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WO2017174060A1 - Mécanisme de réglage - Google Patents

Mécanisme de réglage Download PDF

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Publication number
WO2017174060A1
WO2017174060A1 PCT/DE2017/100203 DE2017100203W WO2017174060A1 WO 2017174060 A1 WO2017174060 A1 WO 2017174060A1 DE 2017100203 W DE2017100203 W DE 2017100203W WO 2017174060 A1 WO2017174060 A1 WO 2017174060A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission element
wave generator
outer ring
teeth
flexible transmission
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.)
Ceased
Application number
PCT/DE2017/100203
Other languages
German (de)
English (en)
Inventor
Thomas Nehmeyer
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Priority to CN201780022388.7A priority Critical patent/CN108884923B/zh
Publication of WO2017174060A1 publication Critical patent/WO2017174060A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16H49/00—Other gearings
    • F16H49/001—Wave gearings, e.g. harmonic drive transmissions
    • 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
    • F16H49/00—Other gearings
    • F16H49/001—Wave gearings, e.g. harmonic drive transmissions
    • F16H2049/003—Features of the flexsplines therefor

Definitions

  • the invention relates to a control gear for a motor vehicle with a wave gear, which has a rigid transmission element and a directly cooperating with this, flexible transmission element, wherein a concentric to a rotational axis of the corrugated gear internal teeth of the rigid transmission element meshes with an external toothing of the flexible transmission element and the Deformation of the flexible transmission element, a wave generator is provided, which has a nen NEN outer ring, the radial forces - based on the said axis of rotation - transmits to the flexible transmission element.
  • a wave gear is known, for example, from EP 0 514 829 B1.
  • This wave gear has a cup-shaped flexible transmission element, which is referred to in this case as a deformable toothing part.
  • the called in this case as a stress wave gear wave gear should be suitable for use in robots.
  • a suitable in a motor vehicle wave gear is known for example from DE 10 2014 213 597 A1.
  • the wave gear is part of a camshaft adjuster and at the same time coupled to an auxiliary or auxiliary unit of an internal combustion engine.
  • the subsequently published DE 10 2015 104 135 A1 shows a harmonic drive with a dry run.
  • the wave gear has a bearing outside the projection of the internal teeth of the internal gear perpendicular to the direction of the rotation axis and a contour of the external teeth, which is disengaged in the foot region.
  • DD 244 796 A1 shows a Wellgetnebe with a tooth region whose load deformation is homogenized in that the cup-shaped, elastic wheel has a conical toothing, which reduces the outer diameter of the pot sleeve to the pot edge out.
  • the wave generator the pot sleeve is deformed with the toothing so that a more uniform tooth engagement arises.
  • the preparation of the conical toothing is complex and requires accurate axial positioning of the wave generator.
  • the invention has for its object to further develop a control gear with respect to the cited prior art with respect to a particularly compact, claim-proper structure.
  • the corrugated transmission of the adjusting gear has a per se known basic structure, a rigid in itself gear element, which is provided with an axis of rotation of the corrugated gear concentric internal teeth.
  • the rigid transmission element can be arranged either rotatable or fixed in a surrounding construction.
  • a flexible transmission element cooperates with the inherently rigid, an annular internal teeth having transmission element, wherein an external toothing of this flexible transmission element partially meshes with the internal toothing of the rigid transmission element.
  • the flexible transmission element is permanently deformed, this deformation being accomplished by a wave generator having an outer ring which is arranged flexibly and on the inside of the deformable, externally toothed transmission element.
  • the outer ring of the wave generator in the axial direction, relative to the axis of rotation of the wave gear is opposite the teeth, that is to say both the outer teeth of the flexible gear element. mentes and the internal toothing of the rigid transmission element offset.
  • the mutually meshing toothings of the two mentioned transmission elements protrude in the axial direction beyond the wave generator, at least beyond its outer ring.
  • the invention is based on the consideration that the rigid gear element in the region of its internal toothing has a nearly ideal cylindrical shape.
  • the flexible transmission element also describes a cylindrical shape as long as it is not deformed. Accordingly, the teeth of the two gear elements are perfectly matched to each other, as long as no deformation of the flexible transmission element is given.
  • inherent deformations primarily mean a transition from a circular cross-section of the flexible transmission element to an elliptical cross section. It has been shown that in these deformations, although a slight, but not negligible conicity of the flexible transmission element is formed. This conicity causes the rolling contact between the outer toothing of the flexible transmission element and the internal toothing of the rigid transmission element deviates from the design state. Such deviations could, in principle, be compensated for by modifying the teeth of the rigid and flexible gear element corresponding to the toothings of rotating gear elements whose axes of rotation are not parallel to one another.
  • the already existing flexibility of the resilient, externally toothed transmission element is used to achieve in cooperation with the wave generator an at least approximately ideal rolling contact between the outer toothing of the flexible transmission element on the one hand and the internal toothing of the rigid transmission element on the other.
  • the support of the inside of the flexible transmission element by the wave generator is set away from the toothed region of the flexible transmission element in such a way that the externally toothed region of the flexible transmission element is enclosed. least minimally movable in the radial direction relative to the outer ring of the wave generator, in particular tiltable, is.
  • a common center plane can be laid, which is normal to the axis of rotation of the corrugated transmission and is briefly referred to as the toothing plane.
  • a plane which is set in an analogous manner centrally through the wave generator and which is also normal to the axis of rotation is referred to as the bearing plane.
  • an axial offset measured in the axial direction of the corrugated transmission is provided, which is at least a quarter of the width of the outer ring of the wave generator and less than half the width of the toothings.
  • the widths mentioned, that is outer ring width and tooth width are measured in the axial direction of the wave gear. In the axial direction is in the described embodiment, although an offset, but also an overlap between the outer ring of the wave generator on the one hand and the teeth of the gear elements on the other hand given.
  • the flexible transmission element is preferably cup-shaped. This is followed by a not necessarily closed bottom of a cylindrical, deformable portion of the transmission element, which lies in a plane normal to the axis of rotation of the wave gear. This bottom is connectable to an output member of the wave gear and may be significantly resilient in addition to the cylindrical portion.
  • the external toothing of the flexible transmission element is preferably at the open, the bottom facing away from the end of the cylindrical Ab- Incidentally, while the outer surface of the cylindrical portion is not toothed.
  • the entire flexible transmission element including the external teeth is rationally manufactured as a non-cutting deformable sheet metal part. For the production of the rigid, internally toothed transmission component, in particular chip-removing machining methods come into consideration.
  • the wave generator of the wave gear has a bearing, which can be designed in principle either as a sliding bearing or as a rolling bearing.
  • the outer ring of the wave generator is a bearing ring on which rolling elements roll.
  • the outer ring of the wave generator is designed as a resilient element. If the bearing of the wave generator is designed as a rolling bearing, this can in particular be a ball bearing, for example a single-row deep groove ball bearing. Alternatively, the bearing of the wave generator may be, for example, a needle bearing.
  • the wave gear is part of a control gear of a motor vehicle.
  • this is a transmission for varying the compression ratio of a reciprocating engine.
  • the wave gear is suitable as a control gear in an electric camshaft adjuster an internal combustion engine.
  • Fig. 2 shows a detail of the wave gear with deformed flexible transmission component in excessive representation.
  • a wave gear designated as a whole by the reference numeral 1 is for use in a device for adjusting the compression ratio of a Hubkolbenmotors provided in a motor vehicle.
  • a trained as a ring gear rigid transmission component 2 is in this case firmly connected to a cylinder block of the internal combustion engine.
  • the reference numeral 3 denotes a shaft, namely eccentric shaft, which acts as an output element of the wave gear 1 and cooperates with a secondary connecting rod of the crank mechanism of the internal combustion engine.
  • a toothed region 4 of the wave gear 1 represents a torque-transmitting connection between the rigid transmission component 2 and a flexible transmission component 5.
  • a wave generator 6 For the deformation of the flexible transmission component 5 during operation of the wave gear 1, a wave generator 6 is provided.
  • the axis of rotation of the wave generator 6 is identical to the axis of rotation of the eccentric shaft 3 and thus of the entire wave gear 1.
  • the wave generator 6 has a roller bearing 7, namely ball bearing, which comprises an inner ring 8, an outer ring 9, and between the bearing rings 8, 9 rolling rolling elements 10, namely balls.
  • the inner ring 8 is rigid in itself, while the outer ring 9 is deformable.
  • the inner ring 8 has an elliptical shape, which transmits via the balls 10 to the outer ring 9.
  • the outer ring 9 contacts a designated 1 1 cylindrical portion of the flexible transmission component 5.
  • a bottom 12 of the flexible transmission member 5 connects, which is fixedly connected to the eccentric shaft 3.
  • the flexible transmission component 5 thus has an overall top shape.
  • the corrugated transmission 1 thus represents a highly subordinate actuating gear.
  • the inner ring 8 of the wave generator 6 is driven in a manner not shown by an electric motor.
  • the cylindrical portion 1 1 is thus not radially supported on its end face remote from the bottom 12 from the inside, whereby in this area a specific radial compliance with respect to the outer ring 9 of the wave generator 6 is given. Because of this flexibility, during operation of the wave gear 1, frontal deformations of the cylindrical portion 11, which contribute significantly to the adaptation of the position of the external toothing 13 to the internal toothing 14, occur.
  • VA axial offset between the toothed region 4 and the outer ring 9 and thus the entire wave generator 6.
  • BV is the tooth width, that is, the width of the toothed portion 4 and BL
  • the bearing width that is, the width of the outer ring 9, which is defined as the width of the wave generator 6, respectively.
  • a plane placed centrally through the teeth 13, 14 is designated as a toothing plane EV, a plane centered by the roller bearing 7 of the wave generator 6 and designated EL.
  • the distance between the mutually parallel planes EL and EV corresponds to the axial offset V a .
  • the axial offset V a is less than the tooth width BV and also less than half the bearing width BL.
  • the axial offset V a in the illustrated embodiment is greater than a quarter of the bearing width BL, which corresponds to the width of the outer ring 9.
  • the bearing plane EL is placed centrally through the Wälzköper 10 and cuts the outer teeth 13 of the flexible transmission member 5 and the internal teeth 14 of the rigid transmission component 2.
  • the axial offset V a is less than the Wälz Eisenmesser DW in the present case, but greater than half the rolling element diameter DW, that is, the radius of the balls 10.
  • the measured in the axial direction distance between the bottom 12 of the flexible transmission member 5 and the external teeth 13 of this transmission component is less than the tooth width BV.
  • the distance between the bottom 12 and the bearing rings 8, 9 of the roller bearing 7 measured in the same direction, that is to say along the axis of rotation R, is greater than the tooth width BV.
  • roller bearing 7 of the wave generator 6 is offset from the open front side of the flexible transmission component 5 inwards, that is to the bottom 12, free space is formed on the end face of the flexible transmission component 5 remote from the bottom 12 for drive components of the wave generator 6, in particular electrical drive components, can be used.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

Selon l'invention, un réducteur harmonique comprend un élément d'engrenage (2) rigide en soi, présentant une denture intérieure (14) concentrique par rapport à un axe de rotation (R), et un élément d'engrenage (5) flexible, coopérant avec l'élément d'engrenage rigide, présentant une denture extérieure (13), un générateur d'onde (6) présentant une bague extérieure (9) servant à la déformation de l'élément d'engrenage flexible. La bague extérieure (9) du générateur d'onde (6) est décalée dans le sens axial par rapport aux dentures (13, 14).
PCT/DE2017/100203 2016-04-07 2017-03-14 Mécanisme de réglage Ceased WO2017174060A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201780022388.7A CN108884923B (zh) 2016-04-07 2017-03-14 调节传动装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016205748.0A DE102016205748B3 (de) 2016-04-07 2016-04-07 Stellgetriebe
DE102016205748.0 2016-04-07

Publications (1)

Publication Number Publication Date
WO2017174060A1 true WO2017174060A1 (fr) 2017-10-12

Family

ID=58503554

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2017/100203 Ceased WO2017174060A1 (fr) 2016-04-07 2017-03-14 Mécanisme de réglage

Country Status (3)

Country Link
CN (1) CN108884923B (fr)
DE (1) DE102016205748B3 (fr)
WO (1) WO2017174060A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017125254A1 (de) 2017-10-27 2019-05-02 Schaeffler Technologies AG & Co. KG Vorrichtung zur Verstellung des Verdichtungsverhältnisses eines Hubkolbenmotors
DE102018132400A1 (de) * 2018-12-17 2020-06-18 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Herstellung eines Wellgetriebes
EP4198339A4 (fr) * 2020-10-16 2023-11-22 Midea Group Co., Ltd. Dispositif d'engrenage harmonique et actionneur
DE102020129738B4 (de) 2020-11-11 2025-01-16 Schaeffler Technologies AG & Co. KG Wellgetriebe, Verfahren zur Herstellung eines Wellgetriebes und Brennkraftmaschine mit Wellgetriebe aufweisenden Nockenwellenverstellern
JP7535486B2 (ja) * 2021-10-25 2024-08-16 美的集団股▲フン▼有限公司 波動歯車装置、波動歯車装置の製造方法、ロボット用関節装置及び歯車部品

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60175840A (ja) * 1984-02-22 1985-09-10 Yaskawa Electric Mfg Co Ltd アクチユエ−タ
DD244796A1 (de) 1985-12-23 1987-04-15 Wtz Getriebe & Kupplungen Veb Verzahnung an wellgetrieben, insbesondere mit topffoermigem elastischen rad
EP0514829B1 (fr) 1991-05-20 1996-08-14 Harmonic Drive Systems Inc. Transmisson harmonique avec un élément en forme de coupe court et flexible
EP0741256A1 (fr) 1994-12-14 1996-11-06 Harmonic Drive Systems Inc. Dispositif a engrenage souple du type haut-de-forme
DE19520555A1 (de) * 1995-06-06 1996-12-12 Fickelscher Kurt G Dipl Ing Elastische Steckwellenverbindung für Planetengetriebe mit flexiblem Planetenrad
JP2000055146A (ja) * 1998-08-03 2000-02-22 Fujitsu Ltd ハーモニックドライブ式変速機
JP2000179631A (ja) 1998-12-21 2000-06-27 Harmonic Drive Syst Ind Co Ltd 波動歯車装置
WO2006039825A1 (fr) * 2004-10-16 2006-04-20 Thyssenkrupp Presta Ag Dispositif de superposition de vitesses pour un systeme de direction
DE102014213597A1 (de) 2014-07-14 2016-01-14 Schaeffler Technologies AG & Co. KG Vorrichtung zum Verstellen einer verstellbaren Nockenwelle einer ein Hilfs- oder Nebenaggregat aufweisenden Brennkraftmaschine
DE112013007274T5 (de) 2013-07-25 2016-04-14 Harmonic Drive Systems Inc. Spannungswellengetriebe
DE102015104135A1 (de) 2015-03-19 2016-09-22 Harmonic Drive Ag Wellgetriebe mit Trockenlauf

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2481905Y (zh) * 2001-02-16 2002-03-13 北京中技克美谐波传动有限责任公司 一种带有杯形柔轮的谐波传动装置
CN103827542B (zh) * 2011-09-29 2016-09-21 谐波传动系统有限公司 具有锥形可挠性外齿轮的波动齿轮装置

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60175840A (ja) * 1984-02-22 1985-09-10 Yaskawa Electric Mfg Co Ltd アクチユエ−タ
DD244796A1 (de) 1985-12-23 1987-04-15 Wtz Getriebe & Kupplungen Veb Verzahnung an wellgetrieben, insbesondere mit topffoermigem elastischen rad
EP0514829B1 (fr) 1991-05-20 1996-08-14 Harmonic Drive Systems Inc. Transmisson harmonique avec un élément en forme de coupe court et flexible
EP0741256A1 (fr) 1994-12-14 1996-11-06 Harmonic Drive Systems Inc. Dispositif a engrenage souple du type haut-de-forme
DE19520555A1 (de) * 1995-06-06 1996-12-12 Fickelscher Kurt G Dipl Ing Elastische Steckwellenverbindung für Planetengetriebe mit flexiblem Planetenrad
JP2000055146A (ja) * 1998-08-03 2000-02-22 Fujitsu Ltd ハーモニックドライブ式変速機
JP2000179631A (ja) 1998-12-21 2000-06-27 Harmonic Drive Syst Ind Co Ltd 波動歯車装置
WO2006039825A1 (fr) * 2004-10-16 2006-04-20 Thyssenkrupp Presta Ag Dispositif de superposition de vitesses pour un systeme de direction
DE112013007274T5 (de) 2013-07-25 2016-04-14 Harmonic Drive Systems Inc. Spannungswellengetriebe
DE102014213597A1 (de) 2014-07-14 2016-01-14 Schaeffler Technologies AG & Co. KG Vorrichtung zum Verstellen einer verstellbaren Nockenwelle einer ein Hilfs- oder Nebenaggregat aufweisenden Brennkraftmaschine
DE102015104135A1 (de) 2015-03-19 2016-09-22 Harmonic Drive Ag Wellgetriebe mit Trockenlauf

Also Published As

Publication number Publication date
CN108884923B (zh) 2021-11-05
CN108884923A (zh) 2018-11-23
DE102016205748B3 (de) 2017-07-20

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