EP1119707B1 - Kraftfahrzeug-anlasser mit reibungsantrieb - Google Patents

Kraftfahrzeug-anlasser mit reibungsantrieb Download PDF

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Publication number
EP1119707B1
EP1119707B1 EP00958652A EP00958652A EP1119707B1 EP 1119707 B1 EP1119707 B1 EP 1119707B1 EP 00958652 A EP00958652 A EP 00958652A EP 00958652 A EP00958652 A EP 00958652A EP 1119707 B1 EP1119707 B1 EP 1119707B1
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EP
European Patent Office
Prior art keywords
starter
frusto
roller
conical
output shaft
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.)
Expired - Lifetime
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EP00958652A
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English (en)
French (fr)
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EP1119707A1 (de
Inventor
Gérard Vilou
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Valeo Equipements Electriques Moteur SAS
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Valeo Equipements Electriques Moteur SAS
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Publication of EP1119707A1 publication Critical patent/EP1119707A1/de
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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
    • F02N15/08—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing being of friction type

Definitions

  • the invention relates to a motor vehicle starter.
  • the invention relates more particularly to a starter for motor vehicle designed to rotate a wheel of starting a heat engine, of the type comprising an output shaft which is rotated by the armature shaft of an electric motor, type in which the output shaft is fitted with a drive device of the starter wheel.
  • the starter 10 has an output shaft 12 which is driven in rotation by the armature shaft 14 of an electric motor 16 by via a planetary gearbox 18.
  • the output shaft 12 and the armature shaft 14 are coaxial with axis X1.
  • the free rear 20 and front 22 ends of the output shaft 12 are guided in rotation, respectively by a rear bearing 24 and a front bearing 26, with interposition of a sleeve respectively rear guide 25 and a front guide sleeve 27.
  • a launcher 28 includes a rear freewheel 30 which drives a front pinion 32.
  • the starter 28 is mounted to slide axially on a fluted intermediate section 34 of the output shaft 12 so as to be secured to the latter in rotation.
  • the planetary gearbox 18 includes a set of satellites 36 whose axes of rotation 38 are carried by a flange 40 transverse orientation which is integral in translation and in rotation with the output shaft 12 and which is fixed on the latter by crimping.
  • the satellites 36 are immobilized axially in translation by a plate 42 force fitted onto the axes 38 of the satellites 36.
  • the reduction gear 18 also includes an internal gear crown 44 which is fixed by overmolding on a transverse plate 46 fixed on the housing 48 of the starter 10.
  • the satellites 36 mesh with grooves 50 carried by a front section 52 of the armature shaft 14.
  • the free front end 54 of the armature shaft 14 is guided in rotation in a blind axial bore 56 which is produced in the face rear of the rear free end 20 of the output shaft 12 with interposition of a guide sleeve 58.
  • the free front end 54 of the armature shaft 12 is wedged in forward translation by an element of wedging 60 which is housed in the bottom of the blind axial bore 56.
  • the starter 10 also includes a contactor 62 including a core moving magnetic 64 controls the axial movement of the launcher 28 by through a lever 66.
  • the operation of the starter 10 is as follows.
  • the contactor 62 is supplied with electric current to cause both the axial displacement of the launcher 28 forwards to engage the pinion 32 with the starter wheel 68, and starting the engine electric 16.
  • the electric motor 16 rotates the armature shaft 14. This transmits this rotational movement to the output shaft 12 by through the meshing of the grooves 50 in its section intermediate 52 with the satellites 36 of the reduction gear 18.
  • the rotation of the output shaft 12 and the freewheel 30 causes the rotation of the pinion 32 of the starter 28 which drives the starter wheel 68 so as to start the engine.
  • the freewheel 30 avoids transmitting the overspeed of the pinion 32 to the output shaft 12.
  • the freewheel 30 thus protects the electric motor 16 and the reducer 18 against a too high rotational speed which can lead to degradations of the rotating members of the starter 10.
  • the supply of the contactor 62 is stopped. which causes the axial launcher 28 to withdraw from the starter wheel 68, and the return of the launcher 28 to a rear position of rest.
  • the presence of the freewheel 30 increases the length and the weight of the starter 10, as well as its cost.
  • this contactor 62 constitutes a protuberance above the electric motor 16 which is often a source difficulties in installing the starter 10 on the heat engine in because of the space.
  • Contactor 62 also represents a significant part of the weight starter 10.
  • the starter 10 here comprises a sleeve 114 which is mounted sliding axially around the output shaft 12 and which is secured in rotation with the latter by an axial groove 116.
  • the sleeve 114 carries at the front a frustoconical crown 70 drive which is integral with it in rotation and in axial displacement.
  • the tapered crown 70 has a friction surface frustoconical 74 complementary to a frustoconical bearing before 110 of the starter wheel 68.
  • a rear tapered roller 82 for driving is mounted screwed on a helical thread 118 of the sleeve 114, so that it moves axially forward in the direction of screwing.
  • the tapered roller 82 has a friction surface frustoconical 86 complementary to a rear frustoconical bearing 112 of the starter wheel 68.
  • the output shaft 12 has at its free end before a front axial stop, here a nut 120, which retains the sleeve axially 114 on the shaft 12 in its rest position.
  • a helical compression spring 122 is interposed between the box 48 of the starter 10 and the rear transverse face 124 of the sleeve 114 in order to return it to its rest position against the axial stop before 120.
  • the displacement of the frusto-conical roller 82 is not reliable because its movement is very strongly linked to its qualities of friction on the thread 118 of the sleeve 114.
  • the good functioning that can be observed on a starter new may disappear due to corrosion of parts, following deposits of dust, following the aging of the lubricant which tends to harden, or following to the modification of the geometry of the thread 118 caused by wear.
  • the known system may suffer from malfunctions cold because lubricants are more viscous when they are cold, which produces an additional resistance to screwing.
  • the acceleration characteristics of the electric motor which are essential to create the inertial torque effect, are lessened cold due to energy losses in the bearing lubricants. in also because of the poorer battery performance.
  • starter 10 capable of providing greater drive torque than a conventional starter 10.
  • the starter 10 should then be more large in diameter, heavier and more expensive.
  • the invention aims to remedy these drawbacks by proposing a starter of the friction drive type, in which the control of the movement of the frusto-conical roller is not inertial and in which the displacement of the frusto-conical roller is not dependent on the angular acceleration characteristics of the starter.
  • the invention provides a vehicle starter automobile designed to drive a starter wheel in rotation heat engine, of the type having an output shaft which is driven in rotation by the armature shaft of an electric motor.
  • the output shaft is provided with a wheel drive device friction start
  • the type comprising at least one frustoconical roller before training which is planned to cooperate with a litter tapered front complementary to the starter wheel in order to drive it in rotation
  • the tapered roller is mounted screwed on a thread carried by the output shaft to be moved axially backwards towards the starter wheel, when the output shaft turns relative to the frustoconical roller in a first direction of rotation, characterized in that it includes a device for braking which, when starting the electric motor, brakes the roller frustoconical in rotation, in order to cause axial displacement, towards the rear, of the frusto-conical roller, from its rest position to its active position, in which the tapered roller is in contact with friction with the starter wheel.
  • rollers can be used small dimensions, which allows to keep reduction between the starter wheel and the rollers which are substantially identical to those used in conventional starters.
  • the architecture used in the starter according to the invention completely protects the threaded parts, which prevents them from being exposed to dust splashes and corrosion.
  • the starter according to the invention has a simpler structure than that of known starters. It has fewer parts and one of the tapered rollers is integrated into the output shaft.
  • the starter 10 is shown in Figure 2 in a rest position P r .
  • the starter 10 has an output shaft 12 which differs at several points on the output shaft 12 of a starter 10 depending on the state of technique.
  • the output shaft 12 has an intermediate section machined from so as to form a frustoconical drive crown 70.
  • the tapered crown 70 has a surface at the front frustoconical 74 inclined towards the axis X1 and towards the front.
  • the crown frustoconical 70 delimits with the output shaft 12 a surface shoulder 72 oriented towards the rear.
  • the output shaft 12 comprises an intermediate cylindrical section 76 which delimits, with a threaded front section 78, a shoulder surface 80 oriented towards forward.
  • a frustoconical drive roller 82 is mounted screwed on the threaded front section 78 of the output shaft 12.
  • the tapered roller 82 has a front section 84, the outer surface 85 is cylindrical, and a rear section 87 of which the outer surface 86 is frustoconical and inclined towards the axis X1 and towards the rear.
  • the tapered roller 82 also has an internal bore 88 as well as a tapped front neck 90 complementary to the threads of the section threaded front 78 of the output shaft 12.
  • the internal bore 88 delimits with the threaded neck 90 a shoulder surface 92 oriented towards the rear.
  • a return compression helical spring 94 is mounted on the threaded front section 78 of the output shaft 12 and in the internal bore 88 of the frustoconical roller 82.
  • the return spring 94 is in axial support front on the shoulder surface 92 of the frusto-conical roller 82 and in support rear axle on the shoulder surface 80 of the output shaft 12.
  • the frusto-conical roller 82 is in front axial abutment against a front stop plate 96 which is fixed on the rear transverse face of the front bearing 26 of the output shaft 12.
  • the rear section 87 of the frustoconical roller 82 is in radial support guide, by the internal bore 88, on the cylindrical section intermediate 76 of the output shaft 12, so that the relative screwing of the tapered roller 82 relative to the output shaft 12 causes the axial sliding of the rear section 87 on the cylindrical section intermediate 76 back and forth.
  • the wedging element 60 which is housed in the bottom of the axial bore blind 56 of the rear free end 20 of the output shaft 12 is a ball.
  • the output shaft 12 is in rear axial abutment against the ball 60, which is itself in axial abutment against the front free end 54 of the armature shaft 14, so that the shoulder surface 72 of the tapered crown 70 is not in contact with the transverse face front of rear guide sleeve 25.
  • the output shaft 12 is slidably mounted axially in the rear guide rings 25 and front 27.
  • the lower part of the housing 48 of the starter 10 includes a cylindrical chimney 98 oriented radially with respect to the axis X1.
  • the upper opening of the chimney 98 opens radially to the right of the front section 84 of the tapered roller 82.
  • the opening bottom of the chimney 98 is closed by a washer 100 maintained by crimping.
  • a hollow cylindrical shoe 102 is slidably mounted in the chimney 98.
  • the inner radial end of the shoe 102 is closed by a disc 104 so as to have a friction surface 106 facing up.
  • the friction surface 106 is in radial abutment against the surface cylindrical 85 of the frustoconical roller 82 under the axial pressure of a shoe spring 108, and it has a profile in the trunk of a cylinder concave complementary to the cylindrical surface 85.
  • the pad spring 108 is mounted inside the pad 102, in lower axial support on the washer 100 and upper axial support on the underside of disc 104.
  • the starter wheel 68 has a frustoconical bearing front 110 complementary to the frustoconical surface 86 of the frustoconical roller 82 and a rear frustoconical bearing 112 complementary to the surface tapered 74 of the tapered crown 70.
  • the armature shaft 14 transmits the rotational movement to the output shaft 12 by through the reducer 18.
  • the frusto-conical roller 82 is braked in rotation relative to the shaft output 12 under the effect of the braking produced by the friction of the shoe 102 on the cylindrical surface 85 of the frusto-conical roller 82. Consequently, the relative rotation of the threaded section 78 of the output shaft 12 relative to the tapped neck 90 of the frustoconical roller 82 causes the screwing of this last on the output shaft 12 and its axial displacement towards the rear.
  • the tapered roller 82 therefore moves axially rearward by compressing the return spring 94, until its surface frustoconical 86 comes into axial abutment against the frustoconical bearing front 110 of the starter wheel 68.
  • the output shaft 12 therefore moves axially forward by sliding in its rear guide sockets 25 and front 27.
  • the output shaft 12 moves with all of the satellites 36 of the reducer 18. Also, the satellites 36 slide axially towards the front on the splines 50 of the armature shaft 14 and on the teeth of the internal gear 44.
  • the output shaft 12 moves axially forwards in compressing the return spring 94, until the crown frustoconical 70 comes into axial abutment against the frustoconical bearing rear 112 of the starter wheel 68.
  • the starter wheel 68 is is then clamped axially between the frustoconical crown 70 and the tapered roller 82.
  • the axial pressure exerted on the frustoconical bearing surfaces before 110 and rear 112, on one side by the tapered crown 70 and on the other by the tapered roller 82, is maintained by the tendency to screw in the output shaft 12 in the threaded neck 90 of the frustoconical roller 82.
  • the tapered crown 70 continues to rotate with the shaft of outlet 12, and the friction of the frustoconical surface 74 on the bearing tapered rear 112 produce a rotation of the starter wheel 68 in the opposite direction to the rotation of the frustoconical crown 70.
  • the tapered crown 70 then drives the starter wheel 68 in rotation about the axis X2, in the opposite direction to the screwing direction of the output shaft 12.
  • the shoe 102 does not have enough force to prevent the roller frustoconical 82 to rotate, its friction surface 106 then slides on the cylindrical surface 85 of the frustoconical roller 82.
  • a high driving torque C e produced by the rapid rotation of the starting wheel 68, is exerted on the frustoconical roller 82 and the frustoconical crown 70.
  • the tapered roller 82 unscrews and moves axially forward.
  • the frusto-conical roller 82 is nevertheless braked in its unscrewing by the shoe 102. This allows the frusto-conical crown 70 to retain a front axial pressing force F x against the rear frusto-conical surface 112 of the starting wheel 68.
  • the axial pressing force F x of the frustoconical crown 70 against the starting wheel 68 then becomes too weak to cause the electric motor 16 to overspeed. There is a sliding of the frustoconical crown 70 on the rear frustoconical bearing 112 of the starting wheel 68.
  • the axial dimensioning of the reducer 18 and of the rear bearings 24 and front bearings 26 is designed to accept displacement in axial translation of the output shaft 12 by at least ten percent greater than the stroke necessary for the tapered crown 70 comes into contact with the tapered rear seat 112 of the starting 68. This allows correct operation of the starter 10 despite the positioning dispersions of the starter 10 and the wheel 68, and despite the wear of the surfaces of the frustoconical bearing rear 112 and the frustoconical surface 74.
  • the starting wheel 68 is clamped between the frustoconical crown 70 and the frustoconical roller 82 by a rear linear contact zone AB and a front linear contact zone CD respectively.
  • These two substantially linear contact zones are included in a plane P X1-X2 containing the axis of rotation X1 of the output shaft 12 and the axis of rotation X2 of the starting wheel 68.
  • FIG. 6 schematically represents a section of the starting wheel 68 and of the frustoconical crown 70 along the plane P X1-X2 .
  • This figure shows the forces used in the contact between the rear tapered seat 112 of the wheel starting 68 and the frustoconical surface 74 of the frustoconical crown 70.
  • the axial support force F x is parallel to the axis X1 and oriented towards the front.
  • the axial pressing force F x produces against the starting wheel 68 a normal pressing force F n perpendicular to the segment AB in the plane P X1-X2 .
  • the normal bearing force F n is the component normal to the segment AB of the axial bearing force F x .
  • the axial pressing force F x also produces a radial pressing force F y against the starting wheel 68.
  • the radial pressing force F y is parallel to the radius of the starting wheel 68 in the plane P X1-X2 and oriented towards the center of said wheel 68.
  • the starter wheel 68 driven by the crown tapered 70 also depends on the couple C, resistance to training of the engine.
  • the torque C r produces a tangential force F t perpendicular to the plane P X1-X2 and oriented here upwards, in the opposite direction to the rotation of the starting wheel 68.
  • a torque is equal to the value of the force multiplied by the length of the lever arm.
  • the result of the normal bearing force F n added to the tangential force F t is the contact force F c which is contained in a plane perpendicular to the plane P X1-X2 and to the segment AB passing through the point M.
  • the contact force F c describes a drive angle ⁇ with the normal support force F n .
  • the final formula (4) allows us to know the parameters that we can modify to obtain in all cases a training by starter wheel friction 68.
  • a small angle ⁇ is chosen. In this case, however, care must be taken that the radial support force F y is not too great to remain compatible with the mechanical strength of the output shaft 12 and its rear bearings 24 and front 26.
  • the axial bearing force F x results from the transformation of the torque of the electric motor 16 by the screw-nut system constituted by the threaded section 78 of the output shaft 12 and the threaded neck 90 of the frustoconical roller 82. According to the laws classics that govern this transformation, F x will depend on the pitch and the slip coefficient of the threads.
  • the axial bearing force F x must not however be too high in order not to exceed the admissible limits of contact pressure between the frustoconical roller 82 and the starting wheel 68.
  • angles of the cones formed by the tapered roller 82 and the tapered crown 70 are the same.
  • angles of the cones formed by the roller tapered 82 and the tapered crown 70 may not be identical.
  • the frustoconical surfaces of the frustoconical roller 82, of the crown frustoconical 70, and starting wheel 68 of friction linings aimed in particular at facilitating the driving of the starting wheel 68.
  • the latter is pressed against the frustoconical roller 82 by a controlled electromagnet.
  • This embodiment makes it possible for example to control the stopping of the pressure of the shoe 102 against the frustoconical roller 82, when the starter 10 is in its active position P a .
  • FIG. 8 and 9 There is shown schematically in Figures 8 and 9 a alternative embodiment of the braking device in which the surface cylindrical 85 of the frustoconical roller 82 has axial grooves 126, or axial grooves, and in which the friction surface 106 of the shoe 102 has an axial rib 128 of complementary shape a groove 126 of the frustoconical roller 82.
  • the friction surface 106 of the shoe 102 can have several axial ribs 128, or axial grooves, complementary grooves 126 of the frusto-conical roller 82.
  • the axially oriented edges of the grooves 126 and of the rib 128 are inclined or rounded, so that the grooves 126 and the rib have a section, in a plane transverse to the axis X1, of substantially triangular or rounded profile.
  • Figures 8 and 9 we have shown rounded profiles.
  • the radial result of the surface reaction cylindrical 85 on the shoe 102 is greater than the radial bearing force exerted by the shoe 102 on the cylindrical surface 85, so that the tapered roller 82 pushes the shoe 102 outward, which allows to rotate around the X1 axis.
  • a high braking torque is thus obtained on starting, while the frusto-conical roller 82 moves axially rearward.
  • This braking torque is reduced when the roller 82 rotates at high speed high because, due to the inertia of the shoe 102, its axial rib 128 has more time to descend in the axial grooves 126 of the surface cylindrical 85.
  • the friction torque of the shoe 102 on the surface cylindrical 85 is then close to the friction torque of the shoe 102 on a smooth surface cylinder.
  • the grooves 126 and the rib 128 have a section curved profile, so as to avoid aggressive profiles which favor noise and wear.
  • roller tapered 82 its cylindrical surface 85 has grooves helical which rotate in opposite direction with respect to thread 78 of the output shaft 12.
  • the friction surface 106 of the shoe 102 comprises also helical grooves of complementary shape and orientation grooves of the cylindrical surface 85.
  • the helical grooves have a profile section triangular or rounded, and the step between two grooves is equal to the step thread 78.
  • the device for braking comprises a single braking shoe 102.
  • a braking device comprising several pads 102 similar acting in parallel which are preferably distributed circumferentially evenly around the surface cylindrical 85.
  • FIG. 10 shows another alternative embodiment of the braking device in which the shoe 102 is of annular shape coaxial with the frusto-conical roller 82, and in which the frusto-conical roller 82 has a generally frusto-conical surface 130 forward.
  • the front frusto-conical surface 130 is inclined towards the axis X1 and forward.
  • the annular shoe 102 has a bearing surface tapered rear 132, or friction surface, which is shaped complementary to the frustoconical bearing front 130 of the roller 82.
  • the annular shoe 102 is biased axially towards the rear against the frustoconical bearing surface before 130 of the roller 82, by a coaxial helical compression spring 134 which is interposed between the rear transverse surface 29 of the front bearing 26 of the starter 10 and the front transverse surface 136 of the annular shoe 102.
  • the spring 134 has a front axial return 138 which is embedded in the rear transverse face 29 of the front bearing 26 and a rear axial return 140 which is embedded in the front transverse face 136 of the annular shoe 102, in order to stop the shoe 102 in rotation by compared to the housing 48 of the starter 10.
  • the annular shoe 102 produces a force of friction on the tapered roller 82, oriented axially here, which causes the axial, rearward movement of the tapered roller 82 during starting the electric motor 16.
  • the frustoconical profile of the front bearing surface 130 of the roller 82 and the friction surface 132 of the annular shoe 102 thanks to The "wedge effect" allows obtaining a significant braking torque with weak axial force.
  • the angle of the span cone frustoconical 130, 132 complementary to the shoe 102 and the roller 82 by axis X1 must be important enough to avoid any blocking of the annular shoe 102 by wedging.
  • the annular shoe 102 is immobilized in rotation relative to the housing 48 of the starter 10 thanks to an external radial extension of the shoe 102, by example a groove, which extends inside an internal groove complementary to box 48 of starter 10.
  • FIGS. 11 and 12 show another variant of embodiment of the braking device in which the shoe 102 is a elastic band, or elastic strap, which surrounds a portion of the cylindrical surface 85 of the frusto-conical roller 82.
  • the elastic band 102 forms a portion of a ring which extends here approximately 270 degrees around the cylindrical surface 85 of the roller 82.
  • One of the circumferential ends of the elastic band 102 has a tongue 142 which extends radially outwards and which is received in a groove 144 of the housing 48 of the starter 10, in view to immobilize the shoe 102 in rotation relative to the housing 48.
  • the contact force, and therefore the braking force, of the shoe 102 on the frusto-conical roller 82 depends on the inside diameter of the ring formed by the elastic band 102 in its free state, and of the outside diameter of the cylindrical surface 85 of the roller 82, and it also depends on the axial length and radial thickness of the elastic band 102.
  • This type of shoe 102 provides a braking force significant, with a contact pressure of the shoe 102 on the roller 82 relatively low, which reduces wear and the risk of seizure of the braking device.
  • the contact pressure is the quotient of the force of braking on the contact surface.
  • the contact surface of pad 102 is much larger than for the pads 102 described above.
  • the contact surfaces of the shoe 102 and the roller frustoconical 82 may include a surface treatment or a coating of material which improves the friction characteristics.
  • the braking device can be of the electromagnetic type which, compared to the braking of the friction type described above, in particular allows reduce wear on parts.
  • the power supply device (not shown) and control (not shown) of starter 10 is adapted to its new design.
  • the electric motor 16 is powered by a relay whose control coil is actuated by the ignition key of the vehicle or by another known starting control device such as than a transponder.
  • the relay is mounted inside the electric motor 16 or outside the starter 10, in particular in the housing 48.
  • the relay is placed on the starter power cable routing 10, for example in battery power outlet.
  • the relay is electronic and allows a gradual start of the engine.
  • the relay lowers temporarily the supply voltage of the electric motor 16 for starting by “chopping” the motor supply current electric 16.
  • the invention applies to any type of starter 10, with or without reducer 18.
  • the reduction gear 18 can be of planetary gear or of another type.
  • only the frusto-conical roller 82 is axially movable.
  • the output shaft 12 and its tapered crown 70 are blocked in axial sliding, and the starter wheel 68 has axial play.
  • the rotational drive of the starter wheel 68 occurs when the rear frusto-conical surface 112 comes into contact with the surface tapered 74 of the tapered crown 70, under the pressure of the roller tapered 82.

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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)
  • Braking Arrangements (AREA)

Claims (28)

  1. Anlasser (10) für ein Kraftfahrzeug, der vorgesehen ist, um ein Anlaßrad (68) eines Verbrennungsmotors drehend anzutreiben, mit einer Ausgangswelle (12), die durch die Ankerwelle (14) eines Elektromotors (16) drehend angetrieben wird, wobei die Ausgangswelle (12) mit einer Antriebsvorrichtung (70, 82) zum Antrieb des Anlaßrads (68) durch Reibung versehen ist, mit wenigstens einer vorderen kegelstumpfartigen Antriebsrolle (82), die für das Zusammenwirken mit einer formschlüssigen vorderen kegelstumpfartigen Auflagefläche (110) des Anlaßrads (68) vorgesehen ist, um es drehend anzutreiben, wobei die kegelstumpfartige Antriebsrolle (82) an einem an der Ausgangswelle (12) eingearbeiteten Gewinde (78) verschraubt angebracht ist, um in Richtung des Anlaßrads (68) axial nach hinten verschoben zu werden, wenn sich die Ausgangswelle (12) im Verhältnis zur kegelstumpfartigen Antriebsrolle (82) in einer ersten Drehrichtung dreht,
    dadurch gekennzeichnet, daß er eine Bremsvorrichtung (102) umfaßt, die beim Anlaufen des Elektromotors (16) die kegelstumpfartige Antriebsrolle (82) in ihrer Drehbewegung abbremst, um die axiale Verschiebung der kegelstumpfartigen Antriebsrolle (82) nach hinten von ihrer Ruheposition (Pr) zu ihrer Wirkposition (Pa) herbeizuführen, in der sich die kegelstumpfartige Antriebsrolle (82) in reibschlüssigem Kontakt mit dem Anlaßrad (68) befindet.
  2. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß die Bremsvorrichtung wenigstens ein Gleitsegment (102) umfaßt, das sich durch eine Reibfläche (106) in Gleitkontakt mit einer Auflagefläche (85, 130) der kegelstumpfartigen Antriebsrolle (82) befindet, um sie in ihrer Drehbewegung abzubremsen.
  3. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß jedes Gleitsegment (102) mittels eines elastischen Elements (108), welches das Gleitsegment (102) ständig beaufschlagt, oder mittels eines angesteuerten Elektromagneten gegen die Auflagefläche (85) der kegelstumpfartigen Antriebsrolle (82) gepreßt wird.
  4. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß die Auflagefläche (85) der kegelstumpfartigen Antriebsrolle eine koaxiale konvex zylindrische Fläche der Antriebsrolle (82) ist und der Druck gegen die Auflagefläche (85) radial ausgerichtet ist.
  5. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß die zylindrische Fläche (85) axiale Rillen (126) enthält.
  6. Anlasser (10) nach Anspruch 4, dadurch gekennzeichnet, daß die zylindrische Fläche (80) Spiralrillen enthält, deren Windungssinn entgegengesetzt zum Windungssinn des Gewindes (78) der Ausgangswelle (12) verläuft, so daß die Reibung jedes Gleitsegments (102) gegen die zylindrische Fläche (85) eine Einschraubwirkung erzeugt, die zur Verschiebung der kegelstumpfartigen Antriebsrolle (82) axial nach hinten beiträgt.
  7. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß die Steigung der Spiralrillen identisch mit der Steigung des Gewindes (78) der Ausgangswelle (12) ist.
  8. Anlasser (10) nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, daß die Rillen (126) einen Querschnitt mit einem in etwa dreieckigen oder abgerundeten Profil haben.
  9. Anlasser (10) nach einem der Ansprüche 5 bis 8, dadurch gekennzeichnet, daß die Reibfläche (106) jedes Gleitsegments (102) Rillen (128) mit einer zu den Rillen (126) der zylindrischen Fläche (85) komplementären Form und Ausrichtung enthält.
  10. Anlasser (10) nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß er mehrere Gleitsegmente (102) umfaßt, die in Umfangsrichtung gleichmäßig um die zylindrische Fläche (85) herum verteilt sind.
  11. Anlasser (10) nach Anspruch 3, dadurch gekennzeichnet, daß die Auflagefläche eine ringförmige Schulterfläche (130) der Antriebsrolle (82) ist, die nach vorn ausgerichtet ist, und daß der Druck gegen die Schulterfläche (130) axial nach hinten ausgerichtet ist.
  12. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß die Schulterfläche (130) kegelstumpfartig, zur Achse (X1) und nach vorn geneigt ausgeführt ist.
  13. Anlasser (10) nach Anspruch 11 oder 12, dadurch gekennzeichnet, daß er ein einziges mit der kegelstumpfartigen Antriebsrolle (82) koaxiales ringförmiges Gleitsegment (102) umfaßt und daß er Mittel (138, 140) umfaßt, um das Gleitsegment (82) in seiner Drehung im Verhältnis zum Gehäuse (48) des Anlassers (10) zu sichern.
  14. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß die Reibfläche (132) des Gleitsegments in etwa formschlüssig mit der Schulterfläche (130) der kegelstumpfartigen Antriebsrolle (82) ausgeführt ist.
  15. Anlasser (10) nach Anspruch 13 oder 14, dadurch gekennzeichnet, daß das Gleitsegment (102) axial gegen die Schulterfläche (130) mittels einer Druckfeder (134) gepreßt wird, die koaxial zur kegelstumpfartigen Antriebsrolle (82) verläuft und die zwischen dem Gehäuse (48) des Anlassers (10) und dem Gleitsegment (102) eingefügt ist.
  16. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß die Feder (134) einen vorderen axialen Rücksprung (138), der in eine hintere Querfläche (29) eines vorderen Lagers (26) des Gehäuses (48) des Anlassers (10) eingelassen ist, und einen hinteren axialen Rücksprung (140) umfaßt, der in eine vordere Querfläche (136) des Gleitsegments (102) eingelassen ist, um das Gleitsegment (102) in seiner Drehung im Verhältnis zum Gehäuse (48) des Anlassers (10) anzuhalten.
  17. Anlasser (10) nach Anspruch 15, dadurch gekennzeichnet, daß das Gleitsegment (102) eine äußere radiale Verlängerung umfaßt, die sich im Innern einer axialen Nut des Gehäuses (48) des Anlassers (10) erstreckt, um das Gleitsegment (102) in seiner Drehung im Verhältnis zum Gehäuse (48) des Anlassers (10) zu sichern.
  18. Anlasser (10) nach Anspruch 4, dadurch gekennzeichnet, daß das Gleitsegment (102) ein elastisches Band ist, das einen Abschnitt der zylindrischen Fläche (85) der Antriebsrolle (82) umgibt und das eine Zunge (142) umfaßt, die sich in etwa radial nach außen erstreckt, wobei die Zunge (142) in einer Aufnahme oder Auskehlung (144) des Gehäuses (48) des Anlassers (10) aufgenommen ist, um das Gleitsegment (102) in seiner Drehung zu sichern.
  19. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß das elastische Band (102) einen Ringabschnitt bildet, der sich in etwa auf 270 Grad um die zylindrische Fläche (85) der Antriebsrolle (82) herum erstreckt.
  20. Anlasser (10) nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Auflagefläche (85, 130) der kegelstumpfartigen Antriebsrolle (82) und/oder die Reibfläche (106, 132) des Gleitsegments (102) eine Oberflächenbehandlung oder eine Materialbeschichtung umfaßt, welche die Reibungseigenschaften verbessert.
  21. Anlasser (10) nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß zwischen der kegelstumpfartigen Antriebsrolle (82) und der Ausgangswelle (12) ein elastisches Rückstellelement (94) eingefügt ist, um die kegelstumpfartige Antriebsrolle (82) zu ihrer Ruheposition (Pr) zurückzustellen.
  22. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß das elastische Rückstellelement (94) ein elastisches Druckelement ist, das nach hinten an einer Schulter (80) der Ausgangswelle (12) und nach vorn an einer Schulter (92) der kegelstumpfartigen Antriebsrolle (82) zur Anlage kommt.
  23. Anlasser (10) nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Antriebsvorrichtung (70, 82) ein hinteres kegelstumpfartiges Antriebskegelrad (70) umfaßt, das drehfest und axial verschiebungsfest mit der Ausgangswelle (12) verbunden ist und das für das Zusammenwirken mit einer formschlüssigen hinteren kegelstumpfartigen Auflagefläche (112) des Anlaßrads (68) vorgesehen ist, und daß die Ausgangswelle (12) axial gleitend verschiebbar im Verhältnis zur Ankerwelle (14) gelagert ist, um die axiale Verschiebung des Antriebskegelrads (70) nach vorn in Richtung des Anlaßrads (68) zu ermöglichen, wenn sich die Ausgangswelle (12) unter der Einwirkung ihrer Einschraubung in die vordere kegelstumpfartige Antriebsrolle (82) und der Herbeiführung des reibschlüssigen Kontakts dieser Antriebsrolle gegen das Anlaßrad (68) bis zur Herbeiführung des reibschlüssigen Kontakts des Antriebskegelrads (70) mit dem Anlaßrad (68) axial nach vorn verschiebt.
  24. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß die Ausgangswelle (12) an der Ankerwelle (14) über ein Untersetzungsgetriebe (18) angebracht ist, dessen rotierender Teil (36, 40) axial verschiebungsfest mit der Ausgangswelle (12) verbunden ist, und daß der rotierende Teil (36, 40) des Untersetzungsgetriebes (18) axial gleitend an der Ankerwelle (14) und am ortsfesten Teil (44) des Untersetzungsgetriebes (18) gelagert ist.
  25. Anlasser (10) nach Anspruch 23 oder 24, dadurch gekennzeichnet, daß der Winkel des Kegelstumpfes der kegelstumpfartigen Antriebsrolle (82) mit dem Winkel des Kegelstumpfes des Antriebskegelrads (70) identisch ist.
  26. Anlasser (10) nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Kegeistumpfflächen (110, 112, 86, 74) des Anlaßrads (68), der kegelstumpfartigen Antriebsrolle (82) und/oder des Antriebskegelrads (70) Reibbeläge umfassen.
  27. Anlasser (10) nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß der Elektromotor (16) durch ein Relais gespeist wird, von dem eine Betätigungsspule durch einen Zündschlüssel betätigt wird.
  28. Anlasser (10) nach dem vorangehenden Anspruch, dadurch gekennzeichnet, daß das Relais ein allmähliches Anlaufen durch eine kurzzeitige Senkung der Speisespannung des Elektromotors (16) durch Zerhacken des Speisestroms bewirkt.
EP00958652A 1999-08-09 2000-08-07 Kraftfahrzeug-anlasser mit reibungsantrieb Expired - Lifetime EP1119707B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9910386A FR2798167B1 (fr) 1999-08-09 1999-08-09 Demarreur de vehicule automobile comportant un dispositif d'entrainement par friction
FR9910386 1999-08-09
PCT/FR2000/002264 WO2001011232A1 (fr) 1999-08-09 2000-08-07 Demarreur de vehicule automobile du type a entrainement par friction

Publications (2)

Publication Number Publication Date
EP1119707A1 EP1119707A1 (de) 2001-08-01
EP1119707B1 true EP1119707B1 (de) 2004-06-30

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EP00958652A Expired - Lifetime EP1119707B1 (de) 1999-08-09 2000-08-07 Kraftfahrzeug-anlasser mit reibungsantrieb

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JP (1) JP4503898B2 (de)
KR (1) KR20010080027A (de)
BR (1) BR0006993A (de)
DE (1) DE60011865T2 (de)
FR (1) FR2798167B1 (de)
WO (1) WO2001011232A1 (de)

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Publication number Priority date Publication date Assignee Title
FR2864583B1 (fr) * 2003-12-26 2006-03-03 Valeo Equip Electr Moteur Demarreur coaxial perfectionne de vehicule automobile
FR2865243B1 (fr) * 2004-01-16 2009-06-26 Denso Corp Demarreur avec limitation des vibrations et de l'inclinaison de l'arbre de sortie
US8408175B2 (en) * 2010-08-03 2013-04-02 GM Global Technology Operations LLC Stop-start self-synchronizing starter system

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB475599A (en) * 1936-01-09 1937-11-23 Gen Motors Corp Improvements in or relating to engine starters
US4092870A (en) * 1976-08-30 1978-06-06 Facet Enterprises, Inc. Engine starting mechanism
JPS59173556A (ja) * 1983-03-22 1984-10-01 Mitsubishi Electric Corp 摩擦ロ−ラ式動力係合装置
US4738148A (en) * 1984-12-12 1988-04-19 Peter Norton Starter drive

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Publication number Publication date
EP1119707A1 (de) 2001-08-01
DE60011865T2 (de) 2005-08-25
JP4503898B2 (ja) 2010-07-14
FR2798167B1 (fr) 2001-10-12
KR20010080027A (ko) 2001-08-22
BR0006993A (pt) 2001-06-26
WO2001011232A1 (fr) 2001-02-15
FR2798167A1 (fr) 2001-03-09
DE60011865D1 (de) 2004-08-05
JP2003506628A (ja) 2003-02-18

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