EP2836385A1 - Engrenage à denture oblique, machine électrique - Google Patents

Engrenage à denture oblique, machine électrique

Info

Publication number
EP2836385A1
EP2836385A1 EP13712561.3A EP13712561A EP2836385A1 EP 2836385 A1 EP2836385 A1 EP 2836385A1 EP 13712561 A EP13712561 A EP 13712561A EP 2836385 A1 EP2836385 A1 EP 2836385A1
Authority
EP
European Patent Office
Prior art keywords
output shaft
helical
pinion
worm wheel
output
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Withdrawn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
EP13712561.3A
Other languages
German (de)
English (en)
Inventor
Martin-Peter Bolz
Lucas Durix
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 EP2836385A1 publication Critical patent/EP2836385A1/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Withdrawn legal-status Critical Current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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/18—Freewheels or freewheel clutches with non-hinged detent
    • F16D41/185—Freewheels or freewheel clutches with non-hinged detent the engaging movement having an axial component
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
    • F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
    • F16D43/2022—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D43/2024—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/04—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type
    • F16D7/042—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement
    • F16D7/044—Slip couplings, e.g. slipping on overload, for absorbing shock of the ratchet type with at least one part moving axially between engagement and disengagement the axially moving part being coaxial with the rotation, e.g. a gear with face teeth
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/081—Structural association with bearings specially adapted for worm gear drives
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/108—Structural association with clutches, brakes, gears, pulleys or mechanical starters with friction clutches
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • H02K7/1163—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion
    • H02K7/1166—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears where at least two gears have non-parallel axes without having orbital motion 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
    • F16H31/00—Other gearings with freewheeling members or other intermittently driving members
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/118—Structural association with clutches, brakes, gears, pulleys or mechanical starters with starting devices
    • H02K7/1185—Structural association with clutches, brakes, gears, pulleys or mechanical starters with starting devices with a mechanical one-way direction control, i.e. with means for reversing the direction of rotation of the rotor

Definitions

  • the invention relates to a helical gear, in particular for an electric machine, with a drive shaft on which a helical gear
  • Drive pinion in particular a worm
  • an output pinion in particular worm wheel
  • the invention relates to an electrical machine, in particular
  • Electric motor for motor vehicles which is a helical gear with a drive shaft on which a helical drive pinion, in particular a worm, is arranged rotationally fixed, and with an output pinion, in particular worm gear, which is arranged on an output shaft and is in engagement with the drive pinion , wherein the drive shaft is formed by a rotor shaft of the electric machine.
  • the rotor shaft is provided on both sides of a rotor core forming a laminated core with bearings, in particular rolling element bearings, which are fixed in the housing of the electric machine.
  • bearings in particular rolling element bearings
  • the end of the rotor shaft is provided with the drive pinion, via which the torque provided by the electric machine is forwarded.
  • a transmission is provided for forwarding the torque, the speed and torque influenced in an advantageous manner.
  • the transmission is often called
  • Worm gear formed. Due to the helical toothing of the Drive pinion and possibly also of the output pinion or of the worm and worm wheel and axial forces are generated which act, inter alia, on the rotor shaft. To absorb these axial forces in the housing usually the drive pinion associated rolling bearing is pressed onto the rotor shaft and the outer ring beschiled in the housing and axially secured or pressed the outer ring of Wälz analyseslagers in the housing and the inner ring on the rotor shaft beschuppeert and axially secured. In some applications, in normal operation, the axial force on the rotor shaft always or mostly in the same direction affects, so that the
  • Storage of the rotor shaft is designed essentially for receiving an axial force (in one direction).
  • the generated axial force can turn around and act in the opposite direction.
  • the storage is charged unfavorably.
  • An embodiment of the storage such that it can absorb axial forces equally in both directions, is possible only with great design effort.
  • the transmission according to the invention with the features of claim 1 has the advantage over the prior art that it is prevented in the event of a fault that an axial force acting in the wrong direction has an effect on the rotor shaft and in particular on its bearing.
  • the output pinion is connected by means of a freewheel device with the output shaft, wherein the freewheel device is formed at least substantially rotationally controlled.
  • the output pinion is thus not directly rotatably connected to the output shaft.
  • a freewheel device is provided between the output shaft and the output pinion, which enables or prevents a transmission of power from the output pinion to the output shaft depending on the direction of rotation or the driving direction and optionally on the transmitted and / or counteracting torque.
  • the freewheel device is designed as a dog clutch.
  • the freewheel device provides a positive transmission of the driving force in a rotational direction, while repealed in a different direction of rotation of the positive connection and thus a power transmission is prevented.
  • the dog clutch requires only a small space and can therefore be well integrated into the transmission.
  • the dog clutch has a first output pinion associated with the clutch element and a second of the output shaft
  • the coupling elements each end face a complementary helical toothing and wherein at least one of the coupling elements is arranged axially displaceable.
  • the complementary helical toothing leads to that described above
  • the first coupling element is formed by the output pinion or by the worm wheel.
  • the first coupling element is insofar formed integrally with the output pinion or with the worm wheel. This integration of the coupling element in the output pinion a particularly compact design of the transmission is offered. Alternatively, it would of course also conceivable, the first coupling element separately from the
  • Coupling element at least rotatably connected to each other.
  • the second coupling element is designed as a coupling ring.
  • the annular design of the second coupling element can be pushed onto the output shaft in a simple manner.
  • the coupling ring is non-rotatably connected to the output shaft. It is provided in particular that the coupling ring has a radially inwardly projecting driving projection, which with a corresponding
  • Coupling ring and the output shaft may be provided. In any case, a positive power transmission is ensured by the coupling ring on the output shaft.
  • the coupling ring is axially displaceable, in particular the disengagement of the
  • the output pinion is arranged axially fixed on the output shaft, but has a
  • Helical toothing of the input pinion and the output pinion does not exert any axial force on the drive shaft, which could have a negative effect on the bearing of the drive shaft.
  • the worm wheel axially displaceable and rotatable and the coupling ring is axially fixed.
  • the coupling ring and the output pinion or worm wheel are spring-loaded with their helical teeth braced against each other.
  • the spring-loaded bracing is used to hold the dog clutch or the freewheel device in positive engagement during normal operation or after a successful change of direction in which the coupling elements were disengaged to ensure that the coupling elements are brought back into engagement with each other.
  • spring loading is preferably at least one spring element, in particular a spring washer, more preferably at least one disc spring or coil spring, is provided, which is preferably held biased between an axial stop on the output shaft and the output pinion or the coupling ring.
  • Axial stop the output shaft is formed in particular by a shoulder, by an increase in diameter of the output shaft
  • a further axial stop is preferably provided, against which the output pinion or the coupling ring is urged by means of the at least one spring element.
  • the second axial stop can be formed for example by a arranged on the output shaft retaining ring, which rests in a circumferential groove of the output shaft.
  • the electric machine according to the invention with the features of claim 10 has the advantage that the bearing of the rotor shaft can be designed to optimize the direction of rotation, since the formation of unfavorable acting axial forces, against the normal direction of action, is reliably prevented. For this purpose, the electric machine to a transmission, as described above. Further embodiments and advantages therefore also result from the previously described.
  • Figure 3 is an exploded view of a freewheel device of
  • FIG. 4 shows another embodiment of the advantageous
  • Figure 5 is an exploded view of the second embodiment.
  • FIG. 1 shows in a simplified longitudinal sectional view of an electric machine 1, which has a rotatably mounted on a rotor shaft 2 rotor 3, wherein the rotor shaft 2 is rotatably mounted in a housing 4.
  • a drive pinion 5 of a not shown in Figure 1 transmission 9 is also provided at its free end, the one
  • Helical toothing 6 has.
  • roller bearing 7 For storage of the rotor shaft 2, two rolling element bearings 7 and 8 are provided.
  • the roller bearing 7 is arranged between the rotor 3 and the drive pinion 6 on the rotor shaft 2, while the roller bearing 8 is provided on the opposite side of the rotor 3.
  • the helical teeth 6 of the drive pinion 5 produced during operation axial forces acting on the rotor shaft 2 and are usually taken up and supported with the rolling element bearing 7.
  • the inner ring of the roller bearing 7 is pressed onto the rotor shaft 2 and the outer ring in the housing 4 shoulders and axially secured, or the outer ring of WälzMechworts 7 is pressed in the housing 4 and the inner ring on the rotor shaft 2 beschbeschert and secured axially.
  • the type of storage is not of further importance. Of importance is only that the type of storage can usually absorb high axial forces in one direction only. Such bearings are particularly suitable for applications in which the electric machine 1 is always operated in the same direction as it
  • Machine lead A storage, which is acted upon in both directions equally with axial forces, would a high constructive and
  • Figure 2 shows an embodiment of the advantageously designed transmission 9, which prevents that axial forces on the storage of
  • the gear 9 is formed as a worm gear 10, wherein the drive pinion 5 of a worm 11 which is non-rotatably mounted on the rotor shaft 2, which acts insofar as the drive shaft 12 is arranged.
  • the worm 11 is in engagement with a worm wheel 13 which is arranged on an output shaft 14.
  • the worm wheel 13 is thus a cooperating with the drive pinion 5 output gear 15.
  • the worm wheel 13 may have on its outer shell side a helical toothing or a straight toothing, which cooperates with the worm 11.
  • the worm wheel is rotatable on the output shaft 14 and axially displaceable, as by a
  • Double arrow 16 indicated, arranged.
  • the freewheel device 17 has a dog clutch 18, which is formed by two coupling elements 19 and 20.
  • the first coupling element 19 is formed integrally with the worm wheel 13 and the second coupling element 20 is formed by a separate coupling ring 21 which is rotatably connected to the output shaft 14 and fixed axially thereon.
  • the coupling ring 21 is on one side on a contact shoulder of the
  • FIG. 3 shows the output-side part of the worm gear 10 for a better understanding in a perspective exploded view.
  • the coupling ring 21 has on its side facing the worm wheel, a helical toothing 26, which is characterized in that the teeth seen in a rotational direction have oblique flanks 27 and in the
  • Helical teeth 26 thus results from the oblique flanks 27 of the teeth.
  • the helical gearing 26 is similar to a Hirth gearing, with the teeth having an oblique flank on one side and a vertical or steep flank on the other side.
  • the worm wheel 13 has on the side facing the coupling ring 21 a recess 29 whose outer diameter exceeds the outer diameter of the coupling ring 21, so that the coupling ring 21 can be completely accommodated in the recess 29.
  • the bottom of the recess 29 is provided with a complementary to the helical teeth 26 helical teeth 30, which is also characterized by teeth with one-sided oblique edges and other side vertical flanks. With the helical gearing 30, the worm wheel 13 itself forms the first coupling element 19, which cooperates with the coupling ring 21.
  • Clutch ring 21 is fixed axially on the output shaft 14 and the
  • Worm wheel 13 by a plurality of disc springs 31, which are supported on a shoulder 32 of the output shaft 14, is urged against the coupling ring 21, as shown in Figure 2.
  • the worm wheel 13 is driven by the worm such that the vertical flanks of the helical gear 30 are urged against the vertical flanks 28 of the helical gear 26.
  • the coupling ring 21 is positively entrained, and by lying in the Mit Spotifyausnaturalung 25 driving projection 24, the force is transmitted to the output shaft 14 so that it is set in rotation. If the direction of rotation of the electric machine 1 is changed, this means that now the oblique flanks of the helical gearing 30 are forced against the oblique flanks 27 of the helical gearing 26.
  • axial forces are generated, which act between the coupling ring 21 and the worm wheel 13 in such a way that they exceed a still transferable
  • FIGS 4 and 5 show another embodiment of the electric machine 1 with the worm gear 10, wherein already known elements are provided with the same reference numerals, so that reference is made to the above description. In the following, essentially only the differences will be discussed.
  • Figure 4 shows the worm gear 10 in a perspective
  • the Mit Spotifyausnaturalung 25 is aligned in this case preferably l jossnutartig parallel to the axis of rotation of the output shaft 14, so that the coupling ring 21 can be moved with the driving projection 24 on the output shaft 14 without entrainment projection 24 and
  • the electric machine 1 described above is particularly suitable to be used as a drive device in brake booster, which usually require a normal drive direction of rotation and not or rarely a drive in the opposite direction with little
  • Torque occurs.
  • the freewheel device 17 a complex and costly storage of the rotor shaft 2 in the housing 4 can be avoided. Since the freewheel device 17 is almost completely integrated in the worm wheel 13, this can be provided without much additional space requirement.
  • the output shaft 14 is connected for example via a connecting rod with a hydraulic piston to be driven, wherein the connecting rod linkage converts the rotational movement of the output shaft 14 in a translational movement of the piston.
  • Disc springs 31 are provided for clamping the jaw clutch 18. Alternatively, it is also conceivable to replace the disc springs 31 by a coil spring. In principle, the number of springs or the adjustable spring force is freely selectable, however, is by the selected spring force the approved
  • Torque of the freewheel device 17 which can still be transmitted in the opposite direction of rotation before the helical gears 26 and disengaged determined.
  • the effect of the freewheel device 17 can thus be adapted in a simple manner.

Landscapes

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

Abstract

L'invention concerne un engrenage à denture oblique (9), en particulier destiné à une machine électrique (1), comprenant un arbre d'entraînement (12) sur lequel un pignon d'entraînement à denture oblique (5), en particulier une vis sans fin (11), est disposée de manière solidaire en rotation, et comprenant un pignon de sortie (15), en particulier une roue à vis sans fin (13), qui est disposée sur un arbre de sortie (14) et en prise avec le pignon d'entraînement (5). Selon l'invention, le pignon de sortie (5) est relié à l'arbre de sortie (14) au moyen d'un système à roue libre (17), ce système à roue libre (17) étant conçu au moins sensiblement pour une commande dans le sens de rotation. L'invention concerne en outre une machine électrique.
EP13712561.3A 2012-04-12 2013-03-27 Engrenage à denture oblique, machine électrique Withdrawn EP2836385A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012205995A DE102012205995A1 (de) 2012-04-12 2012-04-12 Schräg verzahntes Getriebe, elektrische Maschine
PCT/EP2013/056575 WO2013152955A1 (fr) 2012-04-12 2013-03-27 Engrenage à denture oblique, machine électrique

Publications (1)

Publication Number Publication Date
EP2836385A1 true EP2836385A1 (fr) 2015-02-18

Family

ID=47998456

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13712561.3A Withdrawn EP2836385A1 (fr) 2012-04-12 2013-03-27 Engrenage à denture oblique, machine électrique

Country Status (4)

Country Link
EP (1) EP2836385A1 (fr)
CN (1) CN104203626B (fr)
DE (1) DE102012205995A1 (fr)
WO (1) WO2013152955A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105305719A (zh) * 2015-11-24 2016-02-03 王琳 一种蜗杆传动机构
DE102017206641A1 (de) * 2017-04-20 2018-10-25 Bayerische Motoren Werke Aktiengesellschaft Antriebseinheit und Kraftfahrzeug mit einer Antriebseinheit
EP4117863A4 (fr) * 2020-03-13 2024-03-27 Black & Decker, Inc. Collier de serrage de tuyau, dispositif d'actionnement de collier de serrage de tuyau et mécanisme anti-dévirage

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10356976A1 (de) * 2003-02-20 2004-09-16 Dr.Ing.H.C. F. Porsche Ag Drehfallenantrieb eines Schlosses an einem Kraftfahrzeug

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JPH02168832A (ja) * 1988-12-20 1990-06-28 Asmo Co Ltd 歯車減速モータ
JPH04300425A (ja) * 1991-03-27 1992-10-23 Jidosha Denki Kogyo Co Ltd 摩擦クラッチ付小型モータ
DE29611395U1 (de) * 1996-07-01 1997-11-06 Gebr. Bode & Co GmbH, 34123 Kassel Elektromechanische Antriebsvorrichtung für eine Drehsäule zur Bewegung eines Schwenktürflügels an einem Fahrzeug
DE20208246U1 (de) * 2002-05-27 2003-10-09 Kiekert Ag Motor-Getriebe-Antriebseinheit
CN2609267Y (zh) * 2003-03-17 2004-03-31 刘秋雄 复合计步控制及离合驱动的直流马达装置
JP2005206035A (ja) * 2004-01-22 2005-08-04 Mitsuba Corp 車両用自動開閉装置
JP4346638B2 (ja) * 2006-12-01 2009-10-21 株式会社ツバキエマソン 自動車ブレーキスピードテスト用一方向クラッチ内蔵型減速機
US8151718B2 (en) * 2009-05-20 2012-04-10 Deere & Company Adjustable seed meter drive coupling

Patent Citations (1)

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Publication number Priority date Publication date Assignee Title
DE10356976A1 (de) * 2003-02-20 2004-09-16 Dr.Ing.H.C. F. Porsche Ag Drehfallenantrieb eines Schlosses an einem Kraftfahrzeug

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2013152955A1 *

Also Published As

Publication number Publication date
CN104203626A (zh) 2014-12-10
DE102012205995A1 (de) 2013-10-17
CN104203626B (zh) 2017-12-08
WO2013152955A1 (fr) 2013-10-17

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