EP2411658B1 - Moteur électrique à amortissement intégré pour un élément d'engrenage - Google Patents

Moteur électrique à amortissement intégré pour un élément d'engrenage Download PDF

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Publication number
EP2411658B1
EP2411658B1 EP10709524.2A EP10709524A EP2411658B1 EP 2411658 B1 EP2411658 B1 EP 2411658B1 EP 10709524 A EP10709524 A EP 10709524A EP 2411658 B1 EP2411658 B1 EP 2411658B1
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EP
European Patent Office
Prior art keywords
webs
electrical machine
machine according
housing
ring gear
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Active
Application number
EP10709524.2A
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German (de)
English (en)
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EP2411658A1 (fr
Inventor
Steffen Huemmer
Dieter Spaeth
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2411658A1 publication Critical patent/EP2411658A1/fr
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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
    • F02N15/062—Starter drives
    • F02N15/063—Starter drives with resilient shock absorbers

Definitions

  • FR2 639.701 refers to a reduction gear, which is a planetary gear.
  • the ring gear of the planetary gear is supported by means of elastic elements in a housing.
  • the planetary gear comprises, in addition to the ring gear at least two planet gears, which mesh with an external toothing of a sun gear and the internal toothing of the supported via the elastic elements ring gear.
  • US 2003/0177852 A1 discloses a starter having elastically formed damping elements for both axial and circumferential vibrations to dampen the vibrations created during the starter phase of the starter. Also the starter according to US 2003/0177852 A1 includes a planetary gear.
  • DE 43 02854 C1 refers to a starting device for internal combustion engines.
  • a starting device for internal combustion engines which has a starter motor and a one-way clutch in the drive train of the direction of rotation.
  • a spring accumulator is provided in the drive train.
  • the spring accumulator has a preload torque of 15% to 50% of the short circuit torque of the crank motor.
  • the spring accumulator is between a ring gear of a planetary gear and a fixed part of the housing of the starter arranged.
  • the spring accumulator consists of several distributed on the circumference of the ring gear arranged spring elements, which are supported on the fixed housing part.
  • the spring elements press the ring gear with at least one projection formed thereon to form a bias against the drive direction of the starter against at least one housing fixed stop.
  • the projections on the ring gear are directed radially outward and arranged the spring elements on the outer circumference of the ring gear.
  • the spring elements are, for example, helical compression springs or other curved leaf springs.
  • the starters which are used in internal combustion engines used today, include an internal planetary gear for reasons of available space. Together with the pinion of the starter and the vehicle sprocket can set an optimal gear ratio for starting an internal combustion engine.
  • On the planetary gear strong torque fluctuations act. At each compression, in case the freewheel closes, a shock load in the planetary gear becomes effective. Otherwise, the torque acts by turning the internal combustion engine in a continuous manner on the ring gear.
  • the planetary gear Due to the shape and position tolerance of the drive train and the electric motor of the starter, the planetary gear, in particular the ring gear, heavily loaded and is exposed to high wear. In order to protect particularly loaded ring gears and extend their life, they are not, as is generally customary in plastic, but made of sintered metal.
  • a damping is realized by means of resilient rubber additional elements, as described above the example of FR 2 639, 701 , of the US 2003/0177852 A1 and the DE 43 02854 C1 is disclosed.
  • the solution proposed by the invention makes it possible to dispense with the use of sintered metal hollow wheels with additional spring elements made of rubber on electrical machines, in particular starters for internal combustion engines, as known from the prior art.
  • a ring gear made of plastic for use in a planetary gear can be used, in which the damping is formed directly on the interface to a drive bearing for the realization of a torque support.
  • the damping can be adjusted by simple modification to be made.
  • the degree of damping; which can be effected in the form of nose-shaped projections with the respectively acting on a cover plate, acting in the circumferential direction of torque support is influenced by the shape and can be adapted in an advantageous manner to the torque to be supported.
  • the proposed solution according to the invention makes a use of previously manufactured by way of the sintering process, made of metallic material ring gears for planetary gear superfluous. This can be a considerable savings in terms of manufacturing costs realized.
  • the proposed solution according to the invention makes the use of additional damping elements made of rubber-elastic material or rubber superfluous.
  • the torque support with respect to the ring gear remains integrated in it, so that no structural changes, in particular to a starter for internal combustion engines or other electric machines, on which epicyclic gears are used, are provided.
  • the damping is achieved by a through the shaping and geometric design or a targeted weakening of the torque supports of the ring gear in the drive bearing taking advantage of the relaxation capacity reached the plastic. It is initiated a targeted tangential movement.
  • slits be it symmetric single slits, symmetrical double slits or asymmetric double slits or targeted weakenings in the material due to the geometry of the individual remaining webs or between them resulting free spaces become.
  • the proposed solution according to the invention provides that the torque support due to the slits act as resilient elements in which a damping capacity can be specified by the geometry and number of slits. Due to the tangential resilient elements formed torque supports torque peaks are reduced, so that the mechanical stress acting on the now made of plastic ring gear, can be significantly reduced.
  • the torque support for a transmission component of a planetary gear on a housing is advantageously provided as a symmetrical or asymmetrical torque support with material weakenings that absorb load peaks.
  • a plurality of torque supports distributed in the circumferential direction are executed on a cover plate and have webs. The webs are separated. The webs are formed so that these support surfaces which bear against the housing, in particular on an end face of the housing.
  • the webs act in contact with the housing as leaf springs or bending beams.
  • the symmetrical material weakening is designed as a single or multiple slits with at least two webs and at least one free space lying between them.
  • the asymmetrically formed material weakening comprises webs of different widths.
  • the narrower of the two webs arranged corresponding to the direction of rotation of the epicyclic gear and the wider of the two webs is the narrower of the webs with respect to the direction of rotation arranged trailing.
  • the torque support comprises separate, the housing inner wall assigning surface sections.
  • the proposed torque support also includes in a variant in the wider of the webs a notch-shaped depression, which serves as a material weakening.
  • the manufacturing method for producing the inventively proposed torque support for a transmission component of a planetary gear is characterized in that distributed to a manufactured in plastic injection molding cover plate in the circumferential direction, torque supports are molded, comprising a symmetrical or asymmetrical running material weakening.
  • FIG. 1 is a schematic diagram of construction and electrical circuit to take a starter for internal combustion engines.
  • a starter 10 for an internal combustion engine has a pinion 12 received on an armature shaft of an armature 26. This can be brought into engagement with a ring gear 2 of the internal combustion engine.
  • There is a roller freewheel 16 between the actuatable via the contactor 30 engaging lever 18 and the pinion 12 in the starter 10 is also a planetary gear, in particular a planetary gear 20 is added.
  • the planetary gear 20 has the general advantage that this has a very compact design with high achievable gear ratios.
  • the planetary gear 20 With the favorable meshing geometry of the planetary gear 20, high torques can be transmitted with low noise. Outwardly, the planetary gear 20 is free of transverse forces, so that the bearings of the shaft of the armature 26 and the drive shaft are loaded even at high power only with low shear forces.
  • the planetary gear 20 includes a ring gear 44. Its drive via a sun gear 46, which is connected to the shaft of the armature 26 of the electric drive of the starter 10. At least two planet gears 48 are engaged with both the sun gear 46 and the internal teeth of the ring gear 44. During their rotation, the planet gears 48 drive the drive shaft via their bearing journals, on which the roller freewheel 16 is accommodated.
  • the electric drive of the starter 10 further includes a pole piece 22, which is associated with a field winding 24.
  • the pole pieces 22 enclose an armature 26.
  • the electric drive of the starter 10 comprises a commutator 28, on the periphery of which a plurality of carbon brushes are employed.
  • Above the electric drive of the starter 10 is the already mentioned engagement relay 30, which is actuated by means of a start switch 32.
  • a start switch 32 By means of the start switch 32 is an electrical connection to a battery 34, which also in the schematic diagram according to FIG. 1 is indicated, closed or opened.
  • FIG. 2 shows a variant according to the prior art, in which a cover plate is supported on a housing.
  • a cover plate 42 comprises on its inside a number of circumferentially arranged torque supports 50, hereinafter also referred to simply as supports 50.
  • supports 50 are covered by the housing 62.
  • the transmission component in particular the ring gear 44 of in FIG. 1 schematically indicated circulating gear 20, so for example a planetary gear 20 was added.
  • the protruding beyond the end face of the cup-shaped cover plate 42 extend in ways a closed support surface 60, and a first web 56 and a second web 58.
  • the closed support surfaces 60, supported by the webs 56, 58 extend into receiving grooves 52, which are executed on a housing inner wall 54 of the housing 62.
  • FIG. 3 is a perspective view of the in FIG. 2 To remove the cover plate attached to the housing.
  • FIG. 3 From the perspective view of the cover plate according to FIG. 3 shows that on the circumference of the cover plate 42 six circumferentially distributed assumed supports 50 are formed, each having a closed support surface 60.
  • the closed support surface 60 as shown in FIG. 2 protrude into the receiving grooves 52 on the housing inner wall 54 of the housing 62 are supported by two likewise spaced apart webs, the first web 56 and the second web 58.
  • Inside the cover plate 42 is a transmission component, in particular a ring gear 44, whose torque is to be supported.
  • planetary gears 48 are received, which mesh with a sun gear 46.
  • the representation according to FIG. 4 is a variant of the present invention proposed solution for supporting a transmission component of a planetary gearbox refer.
  • FIG. 4 As can be seen from the illustration according to FIG. 4 can be seen, are at the front side of the cover plate 42 shown in Figure also formed in a 60 ° division of separate supports 50. Unlike the solution according to FIG. 3 are these in FIG. 4 shown supports 50 provided with an asymmetric material weakening 64, in particular a single slot. Due to the asymmetrical material weakening 64, a narrow web is created, cf. Reference numeral 66, and a wider web, cf. Position 68. On the side facing a drive bearing 40 side, the webs 66, 68 of the asymmetrical material weakening 64 support surfaces 72, with which the Support 50 or the supports 50 on the front z. B. a drive bearing 40 abut.
  • this transmission component 44 can also be made of plastic material with a lower mechanical strength.
  • the cover plate 42 has a central passage opening 82. Due to the asymmetrically formed material weakening 64, in particular a slit of the support 50, separate support surface sections 86 are formed thereon.
  • the location of the narrow web 66 and the wide web 68 selected so that this arrangement is specifically designed for loads by planet gears 48 of a planetary gear 20, seen from the starting pinion 12, seen in the direction of the starter motor, counterclockwise in the ring gear 44, which is to be supported in the cover plate 42, moved.
  • the wider of the two webs, ie the web 68 is the trailing edge 66 of the narrow web 66 in the rotation of the planet gears 48 arranged counterclockwise.
  • the cover plate 42 which is preferably produced by way of plastic injection molding, formed six supports 50, a larger or smaller number of supports 50 can be molded.
  • the supports 50 may also be provided with a rubber jacket for selectively influencing the damping characteristic.
  • the representation according to FIG. 5 is a further embodiment of the inventively proposed torque support for a transmission component of a planetary gearbox refer.
  • FIG. 5 shows that on the front side of the cover plate 42 manufactured in the way of the preferably produced by the plastic injection molding process, a number of supports is molded, which is a symmetrical material weakening 70, preferably formed as a slit.
  • a symmetrical material weakening 70 preferably formed as a slit.
  • Each of the symmetrical material weakenings, ie each slot 70 has a first web 71 and a further second web 73. Due to the slit arise the grooves 52 on the housing inner wall 54, each zu josde Abstützberichtabismee, see. Position 86.
  • a free space which separates the first web 71 and the second web 73 from each other is indicated by reference numeral 80. Also according to in FIG.
  • FIG. 5 illustrated second embodiment of the solution proposed by the invention respectively support surfaces 72 are formed on the end faces of the first web 71 and the second web 73, with the webs 71, 73, which are separated from each other by the free space 80, abut the end face of the drive bearing 40 , Also in the embodiment according to FIG. 5 the webs 71 and 73 have the function of bending beams or leaf springs and offer due to the internal friction with respect to the end face of the drive bearing 40 an excellent damping potential.
  • each separate surfaces 86 which abut each other in the circumferential direction spaced apart in receiving grooves 52 of the housing wall 54 of the housing 62 due to the separation.
  • the number of receiving grooves 52 formed in the housing inner wall 54 of the housing 62 advantageously corresponds to the number of supports 50 having either an asymmetrical material weakening 64 or a symmetrical material weakening 70.
  • the representation according to FIG. 6 is another third embodiment of the inventively proposed torque support for a transmission component of a planetary gearbox refer.
  • FIG. 6 shows, at the front side of the cover plate 42 - separated from each other in the circumferential direction - supports 50 are seen, which have a symmetrical material weakening 74, which is formed in this third embodiment as a double slits.
  • the individual supports 50 each have two outer webs 76 and an inner web 78 extending therebetween in the radial direction.
  • the outer webs 76 are separated from the inner web 78 in each case via slots 80.
  • the slot width is smaller compared to the slot width in the case of FIG. 5 illustrated second embodiment with symmetrical slotting 70 of the supports 50.
  • the inventively proposed solution eliminates additional spring elements made of rubber-elastic material.
  • the inventively proposed solution the relaxation of the plastic material from which the cover plate 42 is preferably made by way of plastic injection molding, from.
  • the individual bars, cf. Position 66, 68 in FIG. 4 , Positions 71, 73 in FIG. 5 as well as the positions 76, 78 in FIG. 6 serve as resilient elements, such as leaf springs or bending beam with a very high damping potential, so that momentarily occurring torque loads and their support by way of internal friction on the front side of the drive bearing 40 - to name a few - can be absorbed.
  • FIG. 7 shows a further fourth embodiment of the present invention proposed torque support.
  • FIG. 7 illustrates the supports 50, which are formed in 60 ° division on the front side of the cover plate 42, adjacent to the narrow web 66 a wide web 68, in which a notch-shaped recess 84 extends. About this notch-shaped recess 84 of the wider slot 68 is weakened.
  • FIG. 7 illustrated fourth embodiment of the proposed solution according to the invention also to an asymmetrically formed material weakening 64, with the difference that the wider of the webs 66, 68 has a notch-shaped recess 84.
  • the notch-shaped recess 84 does not extend to the Abstütz vomabitesen 86 at the top of the supports 50.
  • the cover plate 42 comprises a passage opening 82 through which the armature shaft of the starter 10 extends.
  • Reference numeral 88 denotes a shell of the cover plate 42, which is preferably manufactured by means of the plastic injection molding process.
  • Configured supports 50 are formed directly in one operation on the cover plate 42 without the need for further post-processing of the same.
  • FIG. 7 shown fourth variant of the proposed solution according to the invention are located on the front side of the drive bearing 40 facing side of the webs 66, 68, the support surfaces 72 which abut against the end face of the drive bearing 40 and are biased against them.
  • the supports 50 have targeted material weakenings, preferably made of slits, whereby the webs 66, 68, 71, 73, 76, 78 are formed, which act as bending beams or leaf springs. These act under torque stress as damping between the cover plate 42, in which the ring gear 44 is received and the housing 62nd

Claims (12)

  1. Machine électrique, notamment démarreur pour moteurs à combustion interne, comprenant une biellette de suspension (42, 50, 72) pour une roue à denture intérieure (44) en tant que composant d'engrenage d'un engrenage épicycloïdal (20) sur un carter (54, 62), caractérisée en ce qu'au moins une biellette de suspension (42, 50, 72) de configuration symétrique ou asymétrique dans la roue à denture intérieure (44) en une matière plastique possède des affaiblissements de matière (64, 70, 74, 84) intégrés qui absorbent les pointes de charge en utilisant le comportement de relaxation de la matière plastique.
  2. Machine électrique selon la revendication 1, caractérisée en ce que les biellettes de suspension (50, 72) sont réalisées distribuées dans le sens du pourtour sur une plaque de recouvrement (42) et possèdent des nervures (66, 68 ; 71, 73 ; 76, 78).
  3. Machine électrique selon la revendication 2, caractérisée en ce que les nervures (66, 68 ; 71, 73 ; 76, 78) sont séparées les unes des autres.
  4. Machine électrique selon la revendication 2, caractérisée en ce que les nervures (66, 68 ; 71, 73 ; 76, 78) possèdent des surfaces d'appui (72) qui reposent sur le carter (54, 62), notamment au niveau d'une surface frontale du carter.
  5. Machine électrique selon la revendication 2, caractérisée en ce que les nervures (66, 68 ; 71, 73 ; 76, 78), en appui contre le carter (54, 62), agissent comme des ressorts à lame ou des barres de pliage.
  6. Machine électrique selon la revendication 1, caractérisée en ce que le composant d'engrenage (44) est une roue à denture intérieure et l'engrenage épicycloïdal (20) est un engrenage planétaire.
  7. Machine électrique selon la revendication 1, caractérisée en ce que l'affaiblissement de matière symétrique (70, 74) est réalisé sous la forme d'un rainurage simple ou multiple avec au moins deux nervures (66, 68 ; 71, 73 ; 76, 78) et au moins un espace libre (80) se trouvant entre celles-ci.
  8. Machine électrique selon la revendication 1, caractérisée en ce que l'affaiblissement de matière asymétrique (64) possède des nervures (66, 68) de différentes largeurs.
  9. Machine électrique selon la revendication 1, caractérisée en ce que vues dans le sens circonférentiel, la plus étroite des deux nervures (66, 68) est disposée en correspondance au sens de rotation de l'engrenage épicycloïdal (20) et la plus large des deux nervures (66, 68) est disposée en poursuite de la nervure plus étroite (66, 68) en référence au sens de rotation.
  10. Machine électrique selon la revendication 1, caractérisée en ce que les biellettes de suspension (50) possède des portions de surface (86) séparées les unes des autres qui font face à la paroi intérieure du carter (54).
  11. Machine électrique selon la revendication 8, caractérisée en ce qu'un creux (84) en forme d'encoche faisant office d'affaiblissement de matière est pratiqué dans la plus large des nervures (66, 68).
  12. Procédé de fabrication d'une biellette de suspension (42, 50, 72) d'une roue à denture intérieure (44) en tant que composant d'engrenage d'un engrenage épicycloïdal (20) pour une machine électrique, caractérisé en ce que des biellettes de suspension (50, 72) distribuées dans le sens du pourtour sont appliquées par injection sur une plaque de recouvrement (42) fabriquée dans un procédé de moulage par injection de matière plastique, lesquelles comprennent au moins un affaiblissement de matière (64, 70, 74, 84) réalisé intégré de manière symétrique ou asymétrique dans la roue à denture intérieure (44) en matière plastique, les pointes de charge étant absorbées en utilisant le comportement de relaxation de la matière plastique.
EP10709524.2A 2009-03-25 2010-03-18 Moteur électrique à amortissement intégré pour un élément d'engrenage Active EP2411658B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009001835A DE102009001835A1 (de) 2009-03-25 2009-03-25 Elektrische Maschine mit integrierter Dämpfung für eine Getriebekomponente
PCT/EP2010/053544 WO2010108849A1 (fr) 2009-03-25 2010-03-18 Moteur électrique à amortissement intégré pour un élément d'engrenage

Publications (2)

Publication Number Publication Date
EP2411658A1 EP2411658A1 (fr) 2012-02-01
EP2411658B1 true EP2411658B1 (fr) 2017-01-18

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Application Number Title Priority Date Filing Date
EP10709524.2A Active EP2411658B1 (fr) 2009-03-25 2010-03-18 Moteur électrique à amortissement intégré pour un élément d'engrenage

Country Status (7)

Country Link
US (1) US20120083377A1 (fr)
EP (1) EP2411658B1 (fr)
JP (1) JP2012521510A (fr)
CN (1) CN102362065B (fr)
DE (1) DE102009001835A1 (fr)
HU (1) HUE033591T2 (fr)
WO (1) WO2010108849A1 (fr)

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DE102010003431B4 (de) * 2010-03-30 2019-05-16 Seg Automotive Germany Gmbh Startvorrichtung mit Hohlrad- und Zwischenlagerdämpfung
DE102012203490A1 (de) 2012-03-06 2013-09-12 Robert Bosch Gmbh Starter für eine Brennkraftmaschine
CN103485956B (zh) * 2012-06-12 2016-02-10 罗伯特·博世有限公司 用于内燃机的起动装置
DE102012219044A1 (de) * 2012-10-18 2014-04-24 Robert Bosch Gmbh Startvorrichtung für eine Brennkraftmaschine
DE102013207875B4 (de) * 2013-04-30 2021-03-18 Seg Automotive Germany Gmbh Startvorrichtung für eine Brennkraftmaschine
DE102014209315B4 (de) * 2014-05-16 2016-09-01 Robert Bosch Gmbh Startvorrichtung für eine Brennkraftmaschine
DE102016220233A1 (de) 2016-10-17 2018-04-19 Seg Automotive Germany Gmbh Umlaufgetriebe mit integrierter Rutschkupplung für eine elektrische Maschine
KR102565988B1 (ko) * 2021-08-25 2023-08-09 두산에너빌리티 주식회사 배기 디퓨저 시스템 및 이를 포함하는 가스 터빈

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IT1223952B (it) 1988-11-30 1990-09-29 Magneti Marelli Spa Riduttore epicicloidale particolarmente per motorini di avviamento per motori a combustione interna
DE4302854C1 (de) 1993-02-02 1994-06-09 Bosch Gmbh Robert Andrehvorrichtung für Brennkraftmaschinen
EP1094246B1 (fr) * 1999-10-22 2004-06-02 Denso Corporation Amortisseur et dispositif de sécurité anti-surcharge
EP1347171A1 (fr) 2002-03-22 2003-09-24 Valeo Mando Electrical Systems Korea Limited Démarreur équipé d'un dispositif amortisseur de chocs
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US6993989B2 (en) * 2002-04-26 2006-02-07 Denso Corporation Starting apparatus
JP2005098252A (ja) * 2003-09-26 2005-04-14 Denso Corp スタータ
JP4165362B2 (ja) * 2003-10-08 2008-10-15 株式会社デンソー スタータ
FR2902840B1 (fr) * 2006-06-27 2013-03-29 Valeo Equip Electr Moteur Dispositif de demarrage pour moteur thermique
JP2008008225A (ja) * 2006-06-29 2008-01-17 Denso Corp スタータ
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Also Published As

Publication number Publication date
CN102362065B (zh) 2014-07-30
EP2411658A1 (fr) 2012-02-01
WO2010108849A1 (fr) 2010-09-30
CN102362065A (zh) 2012-02-22
HUE033591T2 (hu) 2017-12-28
JP2012521510A (ja) 2012-09-13
US20120083377A1 (en) 2012-04-05
DE102009001835A1 (de) 2010-09-30

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