant by stopping effect. The collecting tube is, unlike the embodiment illustrated in figure 2, fixed to

  satellite pinion carrier 61 between the carriers

  subsequent satellites Thus, at least part of the collecting tube 19 can be housed in the same plane as the satellite pinions The lubricant flows in the collecting tube 19, inwards, in a radial direction, and in the bore 78 from the planet gear carrier 61 to penetrate a radial groove 79 which is covered by a disc 54 rotating with the planet gear holder 61 The lubricant flowing in the radial direction, inwards, into the groove 79, reaches the level of the ball bearing 11 (illustrated only in FIG. 2) If a predetermined quantity of lubricant has been collected in the area of the needle bearing, the lubricant then flows back into the radial bore 50 Thus, the ball bearing 47 is also lubricated The flow of lubricant also moistens the sun wheel 43 and the internal parts, in the radial direction, of the planet gears. The ball bearings 47 and 52 are arranged substantially in the same plane as the planetary gear train 25, 43, 61, 65 The clutch 22 (not shown) is also preferably arranged in this common plane radially

  outside the part carrying the toothed crown 21 d.

  The clutch 22 is preferably annular around the axis A This clutch can be replaced by mechanical, pneumatic or hydraulic clutches The gear system can be

  filled with oil before being combined with the generator The sleeve

  loping 85 and the clutch portion 83 are independent of the rest of the gear system and can be supplied together with

the rest of the system.

  If specific embodiments of the present invention

  tion have been illustrated and described in detail to illustrate the applica-

  tion of this invention, it goes without saying that these embodiments can be modified without departing from the scope of the

present invention.

  The reference numbers used are only intended to facilitate the understanding of the figures and do not

are in no way limiting.

  The organ 5 must be interpreted in one sense

  wide as a rotating element at an output speed.

  Since the freewheel 13 can be, as shown in FIG. 3, engaged with the support member for the ring gear 21, the driven member 5 of the gear system is not necessarily directly included in the transmission of torque between the support member

  of the ring gear 21 and the input shaft 1.

  The sealing ring 31, 29 must also be interpreted in a broad sense and includes all types of sealing means allowing relative rotation of the respective parts which must be sealed

relative to each other.

Claims (32)

  1 gear system intended to be combined with an auxiliary device (6) consuming energy, of a motor vehicle, characterized in that said auxiliary device (6) consuming energy comprises means forming a stator (81) and an input shaft (1) of the auxiliary device with an axis (A), and in that said gear system (4) comprises, in a substantially annular arrangement, around said axis (A), a driving member ( 9) of the gear system, a driven member (5) of the gear system, planetary gear means (25, 43, 61, 65) comprising a sun wheel (43), a ring gear (25), a satellite gear carrier (61)   and at least one satellite pinion (65) on said holder   planet gears (61), said gear system further comprising free wheel means (13), a gear change clutch (22) controllable by external control means (24) and a lubricant (42) containing a liquid lubricant (35) for the lubrication of the engaging faces of the elements (25, 65, 43, 11, 47, 15, 13) of said gear system (4) which are movable in relation to each other, in operation, said driven member (5) of the gear system being adapted to be connected, for common rotation, with said input shaft (1) of the auxiliary device, substantially in alignment with respect to the latter, along said axis (A), said aforementioned elements (25, 65, 43, 11, 47, 15, 13) of said gear system being arranged so that they do not require a minimum space by being adjacent to said auxiliary device (6) consuming energy, at less in the axial direction, when said gear system (4) is combined with said auxiliary device (6) consuming energy. 2 gear system according to claim 1, characterized in that said driving member (9) of the gear system and said driven member (5) of the gear system are placed coaxially with respect to the other, and overlap, in the axial direction, around said axis (A), a member (5), among said driving member (9) of the gear system and said driven member (5) of the latter, being a member central (5), and the other member (9), among said driving member (9) of the gear system and said driven member (5) of the latter being an external member (9), means forming bearings (11 , 15) being provided, in the radial direction, between said driving member (9) of the gear system and said driven member (5) of the gear system, said planetary gear means (25, 43, 61, 65) and said gear change clutch (22) being placed, in an annular manner, around said external member (9), said driving member (9) of the gear system and said driven member (5) thereof having respective first end portions adjacent to said auxiliary device (6) consuming energy, and respective second end portions, further from said auxiliary device (6 ) energy consumer, said second end portion of said driving system gear member (9) being provided with an engaging face (9a) of the drive means 3 Gear system according to claim 2, characterized in that said driving member (9) of the gear system constitutes said external member, and in that said driven member (5) of the gear system constitutes said central organ.   4 gear system according to claim 1, characterized in that said driving member (9) of the gear system is connected, continuously, to said planet gear carrier (61), for the purpose of driving it- ci, said ring gear (25) being adapted to be connected, in a continuous manner, to said driven member (5) of the gear system, for the purpose of driving the latter, said gear change clutch (22) being adapted to be able to selectively block the solar wheel (43) or else release it and thus prevent it from rotating, or let it rotate, respectively, around said axis (A), relative to said stator means (81 ), said free wheel means (13) allowing the rotation of said driven member (5) of the gear system with respect to said driving member (9) thereof, in a predetermined direction of rotation, in response to the action of said gear change clutch (22) preventing said wheel e solar (43) to rotate relative to said stator means (81), said free wheel means (13) transmitting an input torque from the driving member (9) of the gear system to the driven member ( 5) of the latter, in said predetermined direction of rotation, in response to the action of said gear change clutch (22) leaving the sun wheel (43) to rotate about said axis (A), by   report to said stator forming means (81).   Gear system according to Claim 4, characterized in that the said solar wheel (43) has a central passage, the said driving system member (9) having the shape of a primary sleeve of the gear system s' extending, axially, through said sun wheel (43) and having a first end portion adjacent to said stator means (81) and a second end portion remote from said stator means (81), said driven member (5) of the gear system extending, in the axial direction, in said driven member (9) of the gear system and having a first end part adjacent to said stator means (81) and a second part d end distant from said stator means (81), said driven member (5) of the gear system being adapted to be fixed to said primary shaft (1) of the auxiliary device, said driving member (9) of the gear system being fixed , in L e axial direction, and mounted, for its rotation, on said driven member (5) of the gear system, around said axis (A), said planet gear carrier (61) being mounted on said driving member (9) of the gear system, for a common rotation with this member, being placed adjacent to said first end portion of said driving member (9) of the gear system, in the axial direction, between said wheel solar (43) and said stator means (81), said ring gear (25) being able to be fixed on said driven member (5) of the gear system, adjacent to said first end portion thereof, at by means of a member forming a support (21) of the ring gear placed, in the axial direction, between said planet gear carrier (61) and said stator means (81), said second end portion of said driving member (9) of the gear system being provided with an engaging face   (9 a) of the drive means, around said axis.   6 gear system according to claim 5, characterized in that said sun wheel (43) has a first axial end portion adjacent to said stator means (81) and a second axial end portion remote from said stator means ( 81), said second axial end portion of said sun wheel (43) being connected to the stop member (41) of the sun wheel, for a common rotation with the latter, said stop member (41) of the solar wheel (41) being mounted, for its rotation, and fixed, in the axial direction, on an external surface, in the radial direction, of said driving member (9) of the gear system, said stop member (41) of the sun wheel supporting a first clutch part (87) of said gear change clutch (22), a second part (83) of said gear change clutch being fixed, or adapted for   be fixed to said stator means (81).   7 gear system according to claim 6, characterized in that said stop member (41) of the sun wheel has a flange member (41a) extending outward, in the radial direction, said member forming a flange (41a) supporting said first part (87) of said gear change clutch (22), said first part (87) of said gear change clutch (22) being able to engage, by friction, with said second part (83) of said   gear change clutch (22).   8 gear system according to claim 7, characterized in that said first part (87) of said gear change clutch (22) is movable, in the axial direction, relative to said member forming flange (41 a).   9 Gear system according to all of claims 1 to 8,   characterized in that said change clutch   gears (22) is an electro-controlled clutch   magnetic. Gear system according to claim 8, characterized in that said second part (83) of said gear change clutch (22) comprises an electromagnetic coil device and in that said first part (87) of said gear clutch   gear change (22) includes a frame.   11 Gear system according to any one of   claims 5 to 10, characterized in that said   support member (21) of the ring gear is adapted to be clamped between said first end portion of said driven member (5) of the gear system and an abutment face (28a), oriented in the axial direction , provided on said input shaft (1) of the auxiliary device, and fixed, in the axial direction, to the latter, clamping means (3), which can be released, being provided for pushing, in the axial direction, said driven member (5) of the gear system against said support member (21) of the ring gear and the latter against said abutment face (28 a).   12 Gear system according to any one of   claims 6 to 11, characterized in that said   support member (21) of the ring gear is a first part (1) of a chamber housing (40) delimiting said lubricant chamber (42) and in which are housed said planetary gear means (25, 43, 61 , 65), said first housing part (21) being placed adjacent to a first axial end part of said sun wheel (43) closer to said stator means (81), said chamber housing (40) being completed by a second casing portion (23) further from said stator means (81) and adjacent to a second   end part of said solar wheel (43).   13 gear system according to claim 12, characterized in that said second housing part (23) is placed, in the axial direction, between a flange member (41 a) of said stop member (41) of the wheel solar and said second end portion of said solar wheel (43).   14 Gear system according to claim 13, characterized in that said second casing part (23) can be engaged, while being able to rotate, and in a manner ensuring a hermetic closure,   with said stop member (41) of the solar wheel.   Gear system according to claim 14, characterized in that said stop member (41) of the sun wheel can be engaged, while being able to rotate, and so as to ensure a tight closure,   with said driving member (9) of the gear system.   16 Gear system according to any one of   claims 2 to 15, characterized in that said   freewheel means (13) is placed, in the radial direction, between the driving member (9) of the gear system and said driven member (5) of the gear system, substantially in a radial alignment with respect to said solar wheel (43). 17 Gear system according to any one of   claims 6 to 15, characterized in that the means   forming a freewheel (13) is placed, in the radial direction, between an outer circumferential face, in the radial direction, of said planet gear carrier (61) and an inner circumferential face, in the radial direction, of said support member (21 ) of the ring gear, on one side of said support member (21) of the ring gear away from said means stator (81).   18 Gear system according to claim 17, characterized in that the free wheel means (13) is placed, in the radial direction, outside the mounting pins (8) of the planet gears, fixed   said satellite pinion carrier (61).   19 Gear system according to claims 2 to   18, characterized in that said driving member (9) of the gear system is fixed, for rotation, on said driven member (5) of the gear system, by first means forming bearings (11) adjacent to said first end parts of said driving member (9) of the gear system and said driven member (5) thereof, and by second bearing means (15) adjacent to said second end part of said driving member (9 ) of the system   gears and said driven member (5) thereof.   Gear system according to claim 19, characterized in that at least one of said first (11) and second (15) bearing means is adapted to position, in the axial direction, said driving member (9) of the gear system and said driven member (5) of the latter, with respect to each other, in the axial direction.   21 Gear system according to claim 20, characterized in that the above-mentioned adapted bearing means (11) constitutes said first bearing means (11) and in that this means forming   bearing (11) is a means forming a ball bearing.   22 Gear system according to any one of   claims 2 to 21, characterized in that said   stop member (41) of the solar wheel is mounted, for its rotation, on said driving member (9) of the gear system, by means forming bearings (47).   23 gear system according to claim 22, characterized in that said means forming bearings (47), ensuring the fixing of said stop member (41) of the solar wheel on said driving member (9) of the gear system, are means forming ball bearings (47) adapted to position, in the axial direction, said stop member (41) of the sun wheel, with respect to said driving member (9) of the gear system. 24 gear system according to claim 23, characterized in that said stop member (41) of the sun wheel is engaged, so as to ensure a sealed closure, with said driving member (9) of the gear system , at a location further from said stator means (81) than said ball bearing means (47) ensuring the fixing of said stop member (41) of the sun wheel on said   driving member (9) of the gear system.   Gear system according to any one of   claims 2 to 24, characterized in that said member   leader (9) of the gear system is mounted, for its rotation, on said driven member (5) of the gear system, by at least one means forming roller bearings (11, 15), said means forming bearings with rollers (11, 15) comprising a group of members forming rollers, placed, in a circular manner, around said axis (A), said members forming rollers being in direct engagement, with a view to their rolling, with the rolling tracks correspondents arranged in the driving member (9) of the gear system and in the led organ (5) of the latter.   26 Gear system according to any one of   claims 6 to 25, characterized in that said member   stop (41) of the solar wheel is fixed, for its rotation, on said driving member (9) of the gear system, by at least one means forming roller bearings (43), said means forming bearings rollers (43) comprising a group of roller members, placed in a circular manner around said axis (A), said group of roller members being in direct engagement, with a view to their rolling, with the respective raceways formed in said driving member (9) of the gear system and said stop member (41) of the solar wheel.   27 Gear system according to any one of   claims 1 to 26, characterized in that said   sun wheel (43), at least one of said planet gears (65) and said ring gear (25) are housed inside a lubricant chamber (42), the latter being delimited by a chamber casing (40) , said lubricant chamber (42) being closed, in a sealed manner, by means (31, 29) ensuring a sealed closure, and being able to pivot, said chamber casing (40) comprising means forming external casing walls, in the in the radial direction, the said gear change clutch (22) being, at least partially, placed, in the radial direction, outside the said means forming the outer casing wall, in the radial direction, and overlapping the latter, in the axial direction.   28 Gear system according to any one of   claims 1 to 27, characterized in that said   lubricant chamber (42) is an annular chamber (42) around said axis (A) in which are housed at least one of said planetary gear means (25, 43, 61, 65) and said free rolling means (13) and rotatable around said axis (A) in response to rotation of said gear system driving member (9), said liquid lubricant in said lubricant chamber (42) forming a ring of lubricant (35) adjacent to the means forming external walls , in the radial direction, of said lubricant chamber (42) in response to centrifugal forces, the lubricant transport means (19) being placed inside said lubricant chamber (42) for transporting the lubricant from said ring lubricant (35) to the engagement faces of the respective elements of said gear system (4) which   are movable relative to each other.   29 Gear system according to claim 28, characterized in that said lubricant transport means comprises a lubricant collecting tube (19) having an outer end (18), in the radial direction, penetrating into said lubricant ring (35 ) and having collecting means (18) oriented in a substantially circumferential direction around said axis (A), said collecting tube (19) being able to rotate relative to said lubricant (42).   Gear system according to Claim 29, characterized in that the said lubricant chamber (42) is delimited by a chamber housing (40) fixed to the said ring gear (25), with a view to its rotation with the latter, and in that said collecting tube (19) is connected to said solar wheel (43) for a joint rotation with it.   31 Gear system according to claim 29, characterized in that said lubricant chamber (42) is delimited by a chamber casing (40), the latter being mounted, for its rotation, with said toothed ring (25) , said collecting tube (19) being mounted for rotation with said planet gear carrier (61), said collecting tube (19) being, at least partially, placed in a space orthogonal to said axis (A) and containing at least one pinion satellite (65).   32 gear system according to claim 28, characterized in that the transport means (71) comprises at least one transport disc (71) mounted, for rotation, on at least one satellite pinion (65), a corresponding circumferential part of the transport disc (71), external, in the radial direction, being immersed in said lubricant ring (35) and a corresponding circumferential part of this disc, internal, in the radial direction, being oriented towards a location ( 16) receiving lubricant droplets, said corresponding circumferential portion, external, in the radial direction, being moistened by said lubricant (35) during its immersion in said lubricant ring (35) and sending droplets towards said location (16) receiving droplets when it reaches a position adjacent to said location, when   of the rotation of the planet gear (65).   33 Gear system according to claim 32, characterized in that said location (16) receiving droplets is provided with means forming impact faces of the droplets (9, 5), the latter means dispersing the droplets towards locations (47 , 11) for engaging relatively mobile elements of said gear system (4).   34 Gear system according to any one of   claims 1 to 33, characterized in that said   gear system (4) is pre-assembled to be combined with said auxiliary current-consuming device (6) and in that said pre-assembled gear system (4) comprises an engaging member forming shaft (3) provided for fixing, by engagement, with a fixing part (32) of said input shaft (1) of the auxiliary device, said pre-assembled gear system (4) being provided to be maintained in pre-assembly state, after having been combined with said auxiliary device (6) consuming energy, by engagement of said engagement member forming a shaft (3) with said fixing part (32) of said shaft. input (1) of the auxiliary device, said pre-assembled gear system (4) being able to be fixed, in its pre-assembled state, before being combined with said auxiliary device (6) consuming energy, by a fixing member of the pre-assembly whose shape corresponds substantially to said fixing part (32) of said input shaft (1) of the auxiliary device, said pre-assembly fixing member being able to engage with said   engagement member forming a shaft (3).   35 Gear system according to any one of   claims 1 to 33, characterized in that part   (83) of said gear change clutch (22) is fixed, or adapted to be fixed, to said stator means (81), by an enveloping sleeve (85), enveloping at least part of said system gears (4).   36 Gear system according to claim 35, characterized in that said enveloping sleeve can be fixed, so that it can be released, to said stator means (81).   37 Gear system according to any one of   claims 1 to 36, characterized in that said   gear system (4) makes it possible to obtain a first transmission ratio of 1/1 and a second transmission ratio of less than 1.70 / 1 between said driven member (5) of the gear system and said driving member ( 9) of the latter, the driven member (5) of the gear system having a higher rotational speed. 38 Gear system according to any one of   claims 1 to 37, characterized in that said   gear change clutch (22) is controlled using a control member (24), in response to the speed of rotation of the driving member (9) of the gear system corresponding to the speed of a internal combustion engine driving said drive member (9) of the gear system, so that the speed of rotation of said driven member (5) of the gear system increases relative to the speed of rotation of the drive member (9) of the gear system, when the speed of rotation of the latter decreases and becomes less than a value of   predetermined speed of rotation.   39 Gear system according to claim 38, characterized in that said increase in the speed of rotation of said driven member (5) of the gear system, beyond the speed of rotation of said driving member (9) of the system 'gears, which occurs in response to the decrease in the speed of rotation thereof, becoming less than the predetermined speed of rotation value, may also occur in response to a signal (24 b) representing the need to increase the speed of rotation of said   auxiliary device (6) consuming energy.   Gear system according to any one of   claims 1 to 39, characterized in that said   auxiliary device (6) consuming energy is a generator of electric current. 41 Gear system according to any one of   claims 1 to -40, characterized in that said member   gear system driver (9) includes a pulley belt (9 a).   42 Gear system according to any one of   claims 1 to 41, characterized in that all   movable elements of said gear system are in a rest position relative to said driven member (5) of the gear system when this member (5) is directly driven from said driving member (9) of the gear system by the intermediary of said freewheeling means (13).   43 Gear system according to claim 28, characterized in that said freewheeling means (13) are, at least partially, immersed in said lubricant ring (35).   44 Gear system according to claim 28, characterized in that said ring gear (25) comprises means forming internal teeth, in the radial direction, for engagement with at least one satellite pinion (65), said tooth means being, at least partially, immersed in said lubricant ring (35).   Gear system according to claim 12, characterized in that said first housing part (21) and said second housing part (23) are connected, said ring gear (25) being fixed, in axial direction, between said first (21) and second (23) housing parts. 46 Gear system according to claim 28, characterized in that said lubricant transport means (19) comprises lubricant pouring means (44) in a position opposite to at least one bore oriented in a substantially radial direction (16 ) of a rotating hollow element (9), said hollow element (9) rotating about said axis (A) relative to said lubricant pouring means (44), said bore (16) mentioned above, oriented in a radial direction ,   having an elongated section along said axis (A).   47 Gear system according to claim 17, characterized in that said stator means (81) has a convex side wall (30) adjacent to said clutch system (4), said support member (21) of the ring gear having a flange portion (21 c) corresponding substantially to said convex side wall (30), said flange portion (21 c) being provided, at its outer end, in the radial direction, with a portion (21 d ) forming a support for the ring gear, extending in a substantially axial direction, said part (21 d) forming a support for the ring gear and said flange part (21 c) defining a transition zone, in the axial direction, between said ring gear (25) and said flange portion (21c) and adjacent, in a radial direction, to said support portion of the gear ring, said free wheel (13) being placed in the transition zone.