EP2834535A1 - Engrenage, machine électrique - Google Patents

Engrenage, machine électrique

Info

Publication number
EP2834535A1
EP2834535A1 EP13712556.3A EP13712556A EP2834535A1 EP 2834535 A1 EP2834535 A1 EP 2834535A1 EP 13712556 A EP13712556 A EP 13712556A EP 2834535 A1 EP2834535 A1 EP 2834535A1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
spring element
housing
spring
transmission according
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.)
Withdrawn
Application number
EP13712556.3A
Other languages
German (de)
English (en)
Inventor
Martin-Peter Bolz
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
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2834535A1 publication Critical patent/EP2834535A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/10—Arrangements or devices for absorbing overload or preventing damage by overload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H2057/0213—Support of worm gear shafts

Definitions

  • the invention relates to a transmission, in particular worm gear, for an electrical machine, with a rotatably mounted in a housing
  • the invention relates to an electric machine with a transmission as described above.
  • the helical drive pinion ensures that at an abrupt stop exert high axial forces on the drive shaft, which can lead to damage to the bearing of the transmission or the drive shaft.
  • the drive pinion in which the drive pinion is in the form of a worm with a worm wheel as the output gear and thereby realizes a high reduction ratio is high speeds are achieved on the drive shaft. Now, if the worm wheel stopped abruptly, for example, because the output side system moves to a mechanical stop, a high rotational energy is stored in the drive shaft.
  • the transmission according to the invention with the features of claim 1 has the advantage that the excess energy initially in an axially acting
  • Component is converted and then axially absorbed by the spring element.
  • the transmission according to the invention a faster stop of the rotational movements of the drive shaft and output shaft is achieved.
  • the spring element is supported on the housing and biases the drive shaft axially. Due to the helical toothing of the drive pinion, the rotational energy is converted into an axially acting on the drive shaft force, which is received by the drive shaft axially biasing spring element at an abrupt stop of the transmission.
  • the drive shaft is associated with at least one movable bearing, which has a rolling element bearing with an inner ring fixed on the drive shaft and with a in the
  • At least one first brake disc and on the housing a second brake disc are respectively fixedly arranged on the drive shaft, that the brake discs come into operative contact with each other when the drive shaft is displaced against the spring force of the spring element over a predetermined path out.
  • the brake discs limit insofar the maximum displacement of the outer ring of the rolling element bearing. Once the thus limited displacement is achieved, the brake discs are urged against each other, which due to the resulting friction effect an optionally existing rotational movement of the drive shaft is braked.
  • the spring element is designed as a plate spring.
  • a plurality of disc springs may be provided to adjust the spring force.
  • Spring element is designed as a spiral spring.
  • the acting spring force is adjusted in particular by the number of Wnditch and by the diameter of the spiral spring forming wire.
  • the coil spring or the plate spring are arranged coaxially to the drive shaft.
  • the spring force of the spring element is chosen so high that in normal operation, a displacement of the drive shaft or the outer ring bearing is prevented is / is and thus a clear
  • Normal operation ensures a conventional operation of the transmission.
  • At least one, in particular annular holding element is arranged on the housing, which axially supports the second brake disc or the second
  • the holding element serves for axial fixing the brake disc so that it is not axially crazy / shifted when the first brake disc is urged against the second brake disc due to a correspondingly high, applied to the drive shaft axial force.
  • the holding element is designed in particular as a support element for the spring element on the housing, so that the spring element is supported on the housing via the holding element.
  • the second brake disc can also be supported by the holding element in this function.
  • the holding element is simultaneously formed as a brake disc, so that reduces the number of components, and assembly time and
  • the brake discs have mutually complementary conical shapes.
  • the surfaces to be brought into frictional contact with each other are formed by the respective cone-shaped portion of the brake discs. This makes it possible, for example, to provide larger friction surfaces on a smaller radial space.
  • the spring element is held biased between the outer ring of the roller bearing and the second brake disc. This is the case in particular, as already mentioned, when the second brake disk is formed by the retaining element. However, it is also conceivable if the brake disc is supported by a separate holding element.
  • the first brake disc is preferably between the inner ring of the
  • the electric machine according to the invention with the features of claim 10 has the advantage that in an abrupt stop, especially on the output side of the transmission, neither the electric machine nor the transmission are damaged by excess energy.
  • the electric machine has a transmission, as has been described above, wherein in particular a rotor shaft of the electric machine forms the drive shaft of the transmission.
  • Figure 1 shows a first embodiment of an advantageous transmission in a sectional view
  • FIG. 1 shows another embodiment of the transmission in one
  • Figure 1 shows a simplified sectional view of a transmission 1, as
  • Worm gear 2 is formed and insofar a worm 3 as a drive pinion 4 has.
  • the worm 3 is in engagement with two worm wheels 5 and 6 arranged opposite one another.
  • the worm 3 is arranged on a drive shaft 7 which forms the rotor shaft of an electric machine 8 which is only indicated here.
  • a drive shaft 7 which forms the rotor shaft of an electric machine 8 which is only indicated here.
  • Rotor 9 arranged, which cooperates with a stationary stator 10.
  • the stator 10 is held stationary in a housing 1 1 of the electric machine 8, which also carries the drive shaft 7 and optionally also the worm wheels 5 and 6.
  • a floating bearing 12 is provided, which is arranged between the worm 3 and the rotor 9 on the drive shaft 7.
  • the floating bearing 12 has a rolling element bearing 13, the inner ring 14 is pressed onto the shaft 7 to an abutment shoulder 15 of the drive shaft 7, wherein for axial securing additionally on the plant shoulder 15 opposite side a locking ring 16 and snap ring is provided.
  • Wälzoresores 13 is axially backlash in the housing 1 1 arranged.
  • the axial displacement of the outer ring 17 is limited by a shoulder 18 of the housing 1 1.
  • a holding element 19 axially spaced from the outer ring 17 is arranged.
  • the holding element 19 is expediently annular and arranged coaxially with the drive shaft 7. Theoretically, the outer ring 17 of the rolling element bearing 13 could be moved to the holding element 19.
  • a spring element 20 and a brake disc 21 are also arranged, wherein the Brake disk 21 bears axially against a holding element 19 and the spring element 20 is held biased between the outer ring 17 and the brake disk 21, so that it urges the outer ring 17 against the shoulder 18.
  • the spring element 20 is supported via the brake disk 21 and the holding element 19 on the housing 1 1.
  • both brake discs 21 and 22 are annular.
  • the outer diameter of the first brake disc 21 and 22 are annular.
  • Brake disc 22 selected larger than the inner diameter of the second
  • the spring force of the spring element 20, which is formed in this case as a plate spring 23, is chosen so high that ensures the normal operation of the transmission 1 and the electric machine 8 a secure mounting of the drive shaft 7 and prevents displacement of the movable bearing 12 or not possible is.
  • Spring element 20 is dimensioned so strong that no displacement of the drive shaft 17 is possible in normal operation. However, if on the output side by the driven by the worm wheels 5 or 6 systems a stop mechanically approached, which causes a sudden stop of the transmission 1, the helical gearing of the worm 3 acts such that by the still present in the drive side part of the transmission 1 rotational energy an axial force is generated, which tries to move the drive shaft 7 axially. If such an emergency is assumed, is in the present
  • the drive shaft 7 is displaced in the direction of the holding member 19 with the rolling element bearing 17, as indicated by an arrow 24.
  • the power flow in this case runs from the worm 3 to the drive shaft 7, from there via the circlip 16 to the inner ring 14 of the roller bearing 13 and then via the rolling elements of the roller bearing 13 on the
  • Brake disks 21, 22 is pushed together increases with each degree which the drive shaft 7 moves further out of its normal position.
  • a heavy load on many components of the transmission 1 on the electric machine 8 in particular on a proposed fixed bearing, which would otherwise be overloaded avoided. Due to the sufficiently high spring force selected, moreover, the electric machine 8 in
  • Worm gear a simple helical gear with two helical gears is provided. Again, in an output side stop an axial force on the drive shaft due to the Helical teeth are exercised.
  • the holding element 19 is formed, for example, as a nut and holds in any case, the brake disc against rotation on the housing 11.
  • the holding element is suitably dimensioned such that it still allows a certain way the brake disc 22 with a high rigidity, without being damaged or destroyed.
  • FIG 2 shows another embodiment of the electric machine 8 with the transmission 1, wherein from Figure 1 already known elements are provided with the same reference numerals and insofar refer to the above description.
  • the holding element 19 forms the brake disc 22.
  • the spring element 20 is also formed in this case as a spiral spring 26 and held directly between the outer ring 17 and the holding member 19 is biased or biased.
  • cone-shaped portion 24 of the brake disc 22 rubs on the inside of the conical portion 25 of the brake disc 21 when the drive shaft 7 has been displaced correspondingly far axially.
  • brake discs 21, 22 can also be configured here in principle as in the first embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)

Abstract

L'invention concerne un engrenage (1), en particulier un engrenage à vis sans fin (2), destiné à une machine électrique (8). Ledit engrenage comprend : un arbre d'entraînement (7) monté de manière à pouvoir tourner dans un carter (11) et sur lequel est agencé fixement un pignon d'entraînement (4) à denture oblique, en particulier une vis sans fin (3) ; et au moins un élément ressort (20) servant à absorber l'énergie excédentaire. Selon l'invention, l'élément ressort prend appui sur le carter (11), et l'arbre d'entraînement (7) est précontraint axialement. L'invention concerne par ailleurs une machine électrique.
EP13712556.3A 2012-04-05 2013-03-27 Engrenage, machine électrique Withdrawn EP2834535A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012205707A DE102012205707A1 (de) 2012-04-05 2012-04-05 Getriebe, elektrische Maschine
PCT/EP2013/056528 WO2013149907A1 (fr) 2012-04-05 2013-03-27 Engrenage, machine électrique

Publications (1)

Publication Number Publication Date
EP2834535A1 true EP2834535A1 (fr) 2015-02-11

Family

ID=47998452

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13712556.3A Withdrawn EP2834535A1 (fr) 2012-04-05 2013-03-27 Engrenage, machine électrique

Country Status (4)

Country Link
EP (1) EP2834535A1 (fr)
CN (1) CN104204608A (fr)
DE (1) DE102012205707A1 (fr)
WO (1) WO2013149907A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6410393B2 (ja) * 2014-07-15 2018-10-24 株式会社ミツバ ワイパモータ
CN104315783A (zh) * 2014-11-04 2015-01-28 镇江市中协电气有限公司 一种直流电机驱动的冰箱电动风门控制装置
DE102019219218A1 (de) 2019-12-10 2021-06-10 Robert Bosch Gmbh Elektrischer Antrieb

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0943842A1 (fr) * 1998-03-19 1999-09-22 Mannesmann VDO Aktiengesellschaft Engrenage à vis sans fin

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4210302C2 (de) * 1992-03-28 1994-11-24 Licentia Gmbh Getriebemotor, insbesondere elektromotorischer Fensterantrieb oder Schiebedachantrieb
DE9311316U1 (de) * 1993-06-19 1993-10-14 IMO - Industrie Momentenlager Stoll & Russ GmbH, 91350 Gremsdorf Anordnung zum Drehantrieb eines Maschinen- und Anlagenteiles und Schneckengetriebe
DE9400232U1 (de) * 1994-01-08 1994-03-03 Rhein-Getriebe GmbH, 40667 Meerbusch Schneckengetriebe
DE19513970C2 (de) * 1995-04-13 1998-07-16 Webasto Karosseriesysteme Vorrichtung zum Antreiben von Schiebedächern, Fensterhebern und dergleichen
US5605071A (en) * 1995-06-06 1997-02-25 Itt Automotive Electrical Systems, Inc. Enveloped worm gear clutch wedgelock responsive to reaction force
JP2902385B2 (ja) * 1997-09-25 1999-06-07 株式会社マキシンコー 電動モ−タ付きウォーム減速機の制動装置
GB9812844D0 (en) * 1998-06-16 1998-08-12 Lucas Ind Plc Improvements relating to electrical power assisted steering
FR2808759B1 (fr) * 2000-05-10 2005-08-26 Koyo Seiko Co Appareil de direction assistee electrique
DE10117811A1 (de) 2001-04-10 2002-10-17 Bosch Gmbh Robert Vorrichtung zum Verstellen eines Teils mit Federdämpfung sowie Verfahren zu dessen Herstellung
FR2824058B3 (fr) * 2001-04-25 2003-06-27 Yavor Pachov Dispositif de freinage de securite d'un organe rotatif
JP3988519B2 (ja) * 2001-06-20 2007-10-10 株式会社ジェイテクト 電動式動力舵取装置
CN201428774Y (zh) * 2009-04-30 2010-03-24 比亚迪股份有限公司 一种蜗轮蜗杆装置
DE102010003727A1 (de) * 2010-04-08 2011-10-13 Zf Lenksysteme Gmbh Lagerung für eine Schnecke in einem Lenkgetriebe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0943842A1 (fr) * 1998-03-19 1999-09-22 Mannesmann VDO Aktiengesellschaft Engrenage à vis sans fin

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2013149907A1 *

Also Published As

Publication number Publication date
CN104204608A (zh) 2014-12-10
DE102012205707A1 (de) 2013-10-10
WO2013149907A1 (fr) 2013-10-10

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