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EP2334949A1 - Boîtier de différentiel à excentrique - Google Patents

Boîtier de différentiel à excentrique

Info

Publication number
EP2334949A1
EP2334949A1 EP09771480A EP09771480A EP2334949A1 EP 2334949 A1 EP2334949 A1 EP 2334949A1 EP 09771480 A EP09771480 A EP 09771480A EP 09771480 A EP09771480 A EP 09771480A EP 2334949 A1 EP2334949 A1 EP 2334949A1
Authority
EP
European Patent Office
Prior art keywords
output element
output
eccentric gear
gear according
coupling elements
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Withdrawn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
EP09771480A
Other languages
German (de)
English (en)
Inventor
Wolfgang Freund
Andreas Kissler
Jürgen Schulze
Tino Schmidt
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.)
Asturia Automotive Systems AG
Original Assignee
Asturia Automotive Systems 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 Asturia Automotive Systems AG filed Critical Asturia Automotive Systems AG
Publication of EP2334949A1 publication Critical patent/EP2334949A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
    • B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
    • B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
    • B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
    • B60G21/055—Stabiliser bars
    • 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
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load

Definitions

  • the invention relates to a differential eccentric gear according to the preamble of the first claim and is preferably used for the transmission of torque between two relatively rotatable / pivotable elements or for the conversion of relative rotational movements of two elements in an axial movement of a component.
  • a wobble mechanism for a vehicle seat adjustment device in which in a gear housing driven by a drive pinion and connected to a planetary eccentric and connected to an output shaft and standing with the planet gear engaged output ring gear are, wherein the planetary gear in two axially offset planes with the output ring gear engaged with drive wheel and having a housing-fixed support ring gear in engagement standing Abstützrad and the support ring gear is integrated into a connected to the transmission housing gear cover.
  • a hinge fitting for a seat in which a seat associated with the fixed hinge part and the backrest associated pivotable hinge part via a pivot axis with eccentric are connected to each other and a first hinge part has internal teeth on which a part of a wobble mechanism forming external toothing of the second joint part expires.
  • a second, smaller diameter, axially offset internal toothing is provided concentric with the one arranged on the second joint part concentric with the outer toothing, also offset in the axial direction second outer toothing is engaged, wherein the pitch angle of the Gears of each joint part are the same.
  • the second outer toothing is rotatably connected to the first outer toothing.
  • an outer toothing is arranged slightly rotated relative to the other outer toothing and the second outer toothing is mounted on a concentric projection in the center of the first outer toothing. Furthermore, the angle of rotation between the first outer toothing and the second outer toothing is limited by stops.
  • the two solutions mentioned above can not be used for a stabilizer of a vehicle and it is also not possible with these, a relative rotational movement of two To convert components into an axial movement of another element.
  • an electromechanical stabilizer for the chassis of a vehicle, in particular motor vehicle, with an integrated between two stabilizer halves and these if necessary twisting against each other by a twist angle actuator tuator consisting of an electric motor and a downstream of this transmission
  • the transmission has a depending on the angle of rotation changing gear ratio on example, the variable gear ratio having gear can be designed as hypocycloid gear with linear guides or as an eccentric gear.
  • the Hypocycloidgetrie- has a sun gear with a drive shaft and the planet gears have eccentrically arranged bolts and are guided by the ring gear, which is rotatably connected to one of the two stabilizer halves.
  • this hypocycloid gear is rotatably connected, in which as many Gleitstein Entryen are provided as planetary gears are available.
  • a sliding block is mounted, which has a receptacle for a bolt of the associated planetary gear.
  • a sun gear is also provided, the drive shaft of which is optionally connected to the electric motor via the further gear stage with constant gear ratio.
  • the planetary gears have eccentrically arranged bolts, wherein the axes of rotation of the planetary gears are combined to form a journal, which is non-rotatably connected to one of the two stabilizer halves.
  • the output element of this eccentric gear is connected to the other stabilizer half.
  • a sliding block is mounted, which has a receptacle for a bolt of the associated planetary gear. This solution is very expensive and requires a large amount of space.
  • a vehicle height adjustment using two rotors, in which a height adjustment of a spring is realized via a thread in order to realize a leveling of the vehicle is known from DE 10 2007 011 615 A1.
  • This solution requires a high output speed for a relatively small stroke movement.
  • the system works relatively slowly and due to the high friction due to the thread has an unfavorable efficiency.
  • an actuator for actuating two organs by means of tensile forces which has a drivable eccentric shaft and two rotatable about the eccentric shaft arranged ring gears on which suitable traction means for actuating have the organs attached. Furthermore, the actuator has a rotatably mounted on the eccentricity of the eccentric shaft tooth element, which has two toothed zones of different sizes and which mesh with the ring gears. The toothed element is mounted for acoustic decoupling on the eccentric shaft via two angular contact bearings whose radial planes intersect.
  • a driven gear is arranged on the drive side of the eccentric shaft and the other driven gear on the opposite side, wherein both driven wheels are mounted on the eccentric shaft and are driven via the toothed element.
  • a stabilizer arrangement is known from EP 1 627 757A1, but no drive element with different gears is used and no two drives are provided opposite to the drive side.
  • a pivoting motor in which a ring gear is likewise driven by means of an eccentric with two external toothings, describes JP 2007162758 A. However, two opposing outputs rotatable relative to one another are provided.
  • a stabilizer system is also described in US 2008 / 0150241A1.
  • This one has one radially outside seated drive motor with an arranged on the motor shaft gear with external teeth.
  • This drive pinion drives via a plurality of interlocking ring gears with corresponding teeth on two opposite output shafts, which are mounted eccentrically to each other and rotatable relative to each other.
  • the object of the invention is to develop an eccentric differential gear, especially for vehicles, are provided in the two annular output elements which are arranged relative to the drive and relative to each other rotatable in terms of a differential gear and which has a simple structure with low space requirement.
  • the differential eccentric gear has two relatively rotatable output elements, wherein according to the invention a drivable by a drive element wobble having a first longitudinal axis two along the first longitudinal axis successively arranged external teeth and the pitch circle diameter of the first outer toothing is greater than the pitch circle diameter of the second outer toothing and the first External teeth of the wobble wheel, a first output element with a corresponding to the first outer toothing first inner toothing and the second outer toothing of the wobble wheel is assigned a second output element with a second outer toothing corresponding second internal toothing and wherein the first and the second output element on a common second longitudinal axis are rotatably mounted and the first longitudinal axis of the wobble wheel is arranged eccentrically to the second longitudinal axis and by the drive element driven wobble gear partially with its external teeth with the internal teeth of the output elements is engaged and the outer and the inner teeth are designed so that upon rotation of the wobble the first output element and the second output element to perform a relative rotational movement to each other, wherein
  • the wobble wheel, the first output element and the second output element are all rotatable relative to each other. If one of the output elements "held", so that rotates other output element according to the translation faster.
  • the wobble wheel is in particular in the form of a ring gear, engages in the inner diameter of a drive element.
  • the drive element may be, for example, an eccentric shaft or a planet wheel, which is fastened to the rotating drive element and rolls on the inner diameter of the wobble wheel.
  • the drive of the drive element is preferably carried out by an electric drive motor.
  • the first output element is designed in particular in the form of a first ring gear and the second output element in particular in the form of a second ring gear. It is possible to bring the first output element with a first stabilizer part and the second output element with a second stabilizer part of a stabilizer of a vehicle in operative connection, so that in a relative rotation of the two output elements also the two stabilizer halves are rotated relative to each other, thereby compensating for vehicle movements can be.
  • the corresponding drive can be arranged on the side of the first output element or the second output element. It is possible that the first output element is connected to a housing of a stabilizer or forms the housing of a stabilizer, or at the inner diameter of the housing, the first internal toothing is formed.
  • the first stabilizer part is thus fixedly coupled to the housing or formed in the housing.
  • the housing-side end of the second stabilizer part is in this case connected to the second output element.
  • the electric motor sits firmly in the housing. If now the housing and thus the first output element connected to the first stabilizer half rotates relative to the second output element, to which the second stabilizer half is fastened, the two stabilizer halves also rotate relative to one another.
  • the motor can be firmly seated in a housing and the first output element directly connected to the first stabilizer half and the second output element directly to the second stabilizer half.
  • the housing is then secured against rotation on the body.
  • the attached to the output elements of the differential eccentric drive stabilizer halves rotate relative to each other, according to the relative rotation of the output elements.
  • the differential eccentric gear has first coupling elements mounted in an articulated manner on the first output element and second coupling elements articulated on the second output element, wherein the first and second coupling elements have mutually opposing angles of inclination and are hinged at their other ends to the component in such a way that, when the rotational movement of the first and the second output element is relative to one another, the first and the second coupling elements are changed in their angular position and the component thereby performs a lifting movement along the second longitudinal axis of the output elements.
  • the coupling elements are preferably formed in the form of ball bars, which are articulated at both ends.
  • the first and the second bearings lie in a common plane transverse to the second longitudinal axis.
  • the first bearings are arranged on a first larger pitch circle and the second bearings on a second smaller pitch circle.
  • first and the second coupling elements are mounted on the component on a common or on different pitch circles.
  • first coupling elements are arranged on the component on a third pitch circle and the second coupling elements on the component on a fourth pitch circle, wherein the third pitch circle is preferably larger than the fourth pitch circle.
  • the connected to the eccentric differential gear on the coupling elements performs substantially despite a rotational movement of the two output elements only one stroke.
  • the solution can thus be used to generate an axial lifting movement of components.
  • the component can be a spring receptacle of a spring or can be mounted on a spring. ne spring receiving a spring act, whereby the spring receiving is axially adjustable along a spring longitudinal axis.
  • an eccentric differential gear with two output elements which form a differential gear created, which works surprisingly fast and dynamic.
  • By slightly different numbers of teeth of the gear pairs first outer teeth of the wobble and first internal teeth of the first output and second outer teeth of the wobble and second internal teeth of the second output a large gear ratio can be realized, with which high torque can be transmitted.
  • FIG. 3 shows a schematic partial longitudinal section of a stabilizer using a differential eccentric gear
  • FIG. 4 shows a schematic partial longitudinal section of a differential eccentric gearbox using coupling elements for the axial adjustment of a component
  • FIG. 5 shows a top view of a differential eccentric gearbox with a circulation roller as the drive
  • FIG. 6 Section A-A according to FIG. Fig. 5.
  • Fig. 1 the longitudinal section of a differential eccentric is shown. It has a wobble wheel 1 with a first outer toothing z1 and a second outer toothing z2.
  • the pitch circle diameter of the first external toothing z1 is greater than the pitch circle diameter of the second external toothing z2.
  • the wobble wheel 1 has a first longitudinal axis A1 and is driven by drive element, which is designed in the form of an eccentric shaft 2, which engages in the wobble wheel 1.
  • In the here hollow eccentric shaft 2 is a fixed axis 5 for supporting the eccentric shaft 2.
  • the eccentric shaft 2 for example, by an electric drive motor driven and supported by a first bearing L1 on the axis 5 and the wobble wheel 1 via a second bearing L2 on the eccentric shaft 2 from, wherein the first and the second bearing L1, L2 are preferably designed as needle bearings.
  • a first output element 3 (1st output) which is designed in the form of a ring gear and has a first internal toothing z3, which corresponds to the first outer toothing of the wobble wheel 1.
  • the second external toothing z2 of the wobble wheel 1 is assigned a second output element 4 (second output) with a second internal toothing z4 corresponding to the second external toothing z2.
  • the first and the second output element 3, 4 have a common second longitudinal axis A2.
  • the first longitudinal axis A1 of the wobble wheel 1 is offset by an amount a to the second longitudinal axis A2.
  • amount a is the pitch circle diameter of the first outer teeth z1 smaller than the pitch circle diameter of the first outer teeth z3 and the pitch circle diameter of the second outer teeth z2 smaller than the pitch diameter of the second outer teeth z4.
  • the wobble wheel is thereby brought into engagement only partially with its external teeth z1, z2 with the corresponding internal toothings z3, z4 of the two ring gears / output elements 3, 4.
  • the teeth are not engaged on the left side and on the right side partially meshes the first outer teeth z1 with the first internal teeth z3 and the second outer teeth z2 with the second internal teeth z4.
  • the outer and the inner teeth z1 / z3 and z2 / z4 are designed so that upon rotation of the wobble wheel 1, the first output element 3 and the second output element 4 relative to the drive in the form of the eccentric shaft 2 and perform relative to each other a rotational movement .. Will no output element 3, 4 held in a rotationally fixed manner, the rotational speed of the two output elements 3, 4 sets in dependence on the applied torque.
  • the wobble wheel 1 still runs in it and the second output element 4 rotates solely as a function of the transmission ratio which is predetermined by the gear pairings z1 / z3 and z2 / z4.
  • the first output element 3 rotates according to the gear pairings z1 / z3 and z2 / z4, when the second output element 4 is held against rotation.
  • the schematic partial longitudinal section of a differential eccentric is shown in Fig. 2.
  • the drive motor 6 drives the hollow eccentric shaft 2 and thus the wobble wheel 1.
  • the wobble wheel 1 partially engages with its first external toothing z1 in the first internal toothing z3 of the first output element 3 and with its second external toothing z2 partially in the second internal toothing z4 of the second output element 4.
  • the first output element 3 surrounds the second output element 4 and has a mounting flange 7.
  • the schematic partial longitudinal section of a stabilizer using a differential eccentric is shown in Fig. 3.
  • the first output element 3 is formed like a housing and surrounds the drive motor 6 and the entire transmission and is connected to a first stabilizer part 8.1.
  • the second output element 4 is connected to a bushing B, which in turn is firmly connected to the second stabilizer part 8.2.
  • the drive motor 6 is firmly seated in the housing (output element 3).
  • FIG. 4 shows the schematic partial longitudinal section of a differential eccentric with an axially adjustable member 9 using first coupling elements 10.1 in the form of ball bars, which are articulated with their first ends on the first output element 3 with a first (outer) Kalottenring 3.1 and of second coupling elements 10.2 in the form of ball rods which are articulated with their second ends on the second output element 4 with a second (inner) Kalottenring 4.1.
  • the coupling elements 10.1 and the coupling elements 10.2 have opposite inclinations with respect to the longitudinal axis A2.
  • first and second output element 3.4 sits a wobble 1, which is driven by an eccentric shaft 2 by means of the drive motor 6.
  • the first external toothing z1 of the wobble wheel 1 meshes with the first internal toothing z3 of the first output element 3 and the second outer tooth z2 of the wobble wheel 1 with the second internal toothing z4 of the second output element 4.
  • the tooth pairings z1 / z3 and z2 / z4 are axially behind one another, wherein the
  • Pairing z1 / z3 has a larger pitch circle diameter than the pairing z2 / z4.
  • the first output element 3 surrounds the second output element 4, so that the end faces of the output elements lie in the direction of the component 9 approximately in a plane transverse to the longitudinal axis A2 and thus the ball rod ends attached thereto (coupling elements 10.1 and 10.2) also lie in a plane.
  • the other ends of the coupling elements 10.1 and 10.2 are pivotally mounted with their balls on the component 9.
  • the coupling elements 10.1, 10.2 are changed in their angular position, so that the component 9 performs an axial movement when it is rotatably mounted and axially movable.
  • the angle of rotation between the two output elements 3, 4 is determined by the freedom of movement of the ball rods.
  • the component 9 performs an axial movement.
  • the component 9 may for example be a pressure piece for adjusting a spring receptacle of a vehicle spring.
  • FIG. 5 shows the top view and FIG. 6 shows the section A-A according to FIG. Fig. 6 of a differential eccentric with a circulation role as a drive.
  • the wobble wheel 1 is formed as a ring gear. In this engages a drive element 15, which has a circulation roller 16, which rolls on the inner diameter of the wobble wheel 1.
  • the circulation roller 16 is here the outer ring of a ball bearing 17th
  • the longitudinal axis of the drive element 15 is aligned with the second longitudinal axis A2 of the first output element 3 and the second output element 4.
  • the first longitudinal axis A1 of the wobble wheel 1 is arranged eccentrically thereto.
  • the wobble wheel 1 performs a rotary movement and its first longitudinal axis A1 rotates about the second longitudinal axis A2, whereby it partially with its first external teeth z1 in the first internal teeth z3 of the first output element and with its second external teeth z2 in the second internal tooth z4 of the second output element engages.
  • A2 second longitudinal axis a offset between the first and second longitudinal axis A1, A2

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

L'invention concerne un boîtier de différentiel à excentrique comportant deux éléments de sortie (3,4) tournant l'un par rapport à l'autre, une roue oscillante (1) entraînée par un élément d'entraînement (2) comportant deux dentures extérieures (z1, z2) qui sont disposées l'une derrière l'autre et présentent différents diamètres primitifs de référence. A la première denture extérieure (z1) est associé le premier élément de sortie (3) présentant une première denture intérieure (z3) correspondant à la première denture extérieure (z1). A la deuxième denture extérieure (z2) est associé le deuxième élément de sortie (4) présentant une deuxième denture intérieure (43) correspondant à la deuxième denture extérieure (z2). Le premier et le deuxième élément de sortie (3,4) sont montés relativement à l'élément d'entraînement, côté sortie, et pivotent sur un deuxième axe longitudinal (A2) commun qui est disposé de manière excentrique à un premier axe longitudinal (A1) de la roue oscillante (1). Le régime des éléments de sortie (3,4) se règle en fonction du couple de rotation momentané.
EP09771480A 2008-10-19 2009-10-19 Boîtier de différentiel à excentrique Withdrawn EP2334949A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202008013633U DE202008013633U1 (de) 2008-10-19 2008-10-19 Differential-Exzentergetriebe
PCT/DE2009/001481 WO2010043217A1 (fr) 2008-10-19 2009-10-19 Boîtier de différentiel à excentrique

Publications (1)

Publication Number Publication Date
EP2334949A1 true EP2334949A1 (fr) 2011-06-22

Family

ID=41628156

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09771480A Withdrawn EP2334949A1 (fr) 2008-10-19 2009-10-19 Boîtier de différentiel à excentrique

Country Status (8)

Country Link
US (1) US20110190090A1 (fr)
EP (1) EP2334949A1 (fr)
JP (1) JP2012506005A (fr)
KR (1) KR20110086073A (fr)
CN (1) CN102203456A (fr)
DE (2) DE202008013633U1 (fr)
WO (1) WO2010043217A1 (fr)
ZA (1) ZA201102377B (fr)

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DE202010008464U1 (de) * 2010-09-06 2011-12-07 Asturia Automotive Systems Ag Aktuator, insbesondere mit elektromechanischem Antrieb
DE202010008467U1 (de) 2010-09-06 2011-12-07 Asturia Automotive Systems Ag Entkoppelbarer Aktuator, insbesondere mit elektromechanischem Antrieb
DE202011107241U1 (de) * 2011-06-21 2012-11-07 GfA-Gesellschaft für Antriebstechnik Dr.-Ing. Hammann GmbH & Co. KG Rohrmotorantrieb und Excentergetriebe für Rohrmotorantrieb
US9435418B2 (en) 2013-05-08 2016-09-06 Harmonic Drive Systems Inc. Wave generator of strain wave gearing
CN104763785A (zh) * 2014-01-06 2015-07-08 圆和圆科技有限公司 传动轴单元
JP6196588B2 (ja) 2014-07-24 2017-09-13 株式会社スギノマシン 送り台装置、および対象物駆動装置
JP6227496B2 (ja) 2014-07-24 2017-11-08 株式会社スギノマシン 洗浄装置
CN104613134A (zh) * 2015-01-16 2015-05-13 苏州悍猛谐波机电有限公司 同步摆线减速装置
US9927005B2 (en) 2015-08-10 2018-03-27 Southwest Research Institute Two-stage hypocycloidal gear train
JP6609168B2 (ja) * 2015-11-13 2019-11-20 株式会社Ｉｈｉ バルブアクチュエータ
DE102016010700A1 (de) * 2016-09-03 2018-03-08 Sauter Feinmechanik Gmbh Kupplungsvorrichtung
CN109084004A (zh) * 2018-11-01 2018-12-25 明阳科技（苏州）股份有限公司 一种手动或电动铰链
CN113942357B (zh) * 2020-07-17 2024-04-05 广州汽车集团股份有限公司 横向稳定杆总成及车辆

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Also Published As

Publication number Publication date
JP2012506005A (ja) 2012-03-08
KR20110086073A (ko) 2011-07-27
DE102009050032A1 (de) 2010-05-27
CN102203456A (zh) 2011-09-28
WO2010043217A1 (fr) 2010-04-22
ZA201102377B (en) 2011-11-30
DE202008013633U1 (de) 2010-03-18
US20110190090A1 (en) 2011-08-04

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