WO2008019931A1 - Unité de transmission à protection contre les surcharges, et dispositif de réglage - Google Patents

Unité de transmission à protection contre les surcharges, et dispositif de réglage Download PDF

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Publication number
WO2008019931A1
WO2008019931A1 PCT/EP2007/057704 EP2007057704W WO2008019931A1 WO 2008019931 A1 WO2008019931 A1 WO 2008019931A1 EP 2007057704 W EP2007057704 W EP 2007057704W WO 2008019931 A1 WO2008019931 A1 WO 2008019931A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
toothing
axial
gear unit
axial toothing
Prior art date
Application number
PCT/EP2007/057704
Other languages
German (de)
English (en)
Inventor
Stephan Roos
Original Assignee
Siemens Vdo Automotive Ag
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 Siemens Vdo Automotive Ag filed Critical Siemens Vdo Automotive Ag
Publication of WO2008019931A1 publication Critical patent/WO2008019931A1/fr

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
    • 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
    • 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

Definitions

  • the invention relates to a transmission unit with overload ⁇ protection and an adjusting device, in particular a force ⁇ vehicle parking brake.
  • actuators such as the side windows, seat elements or the parking brake with motor vehicle actuators are moved and positioned.
  • Such actuators usually have a gear arrangement and a power-driven drive, usually an electric motor, on. Too high torques or forces in the transmission of power from the drive to the
  • such an actuator can be equipped with an overload protection in the manner of a slip clutch within the transmission.
  • slip-through torque is the same for both directions of rotation, that is, for example, for tightening and releasing a parking brake.
  • slip clutches in the manner of an axial toothing between two cooperating gears, "fixed” and “slip” with aligned gear axes are known, which are arranged on a drive shaft and coupled to each other via a conventional axial teeth.
  • the slip wheel is axially displaceable and rotatably supported relative to the drive shaft and tensioned by a spring element against the fixed gear, whereby the axial toothing is held in engagement with a defined force.
  • the drive or output takes place via a straight-toothed radial toothing of the slip wheel.
  • spur Radialveriereungen lead to increased transmission noise, which are undesirable especially when used in motor vehicles.
  • An object of the present invention is to provide ensurezu- a Getrie ⁇ striking unit with overload protection for an adjusting device, in particular for a motor vehicle parking brake, in which the slip torques for both rotational Rich ⁇ obligations are the same or nearly the same and which is nevertheless much lower gear noise is provided , In this ⁇ transfer is achieved by a gear unit with overload protection according to claim 1 and by a control device with such a gear unit according to claim. 7
  • the transmission unit with overload protection has for this purpose two koaxi ⁇ al arranged in alignment, through a spline set oppel ⁇ te gears, whereby the first gear, the "slip wheel” axially movably disposed, and with the aid of a spring element axially against the second gear, ds "hard ⁇ rad ", is pressed.
  • the axial toothing is Zvi ⁇ rule held the two gear wheels with a defined force against the axial toothing release forces exerted by engaging.
  • the first gear wheel has a helically toothed toothing, via which it is in driving connection with a further gear element (80).
  • the axial toothing (11) has an asymmetric toothing which, depending on the loading direction, generates differently large disengagement forces in the axial direction. Because of the different release forces the resultant of the helical radial toothing axial forces which are added or depending on the loading direction of the gears to the spring force of the spring member subtract, so out ⁇ resembled that in both directions of load, a magnitude of the same size or almost the same size slip ⁇ be moment.
  • the asymmetry of the axial toothing can thus be achieved by a ⁇ slipping torque equal for both directions of rotation, or at least almost the same in spite of the axial forces on the slip wheel.
  • the asymmetry of the axial toothing allows the use of low-noise, helical-toothed radial toothed wheels, wherein the same or almost identical Natural Evolutionmo ⁇ ment can be guaranteed for both directions of rotation.
  • the asymmetry of the axial toothing is preferably represent ⁇ in that the flank angle (angle between a normal to the gear wheel plane and a tooth flank), which magnitude are different in size respectively on a tooth of the axial toothing opposite tooth flanks, wherein the flank angle of the pointing in a first rotational direction tooth flanks the teeth of the axial toothing is greater than the flank angle in the opposite direction of rotation wei ⁇ send tooth flanks.
  • the axial load-relieving forces of the axial toothing on the slip wheel which are generated under load and dependent on the flank angle, are also different depending on the direction of rotation.
  • the larger the flank angle the greater the generated axial force and the smaller the slip torque.
  • flank angle of the axial toothing are chosen so that resulting from the helically toothed radial teeth resulting axial forces, which add or subtract depending on the direction of rotation of the gears to the spring force of the spring element, so balanced that for each direction equal amount or almost equal für Educationmomente guaranteed ⁇ tet are.
  • the flank angle additionally changes with the radius of the axial toothing.
  • the pitch of the tooth flanks changes with the tooth width.
  • the Flankenwin ⁇ angle at the inner diameter so the inside of the axial toothing is comparatively steep / small, while voltage in the direction of outside diameter, say in the direction of the outside of the interlinking ever flatter / increases. In other words, the flank angle increases from the inside to the outside.
  • flank angle which changes with the diameter
  • the course of the tooth heads in particular the course of the tooth bottoms, are each located on a plane which is perpendicular to the gear axis. Since ⁇ is ensured by that the entire tooth head width is up to the attenuation and to the associated slip engaged. If the flank angle were constant over the diameter, the tooth height would grow with increasing diameter. When slipping, the teeth would touch only in a single point and therefore wear relatively quickly.
  • the tooth flanks of the spline set ⁇ are slightly convex, so that the contact point is at a defined diameter, with respect to which the asymmetry of the axial toothing can then be designed.
  • the influence of the load-bearing diameter of the axial toothing on the slip-through torque can also be minimized by reducing the tooth width of the axial toothing.
  • a transmission unit 1 is beschrie ⁇ ben, which serves in a motor vehicle parking brake 100 for over ⁇ tion of a rotational movement of an electric motor 50 on a spindle 60 for actuating a brake cable 70, see
  • the gear unit 1 comprises two cooperating tooth ⁇ wheels 2, 7 21, with aligned gear axes
  • the spindle nut 80 is driven by the first gear 2 of the Zahnradgetrie ⁇ bes 1, see FIG 2.
  • the first gear 2 has the first gear 2 via an obliquely toothed radial toothing 3, which engages in a correspondingly formed counter-toothing of the spindle nut 80.
  • the first gear 2 is on a rigid shaft 4 rotatably supported and is pressed by means of a coil spring 5, which is supported at a point 6 of the shaft 4 against the second gear 7, see Figures 2 and 3.
  • the coil spring 5 is on the shaft 4 by means of two Washers 8 and a securing element 9 mounted.
  • the transmission of the rotational movement of the electric motor 50 from the second (driving) gear 7 to the first (driven) gear 2 via an axial toothings 11 of both gears 2, 7, which engage in the transmission of power, see FIG.
  • the second gear 7 is rotatably connected to the shaft 4, for example, sprayed onto the shaft 4, that is held axially and radially, and is - also via an obliquely ver ⁇ toothed radial teeth 12 - with the aid of another gear member 90 with a corresponding toothing through the Electric motor 50 driven.
  • the second driving gear 7 as well as the first driven gear 2 can be held without rotation on the shaft 4.
  • the second gear 7 instead of a helical gearing ei ⁇ ne spur toothing or any other teeth or have to be configured completely without radial teeth and otherwise powered.
  • the helically toothed radial toothing 3 of the first gear 2 generates axial forces which influence the effect of the spring force of the helical spring 5.
  • these axial forces act with the spring force of the helical spring 5 or against the spring force the coil spring 5 and thus influence the maximum transmissible torque until disengagement of the toothing 11. Act the axial forces against the spring force of ringenfe ⁇ 5, this would cause earlier disengagement of the slip clutch. Act the axial forces with the spring force of the coil spring 5, so higher torques would be transmitted and the slip clutch would slippage later.
  • the slip-through torque of the toothed wheel gear 1 is thus influenced by the spring force of the helical spring 5, the axial forces resulting from the obliquely toothed radial toothing 3 of the first toothed wheel 2, the load-bearing diameter of the axial toothing 11 and friction effects.
  • the second gear 7 has a helically toothed radial toothing 12, of course, also occur on the second gear wheel 7 axial forces. However, this plays no role in the example presented here darge ⁇ , since the second gear 7 is fixedly connected to the shaft 4.
  • the interpretation of the asymmetry of the axial toothing 11 is carried out according to the invention so that the torque difference resulting from the fact that the resulting from the helical Radal ⁇ alveriereung 3 axial force depending on the direction of rotation added to either the spring force of the coil spring 5 or subtracted from this must be balanced.
  • the asymmetry of the axial toothing 11 is provided in order to compensate for the axial forces resulting from the helically toothed radial toothing 3, which add or subtract depending on the direction of rotation of the gears 2, 7 to the spring force.
  • the specific embodiment of the flank angle is thus dependent inter alia on the properties of the radial toothing 3 of the first gear 2. As already shown in FIGS.
  • the axial toothing 11 of the two toothed wheels 2, 7 forming the slip clutch is designed asymmetrically. In detail, this is shown in FIG. This applies to all the teeth 22 of the spline set 11: the facing in a first rotational direction 25 tooth ⁇ edge 23 of a tooth 22 of the axial toothing 11 includes with the perpendicular 27 on the gear circumference (shown here infinitely large) has a flank angle ⁇ and the second in a opposing direction of rotation 26 facing tooth flank 24 of the same tooth has a flank angle ß, wherein the loading ⁇ the angle ⁇ is greater than the amount of the angle ß, (
  • the toothing angle also changes with the diameter of the axial toothing 11.
  • the pitch of the tooth flank 13, ie the flank angle is very steep at the inner diameter 14 of the axial toothing 11, while it is significantly flatter at the outer diameter 15.
  • the axial toothing 11 thus carries on its flank over the entire tooth width 16 equal ⁇ moderately.
  • both the rounded tooth head 17 and the rounded tooth base 18 lie on a plane 19, 19 'perpendicular to the gear axis 21 (see FIG. 6). Until slipping therefore the entire tooth width 16 is engaged.
  • the tooth flanks 13 are designed to be slightly ball-shaped in order to reduce the influence of the (possibly not constant) supporting diameter of the axial toothing 11 on the slipping moment.
  • the tooth flanks 13 are not flat, but have a radius R, so that a rounding of the tooth flanks 13 running from the inner diameter 14 to the outer diameter 15 results.
  • FIG. 7 shows the intermeshing of two tooth flanks 13.
  • the tooth width of the axial toothing 11 can also be reduced overall.

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

Abstract

L'invention concerne une unité de transmission (1) ainsi qu'un dispositif de réglage (100), notamment un frein de stationnement de véhicule automobile. La présente invention a pour objet la mise au point d'une transmission (1) peu bruyante avec deux roues de transmission (2, 7) coopérantes dotées d'axes de roues dentées (21) en alignement. A cet effet, la première roue de transmission (2) est pressée axialement à l'aide d'un élément ressort (5) contre la seconde roue de transmission (7) et est en liaison d'entraînement ou de sortie par le biais d'une denture radiale (3) à flancs obliques avec un élément de transmission (80) suivant, et la seconde roue de transmission (7) est reliée à la première roue de transmission (2) par le biais d'une denture axiale (11) asymétrique de telle sorte que les couples de glissement sont identiques pour les deux sens de rotation.
PCT/EP2007/057704 2006-08-14 2007-07-26 Unité de transmission à protection contre les surcharges, et dispositif de réglage WO2008019931A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610038034 DE102006038034B3 (de) 2006-08-14 2006-08-14 Getriebeeinheit mit Überlastschutz sowie Stelleinrichtung
DE102006038034.7 2006-08-14

Publications (1)

Publication Number Publication Date
WO2008019931A1 true WO2008019931A1 (fr) 2008-02-21

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PCT/EP2007/057704 WO2008019931A1 (fr) 2006-08-14 2007-07-26 Unité de transmission à protection contre les surcharges, et dispositif de réglage

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DE (1) DE102006038034B3 (fr)
WO (1) WO2008019931A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102537257A (zh) * 2010-12-17 2012-07-04 吴舒克 齿轮箱过载保护装置
CN104074883A (zh) * 2014-07-16 2014-10-01 无锡凯绎科技有限公司 机械式电机过载保护装置
WO2018119765A1 (fr) * 2016-12-28 2018-07-05 深圳智慧能源技术有限公司 Engrenage de surface d'extrémité fournissant un effet protecteur d'amortissement et comprenant une précharge
TWI700443B (zh) * 2015-06-30 2020-08-01 日商並木精密寶石股份有限公司 離合器裝置及使用該離合器裝置的電動單元
CN112823077A (zh) * 2018-09-27 2021-05-18 罗伯特·博世有限公司 安全制动设备
WO2022106681A1 (fr) * 2020-11-20 2022-05-27 Valeo Embrayages Dispositif d'entraînement électrique d'un essieu d'un vehicule
WO2022243217A1 (fr) * 2021-05-20 2022-11-24 Liebherr-Components Biberach Gmbh Dispositif d'entraînement et/ou de réglage à protection contre les surcharges
US11725716B1 (en) * 2012-12-12 2023-08-15 Hydro-Gear Limited Partnership Electric actuator for drive apparatus

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017126006A1 (de) 2017-11-07 2019-01-17 Schaeffler Technologies AG & Co. KG Elektromechanische Feststellbremse

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4102014A1 (de) * 1990-03-28 1991-10-02 Licentia Gmbh Handgefuehrte elektrowerkzeugmaschine
DE102004038248B3 (de) * 2004-08-05 2006-03-09 Küster Automotive Control Systems GmbH Elektromotorische Antriebseinheit für eine Feststellbremseinrichtung von Kraftfahrzeugen mit Rutschkupplung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1684233A (en) * 1927-07-16 1928-09-11 Harry A Lewis Differential release transmission
FR1080355A (fr) * 1952-07-05 1954-12-08 United Aircraft Corp Perfectionnements aux démarreurs pneumatiques
US2914929A (en) * 1957-05-20 1959-12-01 Napier & Son Ltd Assemblies including helical splines and coil springs
BE636473A (fr) * 1962-08-24
DE2351240C3 (de) * 1973-10-12 1981-06-19 Robert Bosch Gmbh, 7000 Stuttgart Überlastkupplung

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4102014A1 (de) * 1990-03-28 1991-10-02 Licentia Gmbh Handgefuehrte elektrowerkzeugmaschine
DE102004038248B3 (de) * 2004-08-05 2006-03-09 Küster Automotive Control Systems GmbH Elektromotorische Antriebseinheit für eine Feststellbremseinrichtung von Kraftfahrzeugen mit Rutschkupplung

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102537257A (zh) * 2010-12-17 2012-07-04 吴舒克 齿轮箱过载保护装置
US11725716B1 (en) * 2012-12-12 2023-08-15 Hydro-Gear Limited Partnership Electric actuator for drive apparatus
CN104074883A (zh) * 2014-07-16 2014-10-01 无锡凯绎科技有限公司 机械式电机过载保护装置
TWI700443B (zh) * 2015-06-30 2020-08-01 日商並木精密寶石股份有限公司 離合器裝置及使用該離合器裝置的電動單元
WO2018119765A1 (fr) * 2016-12-28 2018-07-05 深圳智慧能源技术有限公司 Engrenage de surface d'extrémité fournissant un effet protecteur d'amortissement et comprenant une précharge
CN112823077A (zh) * 2018-09-27 2021-05-18 罗伯特·博世有限公司 安全制动设备
WO2022106681A1 (fr) * 2020-11-20 2022-05-27 Valeo Embrayages Dispositif d'entraînement électrique d'un essieu d'un vehicule
FR3116578A1 (fr) * 2020-11-20 2022-05-27 Valeo Embrayages Dispositif d’entraînement électrique d’un essieu d’un véhicule
WO2022243217A1 (fr) * 2021-05-20 2022-11-24 Liebherr-Components Biberach Gmbh Dispositif d'entraînement et/ou de réglage à protection contre les surcharges

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