EP2655863B1 - Elektromotor und brennkraftmaschine starter getriebe - Google Patents

Elektromotor und brennkraftmaschine starter getriebe Download PDF

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Publication number
EP2655863B1
EP2655863B1 EP11817389.7A EP11817389A EP2655863B1 EP 2655863 B1 EP2655863 B1 EP 2655863B1 EP 11817389 A EP11817389 A EP 11817389A EP 2655863 B1 EP2655863 B1 EP 2655863B1
Authority
EP
European Patent Office
Prior art keywords
hub
washer
shoulder
assembly according
ring gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP11817389.7A
Other languages
English (en)
French (fr)
Other versions
EP2655863A1 (de
Inventor
Marius Drozdek
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Equipements Electriques Moteur SAS
Original Assignee
Valeo Equipements Electriques Moteur SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Equipements Electriques Moteur SAS filed Critical Valeo Equipements Electriques Moteur SAS
Publication of EP2655863A1 publication Critical patent/EP2655863A1/de
Application granted granted Critical
Publication of EP2655863B1 publication Critical patent/EP2655863B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
    • F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
    • F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
    • F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
    • 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
    • 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
    • F02N15/065—Starter drives with blocking means

Definitions

  • the invention relates to an assembly for a speed reducer of a rotary electric machine, for example of a thermal engine starter, in particular for a motor vehicle, and a motor starter.
  • 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 rotationally fixed by friction means of the thrower 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 secured to the rear end of the starter shaft.
  • 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 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.
  • the demand FR-2 631 094 discloses a torque limiter adapted to a speed reducer formed of the aforementioned crown and pinion assembly.
  • the limiter comprises a spline hub for its connection in rotation with the output shaft of the starter constituting the starter shaft.
  • the ring gear is rotatably mounted via its flange on a bearing surface of the hub.
  • the hub is provided with a sail attached by crimping on the hub or in one piece with it.
  • the web constitutes a friction disk for the limiter, which comprises elastic means with axial action in the form of an elastic washer with axial action, a friction lining and a bearing flange for the washer.
  • the bearing flange is connected to the flange of the crown by means of spacers traversed by screws.
  • An object of the invention is to create a hub torque limiter that can be used with an epicyclic gearbox with axially acting resilient means exerting a bias on a larger diameter for a better distribution of the forces on the friction disc.
  • the speed reducer comprises a hub in one piece with a flange extended at its outer periphery by a cylindrical portion in which is engaged the ring gear of the reducer.
  • the speed reducer comprises a base plate rotatably connected to the starter housing, and a ring gear bearing against the base plate and rotatable relative to the base plate when the ring gear is subject to a torque greater than a predetermined torque.
  • the ring gear comprises a transverse wall having orifices of frustoconical shape, the base plate which is provided with form bosses complementary being subjected to the action of an elastic washer with axial action.
  • the object of the invention is to improve this system by simplifying in particular the production of the crown.
  • a force loop is thus created according to which the elastic means with axial action, such as an elastic washer, which bear on the first shoulder, exert an axial compressive force in the direction of the transverse wall of the ring; while the second shoulder retains in translation the wall of the ring, so that the base plate is sandwiched between the washer and the transverse wall.
  • the crown is thus immobile in rotation with respect to the base plate when normal forces are applied to the crown.
  • the transverse wall can turn around the axis of the hub by rubbing against the base plate, where appropriate by means of at least one lining, to limit the torque applied to the starter and protect the components of the electric machine.
  • the solution according to the invention takes advantage of the hub which performs several functions and simplifies the speed reducer which uses simple parts, including a ring gear secured to a transverse wall unlike that described in the document EP 1 094 246 .
  • the solution according to the invention is more compact, especially axially.
  • the elastic means with axial action are supported indirectly on the first shoulder by means of a closure washer bearing on the first shoulder and positioned in a groove formed around the hub.
  • the assembly comprises bayonet type mounting means capable of ensuring cooperation between the first shoulder and the closure washer.
  • the first shoulder is constituted by folding the hub material.
  • the ring being made of a plastic material, this ring is overmolded at the outer periphery of the transverse wall.
  • the transverse wall having through openings the ring comprises studs passing through these openings, these pads opening on an outer face of the transverse wall opposite an inner face from which the teeth of the crown extend.
  • the base plate is in direct support on the studs of the crown.
  • the assembly comprises a friction lining interposed between the transverse wall of the crown and the base plate.
  • the assembly further comprises a friction lining positioned between the base plate and the elastic washer with axial action.
  • the friction lining (s) are rotatably connected to the hub.
  • the hub has at least one flat and in that the friction lining or seals have an opening with at least one complementary shaped flat for connection to rotation with the hub by cooperation of shapes.
  • the hub comprises a section having four flat pairs parallel to each other connected by means of cylindrical portions, the friction pad or seals having a complementary shape opening.
  • the one or more gaskets are glued to side faces of the base plate.
  • the second shoulder is divided into several parts belonging to the hub and each having a bearing surface.
  • the bearing surfaces of the parts are angularly offset relative to the flats.
  • the cylindrical portions are each connected to a portion belonging to the hub.
  • the transverse wall has a central opening and is hollowed at its central opening for forming four flanges for receiving parts.
  • the assembly comprises a dissipation washer of the forces associated with the elastic means with axial action.
  • the axial-action elastic means consist of an axially-acting elastic washer comprising a Belleville-type washer.
  • the hub has at its center a through opening allowing passage of the output shaft of the starter, in that the pinion belongs to a launcher having a driver, in that the through opening comprises two separate cylindrical parts by an inner annular portion of smaller internal diameter than the other two cylindrical portions and in that the inner annular portion constitutes a stop for cooperating with the rear face of the driver.
  • the rotating electrical machine is a starter motor 10 similar to the starter described in the document WO 2005/054664 , so that the elements identical or similar to those of the figure 1 of this document WO 2005/054664 , to which reference will be made for more details, will be assigned the same reference signs.
  • this figure 1 it is shown that a portion of the rear end of the output shaft 43 and a portion of the speed reducer 45 visible in the Figures 2 and 3 .
  • This speed reducer 45 belongs according to the invention to a speed reduction unit 57 described below.
  • the starter comprises in this embodiment an output shaft 43, a launcher 30 mounted on the shaft 43 and an electric motor 11 composed of an inductor stator 12 and a rotor 13 induced coaxially mounted, 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 the support 16 metallic 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 inductive permanent magnets carried by the inner periphery of the cylinder head 15.
  • the stator 12 comprises an 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 the document FR-A-2,611,096 .
  • 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 better visible in the Figures 2 to 5 of the document EP A 749 194 .
  • 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 11.
  • 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.
  • the 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 28 having in the central portion a housing for mounting a needle bearing 29.
  • the bearing 28 serves for rotatably mounting the rear end of the shaft 24 of the electric motor 11.
  • the axis of this shaft 24 is coincident 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 28 serves as a centering device at the 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 for screwing the tie rods.
  • the tie rods 31 are located outside the cylinder head 15. Here a small clearance exists between the tie rods and the outer periphery of the cylinder-shaped cylinder head 15.
  • 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 16. This casing is intended to be connected to the mass of the vehicle. automobile via its support 16.
  • the starter 10 also comprises an electromagnetic contactor 32 extending parallel to the electric motor 11 by being radially implanted 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, firstly, to act after catching a game on a rod (not referenced) bearing a movable contact (not referenced) to cause the closing of the contacts of the contactor 32 and supply the electric motor of the starter, and, secondly, actuate a lever 41 for controlling the launcher 30.
  • 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 has a stop at the front 53 adjacent to the bearing 42 to limit the movement of the launcher 30.
  • the rear end 43.2 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 49 integral with the front end of the shaft 24 of the electric motor.
  • the gearbox 45 is of the type described in the document FR 2 787 833 which will be referred to, the latter showing the mounting of the front end of the shaft 24 of the electric motor 11 in the rear end 43.2 of the shaft 43 having a blind hole in which is housed the front end of the shaft 24 with the interposition of a plain bearing and a ball.
  • This conventional assembly is also visible in the figure 9 .
  • 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 43.2 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 outer race of the free wheel 52 roller.
  • the driver 51 is axially extended at the front by a bushing configured internally to form the profiled outer track of the freewheel 52 to rollers 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 coach 51 carries a washer (not referenced) defining with the flange of the coach 51 a groove for the receiving the fingers of the inner end of the fork-shaped lever 41 as best seen in the figure 3 .
  • the upper end of the lever 41 is mounted in known manner to articulation on a rod (not referenced to the figure 1 ) elastically connected to the movable core 40 via a spring housed in the movable core 40.
  • the lever 41 is hingedly mounted on the movable core 40 and the spring surrounds the sleeve of the driver by bearing on the flange of coach as described for example in the document DE 28 22 165 .
  • the sleeve of the driver 51 is internally provided with helical splines (not referenced) in complementary engagement with external helical gears, referenced in 43.1 at the figure 2 , carried by the output shaft 43 in the vicinity of its rear end 43.2 here cylindrical and larger 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 into the position of the Figures 2 and 3 , through its pinion 50, engaged with the drive ring, called the start ring (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 the document FR-A-2,772,433 or a clutch with multiple disks.
  • the launcher 30 variant is implanted in part outside the support 16 at the front thereof. More specifically, the pinion 50 of the launcher 30, instead of being implanted in the support ( Figures 1 to 3 ), can be implanted outside the support as visible for example in the document FR A 2,745,855 to which we will refer.
  • 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 ring 46 due to the structure of assembly 57 described below.
  • the lever 41 is in one piece molded, preferably rigid thermoplastic material to reduce noise, preferably reinforced with fibers.
  • the mounting of the pivot axis 54 is for example made using a support piece as in the documents DE 28 22 165 and FR 2 787 833 or in the support 16 provided with projections for this purpose, the axis 54 being separate or integrated in the lever 41.
  • a sealing pad 158 of elastomer to absorb the dimensional variation.
  • This stud 158 is in contact with the contact face 157 of the contactor and is integral with a plastic part 155 configured to replace the tongue or tabs 55 of the figure of the figure 1 of the document WO 2005/054664 ; the housing of the support 16 being retained.
  • the pad 158 is removed and it is the plastic part 155 is then in contact with the face 157. It can also appeal to the solution described in the document WO 01/31195 . It all depends on the applications.
  • the ring 46 of the speed reducer 45 is of hollow form and is part of an assembly 57 comprising a transverse wall 58 integral with the ring 46, a base plate 60 rotatably connected with the support 16 of the starter, the pads 61 , 62 of friction positioned on either side of the plate 60, elastic means with axial action, in the form in the Figures 2 to 9 an axially acting spring washer 64, used in combination with a disc 65 for dissipating forces and a washer 67 for closing.
  • the elements 58, 60, 61, 62, 64, 65 and 67 are mounted, according to one characteristic, on a hub 68 reported to ensure their centering.
  • This hub 68 carries at least one first shoulder 71 for directly or indirectly supporting the spring washer 64, and at least one second shoulder 72, in the Figures 2 to 8 to support the transverse wall 58 of the ring 46.
  • the shaft 43 of the launcher 30 is rotatably mounted inside the hub 68 via a bearing 85 intervening between the outer periphery of the rear end 43.2 cylindrical of the shaft 43 and the inner periphery of the hub 68.
  • This hub 68 is a stepped diameter bearing hub, as best seen in the figures 4 and 6 , which according to one characteristic is centered relative to the rear end 43.2 of the shaft 43 via the bearing 85, which here is a plain bearing, such as a bearing.
  • Elements 58, 60, 61, 62, 64, 65 and 67 are centrally holed.
  • the centering hub 68 of the elements 58, 60, 61, 62, 64, 65 and 67 is associated with the wall 58, which makes it possible to preserve the structure of the ring 46.
  • the base plate 60 is simplified relative to to those of the document FR 2 924 872 .
  • the forces on the wall 58 are well distributed, which makes it possible to protect the ring 46.
  • the elastic washer 64 with axial action of the Figures 2 to 5 acts at its outer periphery over a large diameter so that the forces are well distributed on the lining 61, 62, the base plate 60 and the wall 58.
  • the hub 68 has an axially oriented axis of symmetry X coinciding with the axis of axial symmetry of the shaft 43.
  • the elements 58, 60, 61, 62, 64, 65 and 67 are of transverse orientation by relation to this axis X; the spring washer 64 being inclined axially.
  • This bearing hub 68 has on the side of its forward axial end 69, the closest to the driver 51, a first axial section 68.1 in which is formed a groove 74 annular.
  • This groove 74 is intended to receive the inner periphery of the closure washer 67 and is delimited at the front by a transverse flange 71 with respect to the axis of the shaft 43 adjacent to the front end 69 of the hub 68.
  • This flange 71 forms the first shoulder 71 and is configured, as described below, to allow bayonet type mounting of the closure washer 67 in the groove 74.
  • the hub 68 has a second cylindrical axial portion 68.2 extending in the extension of the first section 68.1 to the projecting front end 76 of a third section 68.3 axial delimiting the rear end of the second section 68.2 and forming a shoulder.
  • This second section 68.2 is intended to accommodate the spring washer 64.
  • This section 68.2 forms the rear flank of the groove 74, whose front flank is constituted by the rear end face of the shoulder 71.
  • this embodiment of the elastic washer 64 bears indirectly on this shoulder 71 via the sealing washer 67 abuts against the shoulder 71.
  • the length L ( Figure 5 ), which extends between the front end 76 of the third section 68.3 and the rear face 67.1 of the closing washer 67 against which the washer 64 bears, constitutes the working length of the spring washer 64, which is here a Belleville washer. This length L is less than the length L 'which exists between the rear face of the washer 67 and the front face of the wall 58.
  • the third axial section 68.3 extends the second section 68.2 to the rear axial end 70 of the hub. 68 constituting in the embodiment of the Figures 2 to 8 the rear end face of a projecting shoulder 72 constituting the second shoulder.
  • This third portion 68.3 extends between the protruding end 76 of the second section 68.2 forming a shoulder and the second projecting shoulder 72.
  • the hub 68 is thus axially stepped; its third section 68.3 protruding radially from the second section 68.2 delimiting the groove 74 of the first section 68.1.
  • the third section 68.3 comprises at least one flat, while in one embodiment the wall 58, the disk 65 and the washers 61, 62, have a central opening respectively 58.3, 65.3, 61.3 provided with at least one complementary flat to cooperate in shape cooperation with the flat portion 68.3 for blocking rotation of these parts 58, 65, 61, 62 with the possibility of axial movement depending in particular on the wear of the liners 61, 62.
  • shoulder 72 is continuous and the rear face 58.2 of the wall 58 is in contact with the front face of this shoulder 72 of annular shape.
  • the shoulder 72 is split into four projecting portions 77 distributed circumferentially in a regular manner to reduce the axial bulk of the assembly 57 as described below.
  • the front faces 77.1 of each of these parts 77 form a bearing surface against which comes into contact a flange 58.5 of similar shape of the transverse wall 58 formed at the central opening 58.3 of the wall 58.
  • the wall 58 presents therefore four flanges 58.5 constituting in one embodiment the bottom of recesses 58.6 formed by removal of material or alternatively by material embossing on the side of the rear end 70 of the hub 68.
  • the hub 68 thus has a bearing function.
  • the third section 68.3 receives the wall 58, the washers 61, 62, the disk 65 which are intended to be connected in rotation with the hub 68 via this third section 68.3 presenting in the embodiment of the Figures 2 to 9 four flats 79.1 parallel in pairs, that is to say diametrically opposed, interconnected by means of cylindrical portions 80.1 of greater diameter than the second section 68.2; while (See figure 4 ) the transverse wall, the lining 61, 62 and the dispersion disk 65 have an internal opening 58.3, 61.3, 62.3, 65.3 of complementary shape for their locking in rotation relative to the hub 68.
  • the cylindrical parts are connected to the The flats 79.1 each have a surface parallel to the axis X.
  • the parts 77 and therefore the bearing surfaces 77.1 are angularly offset relative to the flats 79.1 on the circumference of the hub 68.
  • the hub 68 thus has a locking function in rotation of the washers 61, 62, the wall 58 and the disc 65.
  • This hub 68 also receives rotation, on the one hand, the spring washer 64, interposed between the washer 67 and the disc 65 rotated on the hub 68, and secondly, the base plate 60 in the manner described below
  • the solution with four flats 79.1, four cylindrical portions 80.1 and four bearing surface 77.1 allows get more effective and reliable locking in rotation with only one flat while having a good support for the wall 58 and a reduced bulk at the shoulder 72 divided into four parts 77.
  • the shoulder 72 has a substantially square shape with a rounded angle due to the presence of the flats 79.1 and parts 77 each with circular outer periphery and lateral edges, which constitute a transverse extension of the flats 79.1.
  • the outer diameter of the parts 77 is greater than that of the parts 80.1.
  • the hub 68 has in its center a through opening 68.4 allowing passage of the shaft 43 of the launcher.
  • This opening 68.4 comprises two coaxial cylindrical portions 81, 82 of different diameter separated from each other by an internal annular portion 83 (see FIG. Figures 4 and 5 ) of smaller internal diameter than the parts 81, 82.
  • the portion 81 of larger internal diameter located on the side of the ring 46 (or the side of the second shoulder 72), is intended to receive the annular bearing 85 ( Figure 2 and 4 ) resting on the shoulder formed by the change in diameter between the portion 81 and the inner annular portion 83.
  • the inner diameter of the bearing 85 is greater than the internal diameter of the portion 83. As visible in FIG.
  • the shaft 43 has a cylindrical section 43.3 interposed between its cylindrical rear end 43.2 and its helically fluted section 43.1.
  • the diameter of the section 43.3 is generally equal to that of the section 43.1 and smaller than that of the section 43.2.
  • the axial length of the section 43.3 is generally equal to the axial length of the inner portion 83 of the hub 68.
  • the section 43.3 enters a mounting clearance in the inner part 83. It follows from the foregoing that the front face of the end 43.2 can bear against the rear face of the inner part 83.
  • the front face of the inner part 83 serves as a stop on the rear face of the driver 51 when the launcher is in the retracted position of rest, knowing that in the figure 2 the launcher is in advanced meshing position with the drive crown.
  • the reclining rest position of the launcher 30 and the coach is visible at the figure 1 of the document WO 2005/054664 .
  • the front face of the inner portion 83 is substituted for the shoulder of the rear end of the shaft 43 of this document; the internal diameter of the cylindrical portion 82 being a function of the outer diameter of the cylindrical rear end of the driver so that this end can enter the portion 82 so that the rear face of the driver 51 abuts against the part 83
  • the inner part 83 thus makes it possible to protect the output shaft 43.
  • the ring 46 hollow in shape and carried by the transverse wall 58, has an annular skirt 46.1 internally toothed to mesh with the satellites 47.1.
  • the skirt 46.1 is axially oriented relative to the axis of the shaft 43 and therefore has a cylindrical shape.
  • the teeth 46.4 of the skirt 46.1 have an axial orientation.
  • the ring 46 is preferably made of a plastic material, preferably reinforced with fibers, to minimize the noise of the gearbox.
  • the skirt 46.1 is extended at its front end by an internal rim 46.3, transversely oriented relative to the axis X and to the axis of the shaft 43.
  • This flange 46.3 projects radially inwards relative to the teeth 46.4 of the skirt 46.1 and is intended to bear on its front face against the rear face 58.4 of the wall 58.
  • the transverse wall 58 is made of a metallic material and is configured to serve as a friction face via its front face for the friction washer 61.
  • the crown assembly 46-wall 58 is therefore in this bi-material embodiment.
  • the ring 46 is overmolded at the outer periphery of the transverse wall 58.
  • the transverse wall 58 having openings 58.1 through, the ring 46 has studs 46.2 through these openings 58.1 which open on a front face 58.2 of the wall 58 opposite a rear face 58.4 of the wall 58 from which the teeth extend. of the ring 46.
  • the front end of the pads 46.2 forming projecting heads with respect to the front face 58.2 of the wall 58, is crushed in contact with the front face 58.2 of the wall 58 for fixing the ring 46 and contact the front face of the flange 46.3 thereof with the rear face 58.4 of the wall 58 of outer diameter greater than that of the ring 46 being close to the outer diameter of the ring 46.
  • the thickness of the friction washer 61 is in this embodiment greater than the thickness of the heads 46.2 studs implanted annularly outside the outer periphery of the friction washer 61, which is adapted to rub against the front face 58.2 of the wall 58, more precisely against the surface of the front face 58.2 of the wall 58 implanted inside the studs 46.2 and holes 58.1.
  • the internal flange 46.3 is intended to form a spacer between the flange of the planet carrier 47 fixed, here by alternately crimping by welding or riveting, on the rear end 43.2 of the shaft 43 and the wall 58.
  • the crown 46 is closed at the rear by a cover 100 fixed to centering with a flange of axial orientation (not referenced) on the rear end of the support 16 as visible in the Figures 2 and 3 .
  • the cover 100 comprises at the rear a socket (not referenced) for receiving here a needle bearing (not referenced) interposed radially between the sleeve of the cover 100 and a bearing of the shaft 24 as visible in the figure 2 .
  • this cover is interposed between the rear end of the support 16 and the front end of the cylinder head 15.
  • the inside of the ring 46 can thus be filled with lubricating grease of the satellites 47.1 and the pinion. solar 49.
  • the hood is of the type of that of the figure 1 everything depends on the applications and in particular the shape of the cylinder head 15.
  • the transverse wall 58 is connected in rotation with the hub 68 by cooperation of forms.
  • the wall 58 has a central opening 58.3, which has a shape at the front. complementary to that of the third section 68.3 of the hub 68 for mounting the wall 58 on the hub 68 by axial threading back and forth.
  • This opening 58.3 is therefore delimited at the front by four flats of complementary shape to the flats 79.1 of the hub 68 and interconnected by means of four cylindrical portions of shape complementary to the cylindrical portions 80.1 of the hub 68.
  • the opening 58.3 presents at the rear a substantially square shape with rounded corners of complementary shape to the shoulder 72 as best visible in the figure 4 .
  • the rear face 58.4 of the wall 58 is cut to form four notches 58.6 flanges 58.5 positioned at the four corners of the opening 58.3.
  • These rims 58.5 are, in a aforementioned manner, intended to abut in complementary manner against the corresponding bearing surfaces 77.1 of the hub 68.
  • These bearing surfaces 77.1 belong to the parts 77 in the form of projections housed in the notches 58.6 to complementary rims 58.5 for reducing the axial size and forming a barrier to prevent the passage of grease.
  • the wall 58 in cooperation with the hub 68, prevents the grease contained in the ring 46 from contaminating the gaskets 61,62.
  • the base plate 60 of transverse orientation and which has two end faces 60.1, 60.2 respectively front and rear, has at least one lug 60.34 for example of rounded shape, intended to cooperate with a groove 88 of axial orientation of support 16 of complementary shape ( Figure 2 ), so as to make the base plate 60 immobile in rotation with respect to the support 16.
  • the plate 60 is able to move in translation relative to the support 16 following the particular wear of the fittings 61, 62.
  • the plate 60 has an opening central 60.3 configured so that the plate 60 is not rotatably connected to the hub 68.
  • the opening 60.3 has a circular shape having a diameter greater than that of the cylindrical portions 80.1 of the third section 68.3.
  • a mounting clearance exists between the plate 60 and the parts 80.1 to allow a relative rotation between the plate 60, integral in rotation with the fixed support 16.
  • the face 60.1 constitutes the front face of the plate and the face 60.2 the rear face of the plate 60
  • the gaskets 61, 62 positioned on either side of the plate 60 have a first respectively front and rear face 61.1, 62.1 respectively in contact with the rear face 60.2 and the front face 60.1 of the plate 60 and a second face 61.2, 62.2 opposite the first face 61.1, 62.1.
  • the second face 61.2 of the lining 61, constituting the rear face thereof is in contact with the front external surface belonging to the front face 58.2 of the transverse wall 58; while the second face 62.2 of the lining 62, constituting the front face thereof, is in contact with the rear face 64.2 of the washer 65 dissipation efforts.
  • These pads 61, 62 are rotatably connected with the hub 68 by cooperation of shapes.
  • the gaskets 61, 62 have, respectively, each a central opening 61.3, 62.3 having a shape complementary to that of the third section 68.3.
  • This opening 61.3, 62.3 has a substantially square shape, the sides of the square being intended to bear against the flats 79.1 of the hub. These sides are interconnected by circular edges.
  • the friction linings 61, 62 are of the organic type, for example obtained from a binder comprising thermosetting resins, fillers, such as graphite-silica-talc-metal powders, and fibers, such as than aramid fibers, for example Kevlar®, or sintered type composed of metal powder, such as bronze, copper and iron agglomerated at high temperature and pressure or metal, such as a copper alloy (for example bronze or brass) or the like.
  • the faces of the fittings 61, 62 are in the embodiments of the smooth figures, alternatively grooved.
  • the plate 60 and the wall 58, configured to form friction tracks for the gaskets 61, 62, are for example made of steel, stainless steel, bronze or cast iron depending on the nature of the gaskets 61, 62.
  • the disc 65 of dissipation of the forces here is metallic and allows to apply homogeneously and over a large diameter the axial force generated by the spring washer 64.
  • the disc 65 has a front face 65.1 turned towards the washer 64 and a rear face 65.2 facing the front face 62.2 of the liner 62.
  • the disc 65 is also rotatably connected to the hub 68 by shape cooperation and has a central opening 65.3 having a shape complementary to that of the third section 68.3. Like the openings 61.3, 62.3 of the gaskets, this opening 65.3 has a substantially square shape. The sides of the square intended to come into contact with the flats 79.1 are interconnected by circular edges.
  • the elastic washer 64 with axial action is here metallic and has a front face 64.1 turned towards the washer 67 for closing at its inner periphery on this washer 67 and a rear face 64.2 turned towards the disc 65 of dissipation for support at its periphery external on the front 64.1 of this disc.
  • the spring washer 64 is for example a Belleville type washer, which, as a variant, has a bead or a shelf at its outer periphery for resting on the front face 64.1 of this disc 65.
  • the length L visible at the figure 5 , is a function of the length L ', the wear of the lining 61, 62 and the characteristic curve of the Belleville washer, which as we know has a generally sinusoidal shape.
  • This washer 64 is made to work close to the top of its characteristic curve so that the load developed by this washer is generally constant despite the wear of washers 61, 62.
  • this spring washer is a diaphragm, that is to say a Belleville washer extended at its inner periphery by legs.
  • this elastic washer is a corrugated washer. All these spring washers mounted on the hub 68 are of low axial size and are configured to exert a load, that is to say a pressure on the disk 65, which can vary depending on the wear of the linings 61, 62 Alternatively, overlapping or counter-rotating washers can be used to achieve the desired load in a small radial space.
  • the type of the spring washer 64 and the number (more than one washer can be used) thus makes it possible to obtain the desired pressure and consequently the limit torque of the torque limiter.
  • This type of washer acts via its outer periphery in the vicinity of the outer periphery of the disc 65, of upper outer diameter, here adjacent, the outer diameter of the lining 61, 62. A better distribution of the loads on the washers 61, 62 is obtained. in the structure of the document FR 2,631,094 .
  • the washer or washers 64 are replaced by a frustoconical coil spring whose smallest diameter bears against the closure washer 67.
  • a cylindrical coil spring of large diameter to be able to exert an action on a large diameter of the disc 65.
  • the solutions with coil spring are more bulky axially.
  • the elastic means with axial action therefore comprise at least one elastic washer with axial action or a coil spring.
  • the closing washer 67 is here metallic and cooperates with the groove 74 formed around the first section 68.1.
  • the washer 67 has a rear face 67.1 facing the spring washer 64 and a front face 67.2 facing the front axial end 69 of the hub 68 and to the shoulder 71 for contact therewith.
  • the washer 67 of closure takes the form of a washer provided with ribs 67.5 directed towards the shoulder 71 and holes 67.6.
  • the central opening 67.3 of the washer 67 comprises four flats 67.9 connected in pairs by circular edges 67.8.
  • the shoulder 71 has a shape complementary to that of the opening 67.3 of the washer 67 and has four flats 71. 7 connected in pairs by circular parts 71.8.
  • the shoulder 71 is in the shape of the third section 68.3, transversely larger, so that the flats 71.7 are in the extension of the flats 79.1 and the circular parts 71.8 in the extension of the circular parts 80.1.
  • each circular portion 71.8 is notched centrally at 71.9 for housing the inner periphery of a rib 67.5. This notch 71.9 also affects the trailing edge of groove 74 as visible in FIG. figure 6 .
  • bayonet type mounting means intervene between the closure washer 67 and the shoulder 71 for bayonet type mounting of the washer 67 in its groove 74 and with locking rotation of the washer 67 as described below.
  • the washer 67 may take the form of a snap ring of the circlip® type that can be installed inside the groove 74 by elastic deformation.
  • the shoulder 71 is continuous.
  • the shoulder 71 has only two flats 71.7 separated by two circular parts 71.8 and the washer 67 has two flats 67.9 and two circular edges 67.8.
  • the spring washer 64 is supported indirectly on the shoulder 71 via the washer 67 and on the disc 65 to axially compress the elements 58, 60, 61, 62 between the disk 65 forming a pressure disk and the bearing surfaces 77.1 of the shoulder 72 forming a reaction shoulder.
  • the elements 58, 60, 61, 62, 65 behave as if they formed one and the same piece immobile in rotation with respect to the support 16 via the plate 60.
  • the transverse wall 58 of the crown 46 is axially inserted through the axial front end 69 of the hub 68 to the third section 68.3, so that the flanges 58.5 it has at its inner periphery come into contact with the bearing surfaces 77.1 of the hub 68.
  • the first friction lining 61 is threaded onto the third section 68.3, so that its rear back face 61.2 is in contact with the front external face 58.2 of the wall 58.
  • the second friction lining 62 is introduced on the third section 68.3, so that its rear back face 62.1 comes into contact with the other front face 60.1 of the plate.
  • the disc 65 is then positioned on the third section 68.3 by its opening 65.3 for the dissipation of forces against the dorsal face 62.2 of the liner 62.
  • the elastic washer 64 is threaded onto the second section 68.2, and then the closing washer 67 is mounted. performing the bayonet mounting of the washer 67 on the shoulder 71. More precisely the flats 67.5 of the washer 67 are brought opposite the flats 71.7 of the shoulder 71.
  • each rib 67.5 is housed in a notch 71.9 to lock the washer 67 in rotation with respect to the hub 68 and secondly, that the base plate 60 is held in pressure between the friction linings 61, 62.
  • the bearing 85 is then positioned inside the opening 81 of the hub 68 and the starter shaft 43 equipped with the planet carrier 47 and a spacer washer 93 is introduced through the rear end 70 the arrow 91 referenced on the Figure 2 , so that the rear end 43.2 of the shaft 43 comes into contact with the inner annular shoulder 83 of the hub 68.
  • the spacer washer 93 is interposed axially between the planet carrier 47 and the rear face of the wall 58.
  • This washer 93 is thicker than the inner flange 46.3 of the ring 46 and is housed inside the flange 46.3.
  • the lug 60.34 is then positioned in a cavity 88 axially oriented support 16 for locking in rotation of the plate 60. This mounting is possible because a radial clearance exists between the plate and the hub 68 in the aforementioned manner.
  • the launcher 30 is mounted on the shaft 43 from front to back, then the abutment 43 is mounted and finally the shaft 43 thus equipped is threaded into the bearing 42.
  • the front end of the shaft 24 in the blind hole and in the plain bearing of the rear end 43.2 of the shaft 43 with the interposition of a ball.
  • the washer 67 and the washer are eliminated, the spring washer 64 bears directly on the first shoulder 71 of the hub 68 formed by a material reversal of the hub 68 at the front end 69.
  • the second section 68.2 of the hub is extended to the front end 69 of the hub and the free end of this second section 68.2 is deformed radially outwardly by crimping to form the first shoulder 71 against which bears directly the inner periphery of the washer 64.
  • the free end of the second section, constituting the front end 69 is continuous. Alternatively this free end is split into tabs to facilitate the crimping operation.
  • the hub 68 is cut at a flat portion 79.1 which ends at the rear face 70 of the hub 68 so that the shoulder 72 of the Figures 2 to 8 is preserved.
  • this shoulder 72 is continuous, and the wall 58 is of constant thickness and is supported by its rear face on the front face of the shoulder 72.
  • the shoulder 72 is attached by welding or riveting on the rear end 70 of the hub 68.
  • we see in 93 the spacer washer interposed between the planet carrier 47 and the rear face of the wall 58.
  • This washer 93 is housed inside the central opening of the flange 46.3.
  • the shoulder 71 is attached by welding, riveting or screwing on the front end 69. All combinations are possible.
  • the shoulders 71, 72 are in all cases carried by the hub 68.
  • At least one of the two friction linings 61, 62 is eliminated.
  • the trim 61 is removed; the base plate 60 then being in direct contact with the studs 46.2 of the crown 46.
  • the lining 62, the plate 60 rubbing against the disc 65 is also removed.
  • disc 65 is eliminated; the washer 64 rubbing directly on the plate 60.
  • the latter 58, 61, 62, 65 comprise splines at their inner periphery entering into cooperation with complementary splines formed at the outer periphery of the third section 68.3 of the hub 68.
  • the flats are therefore alternatively replaced by splines.
  • the gaskets 61, 62 are glued on either side of the base plate 60 via their face 61.1, 62.1.
  • front and rear are understood in relation to the direction of transfer of the torque from the machine to the drive pinion, the "front” side being therefore on the side of the driving pinion 50 while the side “Back” is the side of the electric motor of the electric machine.
  • the set 57 for gearboxes according to the invention is also suitable for use with a speed reducer without a planet carrier and comprising only a ring 46 and an off-axis wheel meshing directly with the internal toothing of the crown. 46, as described in the document FR-2 631 094 .
  • the starter 10 according to the invention is particularly well suited for vehicles of the "start and stop" type comprising a heat engine which is stopped for example at a red light or in traffic jams, and restarted using the starter according to the invention. .
  • the heat engine is fixed and serves to drive for example a PTO.
  • the number of flats 79.1 depends on the torque to be transmitted and the solution according to the invention does not modify the starter in a deep manner. It is apparent from the description and figures that the modification of the shaft 43 is simple and economical. It consists of a change in diameter between the cylindrical section 43.3 and the cylindrical rear end 43.2. In addition, the locking in rotation of the plate 60 is made in a simple manner using at least one cavity 88 of axial orientation. The number of cavities 88 and pins 60.34 depends on the applications.
  • the ring gear 46 is simplified because it is not configured to cooperate with the outer periphery of the bearing and is not configured to serve as a support for an elastic washer with axial action.
  • the forces are cashed by the hub 68 and the wall 58 so that the ring 46 is formed.
  • the wall 58 is integral with the ring 46.
  • the invention is applicable in the aforementioned manner to solutions in which the lever 41 is mounted to articulate distinctly from the ring gear 46.
  • the electric motor 11 of the starter is unchanged. so that alternatively the collector is flat.
  • the pinion 50 of the launcher 30 is in variant, aforesaid mounted on the outside of the housing. This pinion meshes with an embodiment with a toothed wheel intended to engage with the drive ring.
  • the structures can be reversed so that, in a variant, the locking in rotation of the plate 60 is achieved by means of at least one axial projection of the support 16, such as a rib of semicircular section, engaged in an opening complementary embodiment performed at the outer periphery of the plate 60.
  • the support 16 carries at least one pin slidably engaged in a complementary opening of the plate 90.

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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)
  • Retarders (AREA)
  • Braking Arrangements (AREA)

Claims (15)

  1. Einheit (57) für ein Untersetzungsgetriebe einer drehenden elektrischen Maschine (11), wobei die Einheit umfasst:
    - einen Zahnkranz (46), der mit einer Querwand (58) fest verbunden ist,
    - eine Grundplatte (60), die dazu bestimmt ist, drehfest in Bezug auf ein Auflager (16) der Maschine montiert zu werden,
    - elastische Mittel mit axialer Wirkung, wie z. B. eine Federscheibe (64) mit axialer Wirkung, dadurch gekennzeichnet, dass die Einheit ferner umfasst:
    - eine angesetzte Nabe (68), an der die Querwand (58) des Kranzes (46), die Grundplatte (60) und die elastischen Mittel (64) montiert sind,
    - wobei diese Nabe (68) wenigstens eine erste Schulter (71) zur Anlagerung der elastischen Mittel (64) mit axialer Wirkung, und
    - wenigstens eine zweite Schulter (72) zur Anlagerung der Querwand (58) des Kranzes (46) trägt,
    und dass die elastischen Mittel mit axialer Wirkung (64) unter Zwischenstellung einer Abschlussscheibe (67), die an der ersten Schulter (71) anliegt und in einer Nut (74) positioniert ist, die um die Nabe (68) gebildet ist, auf indirekte Weise an der ersten Schulter (71) anliegen.
  2. Einheit nach Anspruch 1, dadurch gekennzeichnet, dass sie Montagemittel vom Bajonett-Typ umfasst, die imstande sind, ein Zusammenwirken zwischen der ersten Schulter (71) und der Abschlussscheibe (67) sicherzustellen.
  3. Einheit nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Kranz (46) aus einem Kunststoff hergestellt ist und dass dieser Kranz (46) am äußeren Umfang der Querwand (58) überformt ist.
  4. Einheit nach Anspruch 3, dadurch gekennzeichnet, dass die Querwand (58) Durchgangsöffnungen (58.1) umfasst, wobei der Kranz (46) Klötze (46.2) umfasst, die durch diese Öffnungen (58.1) hindurchgehen, wobei diese Klötze (46.2) an einer Außenfläche (58.2) der Querwand (58) münden, die einer Innenfläche (58.4) gegenüberliegt, von der aus sich die Zähne des Kranzes (46) erstrecken.
  5. Einheit nach Anspruch 4, dadurch gekennzeichnet, dass die Grundplatte (60) direkt an den Klötzen (46.2) des Kranzes (46) anliegt.
  6. Einheit nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass sie einen Reibbelag (61) umfasst, der zwischen der Querwand (58) des Kranzes und der Grundplatte (60) angeordnet ist.
  7. Einheit nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass sie ferner einen Reibbelag (62) umfasst, der zwischen der Grundplatte (60) und der Federscheibe (64) mit axialer Wirkung positioniert ist.
  8. Einheit nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass der oder die Reibbeläge (61, 62) in Drehung mit der Nabe (68) verbunden sind.
  9. Einheit nach Anspruch 8, dadurch gekennzeichnet, dass die Nabe (68) wenigstens eine Abflachung (79.1) aufweist und dass der oder die Reibbeläge (61, 62) eine Öffnung (61.3, 62.3) mit wenigstens einer Abflachung (79.1) mit komplementärer Form zur Drehverbindung mit der Nabe (68) durch Zusammenwirken der Formen aufweisen.
  10. Einheit nach Anspruch 9, dadurch gekennzeichnet, dass die Nabe (68) einen Abschnitt (68.3) beinhaltet, der vier Abflachungen (79.1) aufweist, von denen jeweils zwei zueinander parallel sind und unter Zwischenstellung von zylindrischen Teilen (80.1) miteinander verbunden sind, wobei der oder die Reibbeläge (61, 62) eine Öffnung (61.3, 62.3) mit komplementärer Form aufweisen.
  11. Einheit nach einem der Ansprüche 6 bis 10, dadurch gekennzeichnet, dass der oder die Beläge (61, 62) an die Seitenflächen der Grundplatte (60) geklebt sind.
  12. Einheit nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass die zweite Schulter (72) in mehrere Teile (77) unterteilt ist, die zu der Nabe (68) gehören und jeweils eine Auflagerfläche (77.1) aufweisen.
  13. Einheit nach Anspruch 12, dadurch gekennzeichnet, dass die Auflagerflächen (77.1) der Teile (77) winkelmäßig in Bezug auf die Abflachungen (79.1) versetzt sind.
  14. Anlasser (10) für ein Kraftfahrzeug, dadurch gekennzeichnet, dass er umfasst:
    - eine elektrische Maschine (11), die eine Ausgangswelle (24) umfasst,
    - einen Umlaufgetriebezug, umfassend ein Zentralrad (49), das in Drehung mit der Ausgangswelle (24) der elektrischen Maschine (11) verbunden ist,
    - eine Einheit (57) nach einem der Ansprüche 1 bis 13 und
    - einen Planetenträger (47), der einerseits mit dem Zentralrad (49) und andererseits mit dem Kranz (46) der Einheit nach einem der Ansprüche 1 bis 13 in Eingriff gelangt, wobei dieser Planetenträger (47) in Drehung mit einer Ausgangswelle (43) des Anlassers verbunden ist, die ein Antriebsritzel (50) trägt, das dazu bestimmt ist, in Eingriff mit den Zähnen des Antriebskranzes eines Verbrennungsmotors des Fahrzeugs zu gelangen.
  15. Anlasser nach Anspruch 14, dadurch gekennzeichnet, dass die Nabe (68) in ihrer Mitte eine Durchgangsöffnung (68.4) aufweist, die den Durchgang der Ausgangswelle (43) des Anlassers ermöglicht, dass das Ritzel (50) zu einer Starteinrichtung (30) gehört, die einen Mitnehmer (51) umfasst, dass die Durchgangsöffnung (68.4) zwei zylindrische Teile (81, 82) umfasst, die durch einen inneren ringförmigen Teil (83) mit kleinerem Innendurchmesser als die zwei anderen zylindrischen Teile (81, 82) getrennt sind, und dass der innere ringförmige Teil (83) einen Anschlag bildet, der dazu bestimmt ist, mit der Rückfläche des Mitnehmers (51) zusammenzuwirken.
EP11817389.7A 2010-12-20 2011-12-19 Elektromotor und brennkraftmaschine starter getriebe Not-in-force EP2655863B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1060785A FR2969219B1 (fr) 2010-12-20 2010-12-20 Ensemble pour reducteur de vitesse d'une machine electrique tournante et demarreur pour moteur thermique associe
PCT/FR2011/053048 WO2012085424A1 (fr) 2010-12-20 2011-12-19 Ensemble pour reducteur de vitesse d'une machine electrique tournante et demarreur pour moteur thermique associe

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EP2655863A1 EP2655863A1 (de) 2013-10-30
EP2655863B1 true EP2655863B1 (de) 2018-05-09

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US (1) US9309856B2 (de)
EP (1) EP2655863B1 (de)
KR (1) KR20140017504A (de)
CN (1) CN103270290B (de)
BR (1) BR112013008506A2 (de)
FR (1) FR2969219B1 (de)
WO (1) WO2012085424A1 (de)

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FR3019858B1 (fr) * 2014-04-11 2016-03-25 Valeo Equip Electr Moteur Ensemble de demarreur pour moteur thermique
JP6113252B1 (ja) * 2015-11-13 2017-04-12 三菱電機株式会社 エンジン始動装置、及びその製造方法
FR3049985B1 (fr) * 2016-04-08 2019-10-04 Valeo Equipements Electriques Moteur Demarreur pour moteur thermique de vehicule automobile muni d'une plaque de base comportant une surepaisseur
FR3049984B1 (fr) * 2016-04-08 2018-03-23 Valeo Equipements Electriques Moteur Demarreur pour moteur thermique de vehicule automobile muni d'une plaque de base a configuration optimisee
CN109884764A (zh) * 2017-12-06 2019-06-14 深圳光峰科技股份有限公司 镜头模组及投影设备
CN111108306A (zh) * 2018-04-04 2020-05-05 阪东化学株式会社 齿形带

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JP2002180938A (ja) * 2000-12-08 2002-06-26 Denso Corp スタータ
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Publication number Publication date
FR2969219A1 (fr) 2012-06-22
KR20140017504A (ko) 2014-02-11
CN103270290A (zh) 2013-08-28
EP2655863A1 (de) 2013-10-30
BR112013008506A2 (pt) 2016-07-05
CN103270290B (zh) 2016-08-10
WO2012085424A1 (fr) 2012-06-28
FR2969219B1 (fr) 2013-01-11
US9309856B2 (en) 2016-04-12
US20140007834A1 (en) 2014-01-09

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