WO2017194045A1 - Réducteur elliptique - Google Patents

Réducteur elliptique Download PDF

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Publication number
WO2017194045A1
WO2017194045A1 PCT/DE2017/100258 DE2017100258W WO2017194045A1 WO 2017194045 A1 WO2017194045 A1 WO 2017194045A1 DE 2017100258 W DE2017100258 W DE 2017100258W WO 2017194045 A1 WO2017194045 A1 WO 2017194045A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission element
output
wave gear
gear
outer part
Prior art date
Application number
PCT/DE2017/100258
Other languages
German (de)
English (en)
Inventor
Resat Aras
Rainer Ottersbach
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to DE112017002364.5T priority Critical patent/DE112017002364A5/de
Publication of WO2017194045A1 publication Critical patent/WO2017194045A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/352—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using bevel or epicyclic gear
    • F01L2001/3521—Harmonic drive of flexspline type

Definitions

  • the invention relates to a suitable as a control gear, in particular in a motor vehicle, suitable wave gear, which has at least on the output side a rigid internally toothed transmission element whose internal teeth mesh with a toothing of a flexible, externally toothed transmission element.
  • Such a wave gear is known, for example, from DE 10 2014 210 360 A1. This is a component of a camshaft adjusting device.
  • Another electric camshaft adjuster is for example from the
  • drive and output components are nested radially to achieve a narrow structure.
  • DE 10 2008 053 915 A1 shows a camshaft adjuster with a corrugated transmission, in which the dimensionally stable transmission elements are brought into a defined distance from each other during assembly. For this purpose, a contact of the dimensionally stable transmission elements is accepted, with the surfaces that come into contact acting as sliding surfaces. This allows a Aufblockmontage.
  • Wave gear works inherently work with a component, for example in the form of a flex ring, a Flextopfes, or a collar sleeve, which is subjected to permanent deformation during operation of the wave gear.
  • the stress of this component can be decisive for the performance and service life of a corrugated transmission.
  • the invention has for its object to provide a comparison with the cited prior art further developed wave gear, which is characterized by a special ders favorable ratio between mechanical load capacity, even under exceptional operating conditions, space requirements and manufacturing costs.
  • This corrugated transmission includes in a known per se basic structure a driven side internally toothed transmission element, optionally also a drive side internally toothed transmission element, wherein the at least one internal toothing of this transmission element or these two transmission elements mesh with the teeth of a single resilient, externally toothed transmission element or mesh.
  • the flexible transmission element including its outer toothing, is permanently deformed by a wave generator which is arranged radially inside this transmission element, at least within its outer toothing.
  • the output-side internal gear element is constructed in several parts, namely divided into a driven inner part and an output outer part, wherein the coupling between the output inner part and the output outer part forms an overload protection.
  • the output inner part and the output outer part thus act together as a single transmission component, namely as the output element of the corrugated transmission. If this torque limit is exceeded, then the drive inner part can rotate temporarily with respect to the output outer part. From this slippage of the output shaft part relative to the output outer part at a torque peak takes neither the drive inner part and the output outer part divided output-side internally toothed transmission element still another component of the harmonic drive damage. In particular, torque peaks are kept away from the resilient, externally toothed transmission element in this way.
  • the internal toothing of the drive-side transmission element is formed directly by the output drive part.
  • the overload protection against torque overload which is formed by the output shaft part and output outer part, can be designed in principle as a latching overload clutch.
  • a given detent position in which the output shaft part is coupled to the output outer part, leave until re-latching takes place in a changed angular relation between the output shaft part and the output outer part.
  • the function of an overload protection can be realized by a press fit between the output shaft part and the output outer part. After slipping between the output inner part and the output outer part as a result of mechanical overload, the new torque transmission between the output inner part and the output outer part, that is, the transition to the normal operation of the corrugated transmission, facilitated by the wave generator permanently radial forces on the arrangement of the resilient, externally toothed gear element and the internal gear elements are applied.
  • the present in the form of interference fit contact surface between the Abtriebs- inner part and the output outer part is preferably arranged radially outside of the resilient, externally toothed transmission element.
  • the measured in the axial direction of the internally toothed transmission element and thus the entire wave transmission width of the contact surface between the output inner part and the output outer part is preferably less than the measured in the same direction width of the compliant, externally toothed transmission element.
  • an internal toothing output shaft portion preferably has a ring shape
  • the output outer part is preferably designed cup-shaped.
  • a drive-side internally toothed transmission element is provided according to a possible embodiment, wherein the internal teeth of these two transmission elements mesh with the same external toothing of the compliant transmission element and this flexible transmission element is designed as a flex ring.
  • this preferably has a smaller outer diameter than the drive-side internally toothed transmission element in this embodiment.
  • the resilient, externally toothed gear element is designed as a collar sleeve and secured to a housing of the wave gear.
  • a housing of the wave gear On this housing is preferably, if the housing is designed as a whole as a rotating part, which may be the case with the previously discussed embodiment with flex ring, a toothing provided which drives the housing via a chain or belt drive or a gear drive allows.
  • the resilient, internally toothed gear element has a pot shape, wherein the bottom of the flexible, cup-shaped gear element is not necessarily closed.
  • the bottom of the pot-shaped gear element can be directly or indirectly connected to an output shaft of the wave gear, for example an eccentric shaft.
  • the harmonic drive is suitable for stationary applications, for example in machine tools or in industrial robots, as well as for applications in vehicles.
  • the wave gear may be a control gear of an electric camshaft adjuster or a device for varying the compression ratio of a reciprocating engine.
  • the drive inner part and the drive outer part are made of different materials.
  • one of the Sintered components and the other of a steel, for example Kaltumformtechnisch be prepared.
  • FIG. 2 shows a detail from FIG. 1 including intermeshing toothings
  • FIG. 4 shows another wave gear in a sectional view analogous to FIG. 1.
  • a generally designated by the reference numeral 1 wave gear is part of an electric camshaft adjuster, with respect to its principal function is made to the cited prior art.
  • a housing 2 of the wave gear 1 is rotatable as a whole about an axis of rotation designated R.
  • a toothing 3 located on the circumference of the housing 2 serves to drive the housing 2 by means of a traction means, not shown, namely a toothed belt or a chain.
  • the traction means is from the crankshaft of a Piston engine driven.
  • the housing 2 for example, via gears driven.
  • Reference numeral 4 designates a driven-side internal gear element - in short: output ring gear - of the harmonic drive 1.
  • the internal teeth of the output ring gear 4 meshes with an external toothing of a flexible transmission element 5, namely flex rings.
  • a wave generator 6 is provided for the deformation of the flex ring 5 during operation of the wave gear 1.
  • the wave generator 6 operates with a rolling bearing 7, namely ball bearings.
  • Components of the rolling bearing 7 are an inner ring 8, an outer ring 9, and a plurality of rolling elements 10, namely balls.
  • the inner ring 6 has a non-circular, namely elliptical, outer contour, and is rigid in itself, the outer ring 9 is designed as a resilient element.
  • the wave generator 6 is driven by an electric motor, not shown, via an adjusting shaft.
  • the shape of the outer ring 9 permanently adapts to the elliptical shape of the inner ring 8.
  • the flexible transmission element 5 immediately surrounds the outer ring 9 without being firmly connected thereto.
  • the outer toothing of the flexible transmission element 5, which is denoted by 1 1 engages at two diametrically opposite points in the inner toothing of the output ring gear 4 designated by 13.
  • the external teeth 1 1 engages in an internal toothing 12 of a drive ring gear 14, which is firmly connected to the housing 2 and is generally referred to as a drive-side internally toothed gear element.
  • a slightly different number of teeth of the teeth 1 1, 12, 13 ensures that at a full rotation of the inner ring 8, the output ring gear 4 is slightly rotated relative to the drive ring gear 14 and thus with respect to the housing 2.
  • the teeth 1 1 and 13 of the flexible transmission element 5 and the output hollow 4 form a transmission stage of the wave gear 1, wherein the number of teeth of the external teeth 1 1 is two less than the number of teeth of the internal teeth 13.
  • the drive ring gear 14 is secured by means of screws 15 and a lid 16 on the housing 2 and projects in the radial direction beyond the output ring gear 4 addition.
  • the output ring gear 4 is composed of a downforce portion 17 and an output outer portion 18, wherein the internal teeth 13 of the output ring gear 4 is formed directly by the output shaft portion 17. While the output shaft part 17 has the shape of a ring, the output outer part 18 describes a pot shape. With the output outer part 18, a stop disc 19 is connected, which in turn is rotatably coupled to a designated camshaft 20.
  • the course of a force flow K from the toothing 3 of the housing 2 to the camshaft 20 is illustrated in FIG. 1 by a line. In this case, it can be clearly seen that the force flow K passes, inter alia, through a cylindrical contact surface between the output drive part 17 and the output outer part 18, which is also provided in the exemplary embodiment according to FIG. 4.
  • the inherently rigid shape of the internal toothing 13 of the output ring gear 4 is achieved not only by the output inner part 17, but completely only by the interference fit between the output inner part 17 and the output outer part 18. As long as a torque transmitted from the flexible transmission element 5 to the output ring gear 4 does not exceed a limit value, the interference fit between the output shaft part 17 and the output outer part 18 is maintained, so that the entire output driving ring gear 4 acts as a single, inherently rigid transmission part. When exceeding this torque limit, the output shaft part 17 slips over the output outer part 18, whereby an overload protection of the wave gear 1 is given.
  • the flexible, externally toothed transmission element 5 is designed as a collar sleeve, which is fastened to the housing 2.
  • a lid 22 can be seen, which the corrugated transmission 1 end face, namely on that end face on which the transmission element 5 is screwed to the housing 2, closes.
  • the wave generator instead of a roller bearing has a sliding bearing 21.
  • an inner ring 8 directly contacts the resilient transmission element 5, so that the sliding contact is formed directly between the inner ring 8 and the flexible transmission element 5.
  • the inner ring 8 is elliptical in the embodiment of FIG. 4.
  • the slide bearing 21 is provided by a roller bearing 7, as in the design Fig. 1 is present, replaceable.
  • the rolling bearing 7 by a sliding bearing 21, as it is available in the wave gear 1 of FIG. 4, replaceable.

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

Abstract

L'invention concerne un réducteur elliptique (1), en particulier pour un déphaseur d'arbre à cames électrique, qui comprend au moins, côté sortie, un élément de réducteur à denture intérieure (4), ainsi qu'un élément de réducteur (5) à denture extérieure, flexible, engrenant avec l'élément de réducteur à denture intérieure (4). L'élément de réducteur (4) cité en dernier est divisé en une partie intérieure de sortie (17) et une partie extérieure de sortie (18), qui forment ensemble une protection contre la surcharge.
PCT/DE2017/100258 2016-05-09 2017-04-04 Réducteur elliptique WO2017194045A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112017002364.5T DE112017002364A5 (de) 2016-05-09 2017-04-04 Wellgetriebe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016207930.1 2016-05-09
DE102016207930.1A DE102016207930B3 (de) 2016-05-09 2016-05-09 Wellgetriebe

Publications (1)

Publication Number Publication Date
WO2017194045A1 true WO2017194045A1 (fr) 2017-11-16

Family

ID=58669548

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2017/100258 WO2017194045A1 (fr) 2016-05-09 2017-04-04 Réducteur elliptique

Country Status (2)

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DE (2) DE102016207930B3 (fr)
WO (1) WO2017194045A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019185088A1 (fr) * 2018-03-26 2019-10-03 Schaeffler Technologies AG & Co. KG Engrenage à ondes de déformation
DE102019109131A1 (de) * 2019-04-08 2020-10-08 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Herstellung eines Wellgetriebes
DE102019116653A1 (de) * 2019-06-19 2020-12-17 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Montage eines Wellgetriebes
CN113242930A (zh) * 2019-02-08 2021-08-10 舍弗勒技术股份两合公司 凸轮轴调节系统以及操作凸轮轴调节系统的方法

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017121320B3 (de) 2017-09-14 2018-10-11 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102017125254A1 (de) 2017-10-27 2019-05-02 Schaeffler Technologies AG & Co. KG Vorrichtung zur Verstellung des Verdichtungsverhältnisses eines Hubkolbenmotors
DE102018101138B4 (de) 2018-01-19 2020-03-26 Schaeffler Technologies AG & Co. KG Lagerring eines Wellgenerators und Verfahren zur Herstellung eines Lagerrings
DE102018126439A1 (de) 2018-10-24 2020-04-30 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Montage eines Wellgetriebes
DE102018129521B3 (de) * 2018-11-23 2020-03-19 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102019101107B4 (de) 2019-01-16 2024-05-16 Schaeffler Technologies AG & Co. KG Wellgetriebe

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004005795A1 (de) * 2004-02-06 2005-08-25 Daimlerchrysler Ag Vorrichtung zur Winkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102004009128A1 (de) 2004-02-25 2005-09-15 Ina-Schaeffler Kg Elektrischer Nockenwellenversteller
DE102008050826A1 (de) * 2008-10-08 2010-04-15 Schaeffler Kg Verstellvorrichtung zur Lageveränderung einer in Exzenterbuchsen gelagerten Kurbelwelle eines Verbrennungsmotors
DE102008053915A1 (de) 2008-10-30 2010-05-06 Ovalo Gmbh Spannungswellengetriebe und Vorrichtung zum Überlagern von Bewegungen
DE102008053913A1 (de) * 2008-10-30 2010-05-12 Ovalo Gmbh Lageranordnung zur Lagerung des Wellengenerators eines Spannungswellengetriebes, Spannungswellengetriebe sowie Vorrichtung zum Überlagern von Bewegungen
DE102014201981A1 (de) * 2014-02-04 2015-08-06 Ovalo Gmbh Anordnung zum Antreiben einer Verstellwelle zum Verstellen des Expansionshubes und/oder des Verdichtungsverhältnisses eines Verbrennungsmotors
DE102014210360A1 (de) 2014-06-02 2015-12-03 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004005795A1 (de) * 2004-02-06 2005-08-25 Daimlerchrysler Ag Vorrichtung zur Winkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102004009128A1 (de) 2004-02-25 2005-09-15 Ina-Schaeffler Kg Elektrischer Nockenwellenversteller
DE102008050826A1 (de) * 2008-10-08 2010-04-15 Schaeffler Kg Verstellvorrichtung zur Lageveränderung einer in Exzenterbuchsen gelagerten Kurbelwelle eines Verbrennungsmotors
DE102008053915A1 (de) 2008-10-30 2010-05-06 Ovalo Gmbh Spannungswellengetriebe und Vorrichtung zum Überlagern von Bewegungen
DE102008053913A1 (de) * 2008-10-30 2010-05-12 Ovalo Gmbh Lageranordnung zur Lagerung des Wellengenerators eines Spannungswellengetriebes, Spannungswellengetriebe sowie Vorrichtung zum Überlagern von Bewegungen
DE102014201981A1 (de) * 2014-02-04 2015-08-06 Ovalo Gmbh Anordnung zum Antreiben einer Verstellwelle zum Verstellen des Expansionshubes und/oder des Verdichtungsverhältnisses eines Verbrennungsmotors
DE102014210360A1 (de) 2014-06-02 2015-12-03 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019185088A1 (fr) * 2018-03-26 2019-10-03 Schaeffler Technologies AG & Co. KG Engrenage à ondes de déformation
CN113242930A (zh) * 2019-02-08 2021-08-10 舍弗勒技术股份两合公司 凸轮轴调节系统以及操作凸轮轴调节系统的方法
DE102019109131A1 (de) * 2019-04-08 2020-10-08 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Herstellung eines Wellgetriebes
DE102019116653A1 (de) * 2019-06-19 2020-12-17 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Montage eines Wellgetriebes
WO2020253906A1 (fr) 2019-06-19 2020-12-24 Schaeffler Technologies AG & Co. KG Réducteur harmonique et procédé pour le montage d'un réducteur harmonique

Also Published As

Publication number Publication date
DE102016207930B3 (de) 2017-08-10
DE112017002364A5 (de) 2019-01-24

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