EP0518895B1 - Dispositif de demarrage avec un blocage de l'arbre menant - Google Patents

Dispositif de demarrage avec un blocage de l'arbre menant Download PDF

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Publication number
EP0518895B1
EP0518895B1 EP91904528A EP91904528A EP0518895B1 EP 0518895 B1 EP0518895 B1 EP 0518895B1 EP 91904528 A EP91904528 A EP 91904528A EP 91904528 A EP91904528 A EP 91904528A EP 0518895 B1 EP0518895 B1 EP 0518895B1
Authority
EP
European Patent Office
Prior art keywords
spring
starting device
armature
engagement
ring
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
Application number
EP91904528A
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German (de)
English (en)
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EP0518895A1 (fr
Inventor
Werner Rometsch
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0518895A1 publication Critical patent/EP0518895A1/fr
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Publication of EP0518895B1 publication Critical patent/EP0518895B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F02N15/067—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 the starter comprising an electro-magnetically actuated lever
    • 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
    • F02N15/022—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch
    • F02N15/023—Gearing between starting-engines and started engines; Engagement or disengagement thereof the starter comprising an intermediate clutch of the overrunning type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/13—Machine starters
    • Y10T74/131—Automatic
    • Y10T74/132—Separate power mesher

Definitions

  • the invention relates to a starting device according to the preamble of patent claim 1.
  • a thrust screwing operation is provided which engages a pinion of the changing device into a squab ring of the internal combustion engine.
  • the engagement relay picks up and moves the pinion in the axial direction via an engagement lever in such a way that it can come into effect with the ring gear of the internal combustion engine.
  • a starter motor starts to rotate. As soon as the pinion engages in the ring gear due to the thrust movement, it is moved further in the axial direction against a stop by the rotation of the starter motor with the aid of a steep thread assigned to the output shaft.
  • a return spring presses the armature of the engagement relay and thus - via the engagement lever - the pinion back into its rest position.
  • This disengagement is supported by the steep thread when overtaking by starting the internal combustion engine.
  • the freewheel device protects the starter rotor from excessive speeds when overtaking by the internal combustion engine.
  • the output shaft carrying the pinion and provided with the steep thread tends to move towards the toothed ring of the internal combustion engine when this movement due to braking moments, for example due to a shaft sealing ring and / or the existing bearings opposing forces of the return spring are smaller than the axial force component on the high-helix thread.
  • the pinion on the running gear ring of the internal combustion engine can start up and be damaged.
  • known starting devices are e.g. provided with a ball lock.
  • a spring-loaded slide secures the axial position of the output shaft carrying the pinion.
  • the aforementioned slide is moved so that the ball can be moved radially outwards.
  • the output shaft is released for axial movement.
  • This ball lock requires highly precise and elaborately designed components, which leads to a complicated and expensive design.
  • a locking device is known in which a part actuated by the armature of the engagement relay is provided with clamping rollers which, on the one hand, take the engagement lever to engage the pinion when the internal combustion engine is turned on by pulling in the armature and, on the other hand, when the engagement relay is switched off by the return spring of the armature, run onto wedge-shaped surfaces of the engagement lever and the locking device attached to the starter housing and are clamped there.
  • clamping effect is particularly dependent on the force of the return spring of the armature, so that over time there are wear and tear on the clamping surfaces and rollers, which reduce the clamping effect or increase it so much that the subsequent one Single-track operation is hindered or even blocked.
  • the present invention strives to provide a structurally simple and reliable locking device.
  • the starting device according to the invention with the characterizing features mentioned in the main claim has the advantage that it reliably prevents the leading of the output shaft carrying the pinion in the non-energized state of the engagement relay with a simple structure. Since, according to the invention, the locking device acts on the armature of the engagement relay in order to secure the rest position of the pinion, no complicated locking is required, but it is possible to resort to structurally simple solutions, since sufficient space is available for such solutions in the area of the engagement relay.
  • the locking device according to the invention which acts on the armature of the engagement relay and thus on the engagement lever, can also be easily assembled since, as in the known ball locking, special mounting positions for introducing the balls do not have to be used.
  • the locking device has a locking member which engages behind a stop of the armature in the drop-out position of the engagement relay and which is operated by means of a positive control by the tightening movement the anchor can be moved to the release position.
  • the armature By energizing the engagement relay, which is caused by the triggering of the starting process of the internal combustion engine, the armature starts to pull in, which releases the locking by means of a positive control, that is to say the locking member is shifted into the release position.
  • the engagement lever is released and can be pivoted by the armature, as a result of which the pinion arranged on the output shaft is axially displaced so that it engages in the ring gear of the internal combustion engine.
  • the engagement relay At the end of the starting process, the engagement relay is de-energized so that the return spring moves the armature back into the rest position (drop position), the output shaft being carried along via the engagement lever.
  • the locking member secures the anchor position, so that inadmissible re-toe-in is prevented.
  • the armature runs through an empty path to bring about the release position before the engagement lever is carried along. Because of this free travel, it is possible that the locking member can first be moved into its release position, that is to say that an unlocking position is brought about by the movement of the armature, so that subsequently -im In the course of the further anchor movement - the entrainment of the engagement lever for engaging the pinion becomes possible.
  • the locking member is preferably a first spring provided with at least one rear grip step, which can be deflected in the release position by means of a control sleeve arranged on a plunger of the armature.
  • the control sleeve moving with the armature thus displaces the locking member in the release position.
  • the control sleeve releases the locking member, which is designed as a spring, in the drop position of the engagement relay, so that the rear grip step for securing the armature position of the engagement relay brings about securing the position.
  • the stop is preferably formed by a ring mounted on the control sleeve.
  • the axial position of the ring can be fixed or released by means of the locking member.
  • the fixed position of the ring prevents a pivoting movement of the engagement lever, so that the output shaft cannot get into its toe-in position.
  • the control sleeve bears against an armature stop by the force of a second spring.
  • This position of the control sleeve is only left with further tensioning of the second spring if engagement of the pinion in the toothed ring of the internal combustion engine is initially prevented due to a tooth-on-tooth position.
  • the second spring nevertheless enables the engagement relay to be tightened, so that contacts of the engagement relay 'are closed at the start of the rotary movement of the starting device. This results in a relative movement between pinion and ring gear, so that a corresponding pinion tooth can enter a tooth gap on the ring gear.
  • a compression spring assigned to the pinion can also be tensioned, which enables a relative movement between pinion and output shaft.
  • control sleeve is arranged axially displaceable relative to the armature in the direction of its fall against the force of the second spring.
  • one side of the ring interacts with the engagement lever, taking into account the free travel.
  • a third spring acts on the other side of the ring.
  • the ring assumes a securing position for the engagement lever when the engagement relay is not energized.
  • one end of the third spring is supported on the housing of the starter and the other end on the ring.
  • a control sleeve stop which limits a displacement path of the ring which is possible in the drop direction and is possible by the force of the third spring.
  • the control sleeve stop thus allows a displacement of the ring by the force of the third spring only up to a certain position.
  • the first spring is designed in particular as a bow spring, which has a rear grip step on each leg having. By shifting the control sleeve, the bow spring can be spread to the release position.
  • the second spring is preferably a helical compression spring, which coils the tappet and is supported at one end against a tappet stop and, at the other end, strikes a control sleeve step.
  • the control sleeve is biased towards the armature so that it rests against the armature stop.
  • the third spring can be designed as a helical compression spring which surrounds the control sleeve. This results in a simple and space-saving structure.
  • the control sleeve has a control collar for spreading the bow spring.
  • the bow spring is fastened to the housing of the starting device in the direction of the longitudinal extension of the plunger.
  • FIG. 1 shows a longitudinal section through a starter device 1.
  • This has a housing 2 in which a direct current motor 3 and an engagement relay 4 are accommodated.
  • the DC motor 3 has a starter rotor 5 which acts on an output shaft 6, on the end 7 of which a pinion 8 is arranged in a rotationally fixed manner.
  • the pinion 8 advances to the position 9 shown in broken lines in FIG.
  • the engagement of relay 4 causes the pinion to move axially to position 9. This will be discussed in more detail below.
  • the starter rotor 5 is provided with a commutator 11, to the segments 12 of which a rotor winding 13 is connected.
  • the commutator 11 interacts with a carbon brush arrangement 14.
  • a stator 15 with a stator winding 16 is provided, which is opposite the starter rotor 5 with a small air gap.
  • the starter rotor 5 has a rotor shaft 17 which is supported at one end 18 in a needle bearing 19 and covered by a housing cap 20.
  • the other end of the rotor shaft 17 has a central receiving bore 22 extending from its end face 21, into which the one end 23 of the output shaft 6 engages.
  • the other end of the rotor shaft 17 is mounted on the end 23 of the output shaft 6 via a needle bearing 31 which is arranged in the receiving bore 22.
  • the lateral surface 24 of the end 25 of the rotor shaft 17 provided with the receiving bore 22 is designed as a sun gear 26 which meshes with planet gears 27 which are arranged on a planet carrier 28 (only one planet gear 27 is shown in FIG. 1).
  • the planet gears 27 are arranged with the interposition of needle bearings on bearing pins 29.
  • the planet gears 27 mesh with a ring gear 30 provided with internal teeth, which is arranged in a stationary manner in the housing 2.
  • the end 23 of the output shaft 6 is mounted in the receiving bore of the axial web 39 via a needle bearing 37.
  • the freewheel outer ring 35 is held by a deep groove ball bearing 38, which is arranged on the axial web 39 and on the other hand is supported in the housing 2 (fixed bearing).
  • a cylindrical roller bearing 33 is provided — held by the housing 2, to which a sealing ring 34 is connected upstream — to the outside.
  • the cylindrical roller bearing 33 guides the output shaft 6 both in the axial and in the radial direction.
  • the planet carrier 28 is axially connected to a freewheel outer ring 35 via screws 36.
  • the freewheel outer ring 35 belongs to a freewheel device 40 which is designed as a roller freewheel. It has spring-loaded rollers 41 which interact with an inner ring 42 of the freewheel device 40.
  • the inner ring 42 is connected to the output shaft 6 via a steep thread 43.
  • the output shaft 6 has a groove 44 in which a snap ring 45 is arranged.
  • the snap ring 45 forms a stop which, in the event of an axial displacement of the output shaft 6 to be described in greater detail, cooperates with a step 46 of the inner ring 42.
  • a retaining ring 47 which has a radial collar 48, is fastened on the output shaft 6. Furthermore, a snap ring 50, which supports a disk 51, lies in a groove 49 of the retaining ring 47. An annular channel 52 is thus formed between the disk 51 and the radial collar 48.
  • the pinion 8 is rotatably but axially displaceably mounted. It is acted upon by a helical compression spring 54. This is preloaded when a tooth-on-tooth position results when the pinion 8 is engaged in the ring gear 10.
  • the engagement relay 4 has a fixed relay winding 61 which interacts with an armature 62.
  • the armature 62 is axially displaceably mounted and is not excited by a return spring 113 designed as a helical compression spring State of the engagement relay 4 pushed into the position shown in FIG.
  • the axis 63 has at its one end region 65 a contact element 66 that can interact with electrical connections 67.
  • the armature 62 is connected to a plunger 68 which projects into a housing space 69 of the housing 2.
  • the plunger 68 interacts with an engagement lever 70 designed as a double lever, which is pivotably mounted approximately in its central region by means of a cross bolt 71.
  • the cross pin 71 is held on a housing-side arm 72.
  • the lower end 73 of the engagement lever 70 is provided with a projection 74 which engages in the annular channel 52.
  • a driving head 76 is formed at the other end 75 of the engagement lever 70.
  • a locking device 77 prevents the pinion 8 from inadvertently moving in the direction of the ring gear 10 of the internal combustion engine, since this could damage the parts. This unintentional axial movement can occur due to the fact that braking moments, which occur, for example, due to the bearings and shaft sealing rings, move the output shaft 6 into the engagement position, that is to say the return spring forces are smaller than the axial force components occurring on the high-helix thread.
  • the formation of the locking device 77 will now be discussed.
  • the locking device 77 fixes the position of the engagement lever 70 shown in FIG. 1 in the deenergized state of the engagement relay 4, so that the output shaft 6 assumes a fixed axial position.
  • the locking device 77 acts on the armature 62, in particular on the plunger 68, of the engagement relay 4 in order to secure the idle position of the pinion 8.
  • the locking device 77 has a locking member 78 which is designed as a first spring 79.
  • the first spring 79 is a bow spring 80 (compare in particular also FIG. 2).
  • the bow spring 80 has two legs 81 which are shaped such that each is provided with a rear grip step 82.
  • the ends 83 of the two legs 81 are divergingly bent outwards, as a result of which bevel slopes 84 are formed.
  • the areas 85 of the legs 81 opposite the run-up bevels 84 are each designed such that - starting from the rear grip step 82 - a section 86 initially runs approximately parallel to the plunger 68, to which a control section 87 then adjoins, which runs diverging outwards and in an arc section 88 merges, which is curved in the opposite direction to the control section 87, with a bend at an angle greater than 90 °.
  • the subsequent end 89 of each leg 81 is fastened in a holder 90.
  • the holder 90 is connected to a threaded screw 91 which extends coaxially to the plunger 68 and is mounted in a bore 92 in the housing 2.
  • the end 93 of the threaded screw 91 protruding outward from the housing 2 is secured by means of a lock nut 94.
  • the plunger 68 connected to the armature 62 of the engagement relay 4 has at its free end 95 an annular groove 96 into which a snap ring 97 is inserted.
  • a disk 98 is supported on the snap ring 97, which is supported on the tappet 68 and is acted upon by a second spring 99. The disk 98 therefore forms a tappet stop 100.
  • the second spring 99 is designed as a helical compression spring 101, which surrounds the tappet 68 and is supported with one end 102 on the tappet stop 100 and with its other end 103 on a control sleeve step 104 of a control sleeve 108.
  • the latter is mounted on the ram 68.
  • the control sleeve step 104 is formed in that the control sleeve 108 is axially penetrated by a stepped bore 105.
  • the force of the helical compression spring 101 pushes the end face 106 facing the armature 62 against an armature stop 107.
  • the helical compression spring 101 is mounted in the section of the stepped bore 105 having the larger diameter.
  • control sleeve 108 At its end facing away from the armature 62, the control sleeve 108 has an axially protruding control collar 109 which, as described in more detail below, interacts with the control sections 87 of the bow spring 80.
  • the control sleeve 108 has different outer diameters, whereby a control sleeve stop 110 is formed.
  • the control sleeve stop 110 faces the armature 62.
  • a disk 111 is pressed against the control sleeve stop 110 by means of a third spring 112, which is designed as a helical compression spring 113.
  • One end 114 of the helical compression spring 113 is supported on the housing 2 and the other end 115 on the disk 111.
  • a stop 116 bears against the disk 111, which is designed as a ring 117 and is located on the larger-diameter section of the control sleeve 108.
  • the bow spring 80 is supported on the lateral surface 118 of the ring 117 in the positions shown in FIGS. 1 and 2.
  • the driving head 76 does not completely fill the distance between the one side 119 of the ring 117 and an end face 120 of the control collar 108; rather, an empty path remains b.
  • the steep thread 43 allows an axial displacement of the output shaft 6 by the dimension a.
  • the starting device 1 operates as follows:
  • the engagement relay 4 is energized via a start switch. This leads to the armature 62 moving to the right (FIG. 1), as a result of which the control collar 109 runs against the control sections 87 of the bow spring 80 in such a way that the latter is expanded radially. This gives the rear grip levels 82 the leg 81 the ring 117 free. As long as the ring 117 is engaged by the rear grip steps 82, a relative movement between the control sleeve 108 and the ring 117 is possible while consuming the free travel b because the latter is axially displaceably mounted on the larger diameter of the control sleeve 108.
  • the dragging of the control sleeve 108 by axial displacement of the plunger 68 is effected via the helical compression spring 101.
  • the bow spring 80 assumes its spread position (FIG. 3)
  • the free travel b is used up, that is to say the left side of the driving head 76 is carried along by the end face 120.
  • the engagement lever 70 pivots clockwise around the cross pin 71.
  • the projection 74 shifts the output shaft 6 in the direction of the ring gear 10, as a result of which the pinion 8 engages in the toothing of the ring gear 10.
  • the occurring engagement forces ensure that the pinion 8 now completely retracts into the ring gear 10, the output shaft 6 extending axially due to the steep thread 43, so that — as a result — the position 9 shown in FIG.
  • the engagement relay 4 drops out.
  • the return movement is supported by the return springs 64 and 112.
  • the ring 117 comes with its side 119 against the driving head 76 of the engagement lever 70, so that the engagement lever 70 pivots counterclockwise, whereby the pinion 8 is brought back into the position shown in solid line in FIG. Since the internal combustion engine, which is now in operation, "overtakes” the rotation of the pinion 8 in the final stage of the starting process, the disengagement process is supported by the steep thread 43.

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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)
  • Valve Device For Special Equipments (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un dispositif de démarrage comportant un relais d'embrayage, dont l'induit déplace dans le sens axial, par l'intermédiaire d'un levier d'embrayage, un pignon qui coopère avec un dispositif de roue libre et un rotor de démarrage pour l'entraînement d'une couronne dentée d'un moteur à combustion interne, et comportant également un dispositif de blocage qui empêche l'engagement du pignon lorsque le relais d'embrayage n'est pas excité. Pour assurer la simplicité de la construction, il est proposé que le dispositif de blocage (77) s'engage dans l'induit (62) du relais d'embrayage (4) pour assurer la position de repos du pignon (8).

Claims (12)

  1. Dispositif de démarrage, notamment dispositif de démarrage se dégageant librement, avec un relais d'embrayage (4) dont l'armature déplace axialement, par l'intermédiaire d'un levier d'embrayage (70), un pignon (8) coopérant avec un dispositif de roue libre (40) ainsi qu'avec un rotor de démarrage pour l'entraînement d'une couronne dentée (10) d'un moteur à combustion interne, et avec un dispositif de verrouillage (77) qui empêche le pré-engrènement du pignon lorsque le relais d'embrayage n'est pas excité, ce dispositif de verrouillage (77) venant en prise avec un organe de verrouillage (78) à poste fixe sur une pièce (117) actionnée par l'armature (62) du relais d'embrayage (4), pour le blocage de la position de repos du pignon (8), dispositif de démarrage caractérisé en ce que l'organe de verrouillage (78) est un premier ressort (79) muni d'au moins un redent de retenue (82) qui, au moyen d'une douille de commande (108) disposée sur un poussoir (68) de l'armature (62), est susceptible d'être dévié dans une position de libération.
  2. Dispositif de démarrage selon la revendication 1, caractérisé en ce que l'organe de verrouillage (78) est un ressort en forme de fourche (80) courbé en forme de U, venant en prise par ses branches (81) derrière une butée (116) de l'armature (62) dans la position de retombée du relais d'embrayage (4).
  3. Dispositif de démarrage selon la revendication 2, caractérisé en ce que l'armature (62), avec le poussoir (68) et la douille de commande (108), parcourt une course à vide (b) pour provoquer la position de libération avant qu'un entraînement du levier d'embrayage (70) s'effectue.
  4. Dispositif de démarrage selon la revendication 2, caractérisé en ce que la butée (116) est constituée par un anneau (117) monté sur la douille de commande (108).
  5. Dispositif de démarrage selon l'une des revendications 1 à 4, caractérisé en ce que la douille de commande (108) s'applique, par l'action d'un second ressort (99), contre une butée d'armature (107) et est susceptible d'être déplacée axialement par rapport à l'armature (62) dans la direction de retombée de celle-ci.
  6. Dispositif de démarrage selon l'une des revendications 4 ou 5, caractérisé en ce que l'une des faces frontales (119) de l'anneau (117) coopère avec le levier d'embrayage (70), tandis que l'autre face frontale de l'anneau (117) coopère avec un troisième ressort (112), de sorte qu'une extrémité (114) du troisième ressort (112) prend appui contre le carter (2) du dispositif de démarrage (1), tandis que l'autre extrémité (115) de ce troisième ressort (112) prend appui contre l'anneau (117).
  7. Dispositif de démarrage selon la revendication 6, caractérisé par une butée (110) de douille de commande qui limite une course de coulissement de l'anneau (117) allant en direction de la retombée et rendue possible par l'action du troisième ressort (112).
  8. Dispositif de démarrage selon la revendication 2, caractérisé en ce que le ressort en forme de fourche (80) comporte sur chaque branche (81) un redent de retenue (82).
  9. Dispositif de démarrage selon la revendication 2, caractérisé en ce qu'au moyen du déplacement de la douille de commande (108), le ressort en forme de fourche (80) et susceptible d'être écarté par une collerette (109) de la douille de commande (108) pour l'obtention de la position de libération.
  10. Dispositif de démarrage selon l'une des revendications 1 à 9, caractérisé en ce que le ressort en forme de fourche (80) est fixé sur le carter (2) du dispositif de démarrage (1) de façon réglable en direction de l'étendue longitudinale du poussoir (68).
  11. Dispositif de démarrage selon l'une des revendications 5 à 10, caractérisé en ce que le deuxième ressort (99) est un ressort hélicoïdal de poussée (101) qui entoure le poussoir (68) et prend appui par une extrémité (102) contre une butée (100) du poussoir, tandis que par son autre extrémité (103), le ressort arrive contre un redent (104) de la douille de commande.
  12. Dispositif de démarrage selon l'une des revendications 6 à 11, caractérisé en ce que le troisième ressort (112) est un ressort hélicoïdal de poussée (113) qui entoure la douille de commande (108).
EP91904528A 1990-03-03 1991-02-22 Dispositif de demarrage avec un blocage de l'arbre menant Expired - Lifetime EP0518895B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4006796A DE4006796A1 (de) 1990-03-03 1990-03-03 Andrehvorrichtung mit abtriebswellenverriegelung
DE4006796 1990-03-03
PCT/DE1991/000142 WO1991014096A1 (fr) 1990-03-03 1991-02-22 Dispositif de demarrage avec un blocage de l'arbre menant

Publications (2)

Publication Number Publication Date
EP0518895A1 EP0518895A1 (fr) 1992-12-23
EP0518895B1 true EP0518895B1 (fr) 1994-07-27

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP91904528A Expired - Lifetime EP0518895B1 (fr) 1990-03-03 1991-02-22 Dispositif de demarrage avec un blocage de l'arbre menant

Country Status (8)

Country Link
US (1) US5245881A (fr)
EP (1) EP0518895B1 (fr)
JP (1) JPH05504811A (fr)
DE (2) DE4006796A1 (fr)
ES (1) ES2057871T3 (fr)
HU (1) HU208726B (fr)
RU (1) RU2048654C1 (fr)
WO (1) WO1991014096A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2760491A1 (fr) * 1997-03-07 1998-09-11 Bosch Gmbh Robert Demarreur a degagement libre

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2722037B1 (fr) * 1994-07-04 1996-08-02 Valeo Equip Electr Moteur Induit de machine electrique tournante et demarreur de vehicule automobile comportant un tel induit
FR2745854B1 (fr) * 1996-03-08 1998-04-10 Valeo Equip Electr Moteur Demarreur de vehicule automobile comportant un pignon d'engrenement sans roue libre
DE29704209U1 (de) 1997-03-07 1998-07-02 Robert Bosch Gmbh, 70469 Stuttgart Freiausstoßender Starter
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DE59102367D1 (de) 1994-09-01
RU2048654C1 (ru) 1995-11-20
HU9202825D0 (en) 1992-12-28
WO1991014096A1 (fr) 1991-09-19
HU208726B (en) 1993-12-28
JPH05504811A (ja) 1993-07-22
HUT61613A (en) 1993-01-28
DE4006796A1 (de) 1991-09-12
US5245881A (en) 1993-09-21
ES2057871T3 (es) 1994-10-16
EP0518895A1 (fr) 1992-12-23

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