Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
  • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
  • F02N15/062—Starter drives
  • F02N15/063—Starter drives with resilient shock absorbers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
  • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
  • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
  • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
  • F02N15/043—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer
  • F02N15/046—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the gearing including a speed reducer of the planetary type

Definitions

• the invention relates to a motor starter with a shear absorption device.
• the invention finds a particularly advantageous application, but not exclusive, with vehicles equipped with the function of stopping and restarting the engine (function called "stop and start” in English) depending on traffic conditions.
• a combustion engine also called an internal combustion engine, in particular a motor vehicle
• a rotating electrical machine in the form of a starter provided with a launcher capable of transmitting rotational energy. from the starter to a crankshaft of the engine through a drive gear.
• This launcher is mounted on an output shaft of the electric machine.
• a speed reducer is interposed between this output shaft, constituting the launcher shaft, and the shaft of the electric motor that comprises the rotating electrical machine.
• the interposition of the reducer has the advantage of using a faster electric machine and thus obtain a higher starting torque while reducing the size and weight of the machine for a given power.
• this speed reducer can be formed by a toothed wheel in the form of a pinion fixed at one end of the shaft of the electric motor of the electric machine and a ring gear fixed in rotation by friction means of the launcher shaft; this ring having inner teeth meshing with the pinion.
• the electric motor shaft and the launcher shaft are offset relative to each other.
• the speed reducer is formed by an epicyclic gear train comprising planet gears rotatably mounted about axes carried by a planet carrier comprising a transverse plate integral with the rear end of the planet. the launcher tree. These planet gears mesh with the pinion integral with the shaft of the electric motor and with the inner teeth of the ring gear stationary in rotation relative to the housing that comprises the starter.
• the electric motor shaft and the launcher shaft are coaxial.
• the launcher comprises a pinion provided with teeth configured to mesh with teeth of the drive ring, also called start ring, rigidly or resiliently fixed to the crankshaft of the engine to start.
• This launcher can undergo significant mechanical shocks during operation of the starter, especially during the launch of the engine.
• the teeth of the pinion can slide against the teeth of the drive ring before engaging between them.
• the axial overlap of the respective teeth of the pinion and the drive ring can then be very low and the kinetic energy of rotation of the starter is abruptly transmitted to the ring gear.
• the contact stresses are very high, which can, with wear, cause the destruction of teeth of the crown. This phenomenon is known as milling.
• a conventional assembly consists of a ring of plastic material on which are molded dampers elastomeric thermoplastic material capable of being compressed during the application of an over-torque.
• the compression is effected by a relative angular displacement of the dampers integral in rotation with the ring gear with respect to compressor elements integral in rotation with the starter housing intended to bear against the dampers to compress them.
• absorption of shocks by compression implies a fairly sudden absorption of shocks to the extent that the torque absorbed as a function of the displacement angle of the ring changes exponentially, as shown in FIG. .
• Such a change in the absorbed torque results in rapid wear of the dampers during successive uses of the starter and a transmission of significant forces to the starter traction chain, which reduces its life.
• the subject of the invention is a starter for a motor vehicle engine, comprising:
• an electric motor comprising a shaft
• gear unit having a ring gear, the gear unit being installed between the shaft of the electric motor and the output shaft and rotatingly connecting the shaft of the electric motor to the output shaft;
• At least one shock absorbing device installed between the ring gear and the casing which rotates the ring gear to the casing, characterized in that the shock absorbing device is mounted to absorb, by shear, shocks suffered by the ring gear during an engine start thermal generating relative angular displacement of the ring relative to the starter housing.
• the invention thus makes it possible to damp the shocks in a more progressive manner than a damper working in compression, insofar as the absorbed torque evolves in a linear manner as a function of the rotation angle of the ring during the shearing of an element. elastic.
• the invention therefore makes it possible to increase the life of the traction chain.
• Shear absorbing device means an absorption device which is mounted to deform predominantly by shear to dampen the impact.
• the shear absorption device comprises:
• At least one elastic element having a first face rotationally fixed to the support plate and a second face opposite to the first face integral in rotation with the crown adapted to rotate relative to the housing in the event of shocks to the crown.
• the elastic element has two of these faces integral in rotation with the crown on the one hand and the housing on the other hand allows the elastic element to work significantly in shear.
• the first face of the elastic element comprises a radial surface integral in rotation with the support plate and in that the second face comprises a radial surface integral in rotation with the ring.
• Radial surface means a surface whose projection is perpendicular to the axis of the ring.
• the first face of the elastic element comprises an axial surface integral in rotation with the support plate and in that the second face comprises an axial surface integral in rotation with the ring.
• Axial surface means a surface whose projection is parallel to the axis of the crown.
• At least one of the first or second faces of the elastic element is of conical shape.
• the second face of the absorption device and mounted against a transverse wall of the ring.
• This embodiment makes it possible to arrange the damping device axially to reduce the radial space requirement.
• the shock absorbing device is mounted radially between the crown and the housing.
• This embodiment reduces the axial size of the starter.
• the shear absorbing device further comprises an insert plate secured to the second face of the elastic element, this plate being mounted integral in rotation with the transverse wall of the ring.
• the insert plate is attached to the second face of the elastic member.
• the wafer is attached to the elastic element by overmolding or gluing.
• the support plate is attached to the first face of the elastic member.
• the support plate is fixed to the elastic element by overmolding or gluing.
• the insert plate substantially covers the entire surface of the second face of the elastic element.
• the transverse wall of the crown is fixed by gluing to the second face of the elastic element. This reduces clutter.
• the transverse wall of the ring has openings for receiving pads from the insert plate. This allows for a means of fixing in easy rotation.
• the first and second faces of the elastic element are inclined with respect to each other.
• the starter further comprises a compression shock absorption device adapted to be biased when the ring exceeds an angular displacement threshold so as to limit the stress experienced by the shear absorption device.
• the shear absorbing device and the compression shock absorber are mounted in the starter so that, during an impact, the shearing device initially deforms to the angular displacement threshold and then the two shock absorbers deform to absorb the shock.
• the shear absorbing device and the compressive shock absorption device are mounted in the starter so that, during an impact, the device for absorbing shear impact is deformed in a first step up to the angular displacement threshold and then only the compression shock absorber deforms to absorb the shock.
• the shear absorbing device in the first stage (up to the tripping threshold), only the shear absorbing device deforms.
• the angular displacement threshold is between 15 and 25 degrees. This allows the shear absorption device to absorb non-abruptly part of the shock.
• the device for absorbing shocks by compression comprises at least one damper integral in rotation with one of the transverse wall of the crown and the support plate and at least one corresponding compressor element integral in rotation with the other element intended to bear against the damper during the angular displacement of the ring beyond the angular displacement threshold.
• the compression damper is integral in rotation with the support plate while the compressor element belongs to the transverse wall of the ring.
• a portion of the damper is inserted into a rigid receiving cage located on the opposite side with respect to the compressor element forming a stop.
• the damper has beveled corners on the side of the compressor element.
• the shear absorbing device comprises two diametrically opposed elastic elements having a ring portion shape.
• the compression shock absorption device comprises two dampers each located between two ends of the elastic elements facing one another and two compressor elements each located between an elastic member and a damper.
• FIG. 1 shows a graphical representation of the evolution of the absorbed torque as a function of a rotational angle of the crown of a reduction unit during an impact on the starter according to the state of the art.
• Figure 2 shows a longitudinal sectional view of a starter according to the invention
• Figures 3a and 3b show perspective views from two different angles of a ring of a gear assembly and shock absorbing devices according to the invention associated therewith;
• Figures 4a and 4b show exploded views of the front and rear of the crown and the shock absorbing devices according to the invention associated with it;
• Figure 5 is a top view of the ring and shock absorbing devices according to the invention
• Figure 6 shows a cross-sectional view along the axis A-A of the assembly of Figure 5;
• FIGS. 7a-7c represent the different states of the shock absorption devices according to the invention during the absorption of an impact on the starter according to the invention
• FIG. 8 shows a graphical representation of the evolution of the absorbed torque as a function of a rotational angle of the crown of a reduction unit during an impact on the starter according to the invention.
• the rotating electrical machine is a starter motor 10 similar to the starter described in document WO2005 / 054664, so that elements identical or similar to those of FIG. 1 of this document WO2005 / 054664, which will be referred to for more details, will be assigned the same reference signs.
• the starter comprises an output shaft 43, a launcher 30 mounted on the shaft 43 and an electric motor 1 1 composed of an inductor stator 12 and an armature rotor 13 mounted coaxially, the stator 12 surrounding the rotor 13, which is rotatably mounted about an axis 14 inside a cylinder head 15.
• the latter is secured to a metal support of the starter for attachment to a fixed part of the motor vehicle.
• the support 16 is here moldable material, for example based on aluminum and belongs to the housing of the machine.
• the stator 12 comprises in one embodiment a plurality of inductor permanent magnets carried by the inner periphery of the cylinder head 15.
• the stator 12 comprises a inductor winding 17 comprising two pairs of windings 18, which are each wound around a polar mass 19 integral with the cylinder head 15.
• the polar masses 19 are fixed with screws 20 to the cylinder head 15, here metallic, as described in FR261 1096.
• Each winding 18 is composed of a continuous conductor wound around the polar mass 19 in the direction of its thickness so as to form concentric contiguous turns of increasing diameter as best seen in FIGS. of EP749194.
• the axis of each winding 18 is radial relative to the axis 14 of the rotor 13, which constitutes the axis of rotation of the electric motor 1 January.
• the rotor 13 comprises a bundle of plates provided with grooves for mounting electrical conductors 21 in the form of pins. These conductors 21 are interconnected to form a rotor winding in connection with the conductive blades 22 belonging to a collector 23 with an electrically insulating body integral with the shaft 24 of the electric motor 11. In a variant, the winding is in continuous wire. Brushes 25 rub on the collector slats 22 of the manifold 23 to supply the rotor winding.
• the brushes 25 belong to a brush holder 26 equipped with guiding cages and receiving brushes, which are biased towards the slats 22 by means of springs 27.
• the brush holder 26 is integral with a metal rear bearing 29 having in the central part a housing for mounting a needle bearing 28.
• the bearing 29 serves for rotatably mounting the rear end of the shaft 24 of the electric motor 1 January.
• the axis of this shaft 24 coincides with the axis 14 of the rotor 13, and with the axis of the output shaft 43 of the starter constituting the shaft of the launcher 30.
• the rear bearing 29 serves as a centraliser rear end of the cylinder head 15, and is connected by rods 31 to the support 16 of the starter 10. Two threaded holes (not referenced) are formed in the support 16 for screwing the tie rods.
• the tie rods 31 are located outside the cylinder head
• the metal cylinder head is interposed between the metal support 16 and the metal rear bearing 28.
• the starter housing thus comprises the bearing 28, the cylinder head 15 and the support
• the starter 10 also comprises an electromagnetic contactor 32 extending parallel to the electric motor 1 1 being implanted radially above it.
• the contactor 32 has a metal tank 33 carried by the support 16, and equipped with an excitation coil B provided with at least one winding.
• the tank 33 is closed at the rear by a cover 34 made of electrically insulating material.
• the fixing of the cover 34 is made by folding the material of the free end of the tank 33.
• a shoulder of the tank 33 ensures the axial setting of a fixed core 35, which is wedged axially in the other direction by the cover 34 carrying terminals 36, 37 of power supply.
• the terminals 36, 37 are shaped to each form a fixed contact 38 inside the cover 34.
• One of the terminals 36 is intended to be connected to the positive terminal of the battery, the other 37 is connected by the intermediate of a cable 39 at the input of the inductor winding 17 of the stator and brushes 25 of positive polarity.
• a mobile core 40 is attracted by magnetic attraction towards the fixed core 35 to, firstly, act after catching a game on a rod (not referenced) carrying a movable contact (not referenced) to cause the closure of the contacts of the contactor 32 and supply the electric motor of the starter, and, on the other hand, operate a lever 41 for controlling the starter.
• the output shaft 43 is rotatably mounted in a bearing 42 before the support 16.
• This bearing 42 is constituted by way of example by a needle bearing alternatively by a plain bearing.
• This shaft 43 carries at the front a stop 53 adjacent to the bearing 42 to limit the movement of the launcher 30.
• the rear end of the shaft 43 is configured to be secured to a plate of a planet carrier 47, for example by crimping, this planet carrier 47 belonging to an epicyclic gear train constituting the speed reducer 45 gear.
• This planet carrier 47 carries satellites 47.1 meshing on the one hand with a ring 46 (described in more detail below) and with a sun gear 51 integral with the front end of the shaft 24 of the electric motor.
• the gearbox 45 is of the type described in FR2787833 to which reference will be made, the latter showing the mounting of the front end of the shaft 24 of the electric motor 1 1 in the rear end of the shaft 43 with a blind hole in which is housed the front end of the shaft 24 with the interposition of a plain bearing and a ball.
• the satellites 47.1 are therefore rotatably mounted each about an axis. These axes extend between two plates of transverse orientation relative to the axis of the shaft 43 being carried by these plates, one of which is thicker than the other and is here fixed by crimping to the rear end of the shaft 43.
• the planet carrier 47 comprises a single plate fixed to the rear end of the shaft 43 and carrying the axes.
• the launcher 30 is slidably mounted on the output shaft 43, and comprises a drive gear 50, a driver 51 configured to be actuated by the control lever 41 pivoting, and a free wheel 52 with rollers interposed axially between the 51 and the pinion 50.
• the teeth of the pinion 50 belong to a sleeve extended at the rear to form the cylindrical inner track of the free wheel 52 roller.
• the driver 51 is extended axially at the front by a bushing configured internally to form the profiled outer track of the freewheel 52 with wheels and house the springs acting in known manner on the rollers. More specifically, the driver 51 comprises a sleeve integral with the front of a flange of transverse orientation relative to the axis of the shaft 43.
• This flange is integral at its outer periphery with the sleeve of axial orientation by relative to the axis of the shaft 43 for forming a roller receiving cage closed at the front by washers.
• the driver 51 carries a washer (not referenced) defining with the flange of the driver 51 a groove for receiving the fingers of the lower end of the lever 41 fork-shaped.
• the upper end of the lever 41 is mounted in known manner to articulation on a rod (not referenced in Figure 2) elastically connected to the movable core 40 via a spring housed in the movable core 40.
• the lever 41 is mounted to hinge on the movable core 40 and the spring surrounds the sleeve of the trainer by bearing on the flange of the coach as described for example in DE2822165.
• the sleeve of the driver 51 is internally provided with helical splines (not referenced) in complementary engagement with external helical teeth carried by the output shaft 43 in the vicinity of its rear end here cylindrical and moreover large diameter.
• the launcher 30 is thus animated by a helical movement when it is moved by the lever 41 in the direction of the stop 53 to come, via its pinion 50, in engagement with the drive ring, called the crown of starting (not shown), a heat engine also called internal combustion engine.
• the freewheel device 52 can be replaced by a conical clutch coupling device, of the type described in document FR2772433 or a clutch with several disks.
• the launcher 30 variant is implanted in part outside the support 16 at the front thereof. More precisely, the pinion 50 of the launcher 30, instead of being implanted in the support (see FIG. 2), can be implanted outside the support as can be seen for example in the document FR2745855 to which reference will be made for more information. details.
• the control lever 41 is coupled, here elastically in a variant rigidly in the aforementioned manner, by its upper end to the movable core 40 of the contactor 32, and comprises in its middle part a pivot axis 54, which according to a characteristic is distinct, the toothed gear gear reducer gear ring 46 due to the structure of the assembly described below.
• the lever 41 is in a molded part, preferably made of rigid thermoplastic material to reduce noise, preferably reinforced by fibers.
• the mounting of the pivot pin 54 is for example carried out using a support piece as in DE2822165 and FR2787833 or in the support 16 provided with projections for this purpose, the axis 54 being distinct or integrated in the lever 41.
• a sealing pad 158 of elastomer to absorb dimensional variations.
• This stud 158 is in contact with the contact surface of the contactor and is integral with a plastic part 155 configured to replace the tongue or tabs 55 of Figure 1 of WO2005 / 054664; the housing of the support 16 being retained.
• the pad 158 is removed and it is the plastic part 155 which is then in contact with the contact surface of the contactor.
• the solution described in WO01 / 31195 can also be used. It all depends on the applications.
• the ring 46 of the X-axis speed reducer 45 coincides with the axis 14 is of hollow form and has a wall 58 transverse to the outer periphery of which extends an annular skirt 46.1 of axial orientation provided with inner teeth meshing with satellites 47.1.
• This transverse wall 58 is pierced centrally and mounted on a hub 68 reported to ensure its centering.
• the hub 68 has at its center a through opening allowing the passage of the shaft 43.
• the skirt 46.1 is axially oriented relative to the axis X and therefore has a cylindrical shape.
• the teeth 46.4 of the skirt 46.1 have an axial orientation.
• the ring 46 is closed at the rear by a cover 200 (see Figure 2).
• the inside of the ring 46 can thus be filled with lubricating grease of the satellites 47.1 and the sun gear 49.
• the starter 10 comprises a shock absorbing device 61 installed between the ring gear 46 and the starter housing, in this case the carrier 16, adapted to absorb shear shocks suffered by the ring 46 during overtemperature generated by the start of the engine.
• the device 61 comprises an annular support plate 62 also of X-axis having, on one of its radially oriented faces, pins 64 intended to be inserted. within the not shown openings made in the support 16.
• the support plate 62 is thus integral in rotation with the support 16 and thus with the starter housing.
• the pins 64 are angularly distributed regularly at the outer periphery of the support plate 62. In this case, these six pins 64 have a parallelepiped shape.
• a central opening 67 of the support plate 62 allows the passage of the shaft 43.
• the support plate 62 is for example made of metal and the pins 64 are made of material with the support plate 62.
• the support plate 62 further comprises an indexing means 65 formed by a recess shown in FIG. 3a made at its outer periphery for cooperating with a projection of the support 16. This facilitates the angular positioning of the plate 62 by report to support 16.
• the support plate 62 is devoid of pins 64 and has an annular shoulder 66 at its axially oriented outer periphery and a lug 78 of generally rectangular shape for its indexing and its connection in rotation with the support 16.
• the lug 78 is intended to cooperate with a housing, not shown, of complementary shape formed in the support 16.
• the support plate 62 also comprises an annular sleeve 79 X axis delimiting the opening 67 on which is positioned the ring 46.
• the shock absorption device 61 also comprises two elastic elements 69 fixed on a radial face of the support plate 62 opposite the face comprising the pins 64 or the shoulder 66.
• the fixing of the elastic elements 69 on the support plate 62 is effected for example by bonding a face 70 of the elastic elements 69 to the support plate 62.
• Each elastic element 69 has, for example, a portion shape. annular extending for example on an angle A of the order of 1 12 degrees.
• Each elastic element 69 has an inner radius R1 greater than an outer radius R2 of the sleeve 79 and an outer radius R3 slightly smaller than an outer radius R4 delimiting the plate 62.
• the elastic elements 69 are for example made of rubber.
• the elastic elements 69 have for example a Shore hardness of between 72 and 73 ShA at 80 degrees Celsius.
• an insert plate 71 is integral with a face 72 of each elastic element 69 opposite the face 70 fixed to the support plate 62.
• This plate 71 follows an outer contour of the face 72. (See Figure 4a or 7a) so that the plate 71 has substantially the same surface as the face 72. In other words, the plate 71 substantially covers the entire surface of the face 72.
• the face 72 of the elastic element 69 carrying the wafer 71 is inclined relative to the face 70 fixed to the support plate 62. The stresses experienced by the material during shearing of the elastic elements 69 are thus homogenized.
• the face 70 extends in a plane
• the face 72 is inclined with respect to the inward face 70 of the plate 62 so that the cross-section of each member 69 tends to decrease as one moves from one to the other. outside to the Inside the plate 62.
• the angle of inclination B 'of the two faces relative to each other is for example of the order of 5 degrees.
• the face of the wafer 71 attached to the element 69 has a corresponding inclination.
• the plates 71 take for example each in the form of a thin plate made of metal.
• the transverse wall 58 of the ring 46 is made integral in rotation with the plate 71.
• the wall 58 has openings 74 intended to receive studs 75 coming from the plates 71.
• each plate 71 comprises three studs 75 positioned on the same circumference between the inner periphery and the outer periphery of the elastic element 69. These pads 75 are intended to cooperate with two sets of three diametrically opposed openings 75 formed in the transverse wall 58 of the ring 46 (see Figure 5).
• the transverse wall 58 is fixed by gluing to the wafer 71.
• the starter 10 further comprises a compression damping device 80 biased when the ring 46 exceeds a threshold K1 angular displacement.
• the threshold K1 of angular displacement is between 15 and 25 degrees and is preferably of the order of 23 degrees.
• the device 80 comprises two dampers 81 integral in rotation with the support plate 62 used in combination with two compressor elements 82 integral in rotation with the ring 46.
• each compressor element 82 is spaced angularly by relative to the damper 81 of an angle C equal to the threshold K1 of angular displacement (see Figure 7a).
• Each compressor element 82 is thus intended to bear against the damper 82 when the angular displacement of the ring 46 exceeds the threshold K1.
• a portion of each damper 82 is inserted inside a rigid receiving cage 84 located on the opposite side to the compressor element 82 associated therewith. The cage 84 thus forms a stop, so that when a compressor element 82 acts on a damper 81, the latter is compressed between the cage 84 and the compressor element 82.
• the dampers 81 are diametrically opposite one another and have a ring portion shape. As shown in FIG. 4a, the ring portions extend over an angle D at least two times smaller than the angle A on which the elastic elements 69 extend.
• the inner and outer radii respectively delimiting the internal periphery and External shock absorbers 81 are substantially identical to those R1, R3 of the elastic elements 69.
• Each damper 81 has bevelled angles on the side of the compressor element 82. The bevel is made on an angle E shown in Figure 7a worth for example 10 degrees.
• Each damper 81 is positioned between two ends of the elastic elements 69 facing one another.
• the dampers 81 are fixed to the support plate 62 by means of tabs shown from the support plate 62 entering the dampers 81.
• the dampers 81 are for example made of elastomeric thermoplastic material.
• the compressor elements 82 take for example the form of ribs coming from material with the support plate 62. These ribs of substantially parallelepiped shape have a trapezoidal section.
• the elastic elements 69, the dampers 81 and the compressor elements 82 have a substantially identical height L, as is clear from Figures 3a, 3b, and 4a.
• the operation of the shock absorption system according to the invention is described below with reference to FIGS. 7a to 7c.
• FIGS. 7a to 7c show the states of only one of the elastic elements 69 and only one of the dampers 81 but it is clear that the other elastic element 69 and the other damping 81 not shown have corresponding states.
• the compressor element 82 is connected in rotation with the transverse wall 58 of the ring 46 which has not been shown for the sake of clarity.
• the representation of the support plate 62 is also simplified.
• the dampers 81 may be made integral in rotation with the transverse wall 58 of the ring 46, while the compressor elements 82 are made integral in rotation with the support plate 62.
• the number of elastic elements 69 may be greater than or less than two and in all cases at least one. It depends on the application. It is the same for the number of dampers 81 of the device 80 which may vary depending on the application.
• the starter could also comprise only a shear absorbing device 80 and be devoid of device 61 for compressive shock absorption.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
• Gear Transmission (AREA)

Applications Claiming Priority (2)

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• 2012
  • 2012-11-08 FR FR1260590A patent/FR2997732A1/fr not_active Ceased
• 2013
  • 2013-11-08 WO PCT/FR2013/052675 patent/WO2014072651A2/fr not_active Ceased
  • 2013-11-08 EP EP13801642.3A patent/EP2917558B1/de not_active Not-in-force

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