EP3283789A2 - Mécanisme de réglage - Google Patents

Mécanisme de réglage

Info

Publication number
EP3283789A2
EP3283789A2 EP16735983.5A EP16735983A EP3283789A2 EP 3283789 A2 EP3283789 A2 EP 3283789A2 EP 16735983 A EP16735983 A EP 16735983A EP 3283789 A2 EP3283789 A2 EP 3283789A2
Authority
EP
European Patent Office
Prior art keywords
gear
elements
tooth
ring gear
wave generator
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Withdrawn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
EP16735983.5A
Other languages
German (de)
English (en)
Inventor
Jan Klindworth
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to EP20020227.3A priority Critical patent/EP3751174A1/fr
Publication of EP3283789A2 publication Critical patent/EP3283789A2/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Withdrawn legal-status Critical Current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
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/04—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion
    • F16H25/06—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying rotary motion with intermediate members guided along tracks on both rotary members
    • 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 variable speed according to the one piece
  • Gearboxes are known under the brand name "Harmonie Drive”, which are available in two variants: In the first variant, the gearboxes have an internally toothed ring gear, a thin-walled, externally toothed pot and a so-called wave generator, which is also technically referred to as a wave generator.
  • the second variant of the Harmonic Drive transmission consists of a
  • Wave generator a toothed belt with an external toothing, and two ring gears with a number of teeth difference of two.
  • Gear band is ovalized by the wave generator and then pushed into the two ring gears. This gear is narrower than the first variant, but has a worse tooth contact between the
  • the eccentric element can move the toothed segments very well into the ring gear teeth.
  • gearboxes are used here for adjusting.
  • gears used are particularly torsionally stiff and play as little as possible. This is important to be able to move robots quickly and accurately.
  • gearboxes are often used here according to the principle disclosed in DE 2 143 493 A1. It is a modification of the Cyclogetriebes. While the Cyclogetriebe of a Eccentric shaft is driven, there is the transmission according to DE 2 143 493
  • A1 two, three or more eccentric waves.
  • the eccentric waves are
  • the object of the invention according to independent claims 1 and 6 is to provide a transmission, compared to the prior art
  • a driving pin in contact and which are in contact with the teeth and with a ring gear and then supported on the Wave generator.
  • the toothed element is symmetrical and that the contact surface is arranged in the middle and that the teeth are arranged both to the left and to the right of the contact surface.
  • Tooth element arranged. Since the toothed element is supported against the driving wheel on its driving pin when the ring gear rotates, the toothed element pivots about a positional pole varying in position which lies between the lines of action of the forces acting on the teeth. Because the instantaneous pole lies between the lines of action of these forces, the force which is introduced by the wave generator into the toothed element can be a pure normal force.
  • the toothed elements, which transmit the force for rotating these two wheels against each other in the power flow between the ring gear and the driving wheel, are clamped between the ring gear, the respective associated driving pin and the wave generator.
  • the tooth elements are connected by connecting elements.
  • Connecting elements can be used to return the toothed element during the return stroke of the wave generator.
  • the wave generator consists of an inner part, a sleeve, the cylindrical rollers, the bearing cage and the outer sleeve.
  • the wave generator is a wave generator with rolling bearings.
  • the cylindrical rollers and roller bearing balls can be provided.
  • the toothed elements do not transmit any torques.
  • Tooth elements transmit pure forces.
  • the adjusting mechanism has a substantially rigid ring gear with an internal toothing, an elastic spur gear and a wave generator, with the toothed elements of the spur gear being displaceable transversely to a central gear axis such that an external toothing in the direction from the central gear axis Moved away tooth element can be brought into engagement with the internal toothing, so that the ring gear is rotatable relative to the elastic spur gear around the central axis in a rotational direction, wherein the spur gear entrains a Mitauerrad, which in the direction of rotation by means of several driver body to tooth elements of
  • Gear central axis radially outer end portions of the tooth elements are arranged. Such an arrangement at the outer end makes it possible for the toothed elements, during operation of the adjusting mechanism, to pivot about a position-varying instantaneous pole which remains between the lines of action of forces which lie between the external toothing of the toothed element and the internal toothing of the ring gear in the direction of a further instantaneous pole.
  • This further instantaneous pole is the instantaneous pole between the ring gear and the respectively considered tooth element of the elastic spur gear.
  • Tooth elements optimized embodiment is provided that the recesses in the direction that points away from the transmission center axis, open. As a result, the recesses are open in the direction of the internal toothing, so that the
  • Mitschharma can be arranged very close to the internal toothing. This has the advantage that the forces due to the torque transmission between Ring gear and Mit supportiverad load the tooth elements exclusively at the radially outer end portions on which the teeth of the external teeth are arranged.
  • the respective recess is at least mitbeordinate by a contact surface, so depending on the direction of rotation of the spur gear relative to the ring gear either one of a direction of rotation associated contact area of the contact surface or an opposite direction of rotation associated contact area of the contact surface with the driver body can come in contact, but never both contact areas at the same time.
  • the recesses each open on the end face of the toothed element, which faces away from the central axis of the gear.
  • the respective recess is mitbergic of two webs, on both sides of a
  • each web has at least one tooth, preferably a plurality of teeth, the outer toothing, wherein the tooth elements when rotating the ring gear relative to the Mitauerrad
  • the adjacent tooth elements are connected to each other by means of a leaf spring-shaped connecting element, which causes a restoring force in the direction of the wave generator.
  • the more speed-resistant is the adjusting mechanism. If the wave generator carries out a stroke and accelerates the tooth elements radially outwards, the leaf spring-like connecting elements hold the tooth elements in contact with the tooth elements
  • Wave generator or its outer ring
  • the connecting elements can be screwed to the toothed elements, for example.
  • the connecting elements in a plane perpendicular to the central axis of the transmission have a multi-corrugated profile that is mirror-symmetrical to another level, the
  • the spur gear has a one-piece spur gear part
  • the Stirnradteil is made of a material which is in particular plastic, sintered metal or powder injection molded metal.
  • this spur also has inserts that are not made of plastic.
  • Such inserts may be provided, for example, to reinforce highly loaded parts of the spur gear. Consequently, the inserts can be made of a particularly wear-resistant, low-friction or impact-resistant material.
  • the inserts can be made of metal.
  • the Mit Committeerad has two discs which are interconnected by means of the driver body, wherein one of the two discs has a central recess through which engages a drive member of the wave generator.
  • the Mitauerrad forms a kind of cage for the spur gear.
  • the driver bodies each have an end face pointing away from the central axis of the transmission, which is formed so convexly that there is a between the
  • FIG. 1 shows an adjusting mechanism which is perpendicular to a plane in a plane
  • FIG. 2 shows a detail from FIG. 1 in the region of a tooth element
  • Embodiment of the variable transmission which is a spur gear made of plastic
  • FIG. 5 shows a detail from FIG. 2
  • Figure 6 shows an alternative embodiment of the toothed element
  • Figure 7 shows another embodiment of the tooth element.
  • FIG. 1 shows an adjusting mechanism, which is shown cut in a plane perpendicular to a transmission central axis 10.
  • FIG. 1 shows a view of the main components of the transmission.
  • a ring gear 1 a Mitauerrad 2, a flexible spur gear 3 and a wave generator 4, which is also referred to below as the wave generator 4.
  • Wave generator 4 are arranged coaxially with each other, so that the central transmission axis 10 is formed.
  • the adjusting gear thus has three gear members, of which
  • the first gear member is formed by an inner part 4a of the wave generator 4,
  • the third gear member is formed by the ring gear 1.
  • the substantially rigid ring gear 1 is the respect to the
  • the flexible spur gear 3 consists of individual toothed elements 3a and of individual connecting elements 3b. It is made around, and
  • Spur gear 3 is either by powder metallurgy injection molding
  • recesses 12 are made by water jet cutting.
  • the spur gear 3 has a one-piece spur gear part 14, which connects the tooth elements 3a respectively with two webs 16, 18, a region 20 connecting the two webs 16, 18 of the respective tooth element 3a,
  • the wave generator 4 is designed in the manner of a roller bearing, wherein the rolling elements are cylindrical rollers 4b, but may also be designed as balls or tons.
  • the wave generator 4 consists of the inner part 4a, of a sleeve 4e, of the cylindrical rollers 4b, an outer sleeve 4c and a bearing cage 4d.
  • the inner part 4a has an elliptical, or an ellipse-like, outer contour 22 and is the drive element of this transmission. Due to the elliptical shape ensures that each of the
  • Tooth elements 3a two strokes and two return strokes per revolution of the
  • Inner part 4a performs.
  • the wave generator 4 may also have a different shape.
  • the inner part of the wave generator 4 is driven by a drive member and deforms via the rolling elements, the flexible spur gear 3, which is in the opposite relative to the central transmission axis 10 areas with an internal toothing 26 in engagement.
  • the outer sleeve 4c does not rotate relative to the Mit supportiverad 2, since the outer sleeve 4c is pressed against the respective tooth element 3a with a force FW apparent from Fig. 2, so that between the tooth elements 3a and the outer sleeve 4c, a stiction occurs, whereas the outer sleeve 4c is roller-mounted relative to the inner part 4a of the wave generator 4 by means of the rolling bodies.
  • alternative embodiment can be dispensed with a cage 4d. Both in the alternative cage 4d and in the alternative cage 4d no play, a small game or a large game can be provided between the rolling elements or between the rolling element and the cage 4d.
  • An external toothing 24 of the spur gear 3 does not have the same tooth pitch even then as the internal toothing 26 of the ring gear 1, if the
  • Tooth pitch as the internal teeth 26. This lacks the external teeth a half tooth per 90 ° compared to the internal toothing. With respect to a complete revolution of the spur gear 3 relative to the ring gear 1, the spur gear 3 thus lacks two teeth. After each revolution of the inner part 4a, the ring gear 1 relative to the spur gear 3 has an angular difference corresponding to two teeth. Whether the spur gear 3 leads or lags the ring gear 1 depends on whether the inner part 4 a rotates in one direction of rotation 28 or the opposite direction of rotation 30.
  • Mit Helpbolzen 2a can also be in one piece by sintering or
  • the Ring gear 1, the Mit Economicsrad 2 and the wave generator 4 then rotate concentrically.
  • the Mit supportiverad 2 is supported in the direction of rotation 28 by means of several of the driving pins 2a on the toothed element 3a of the elastic spur gear 2.
  • the driving pins 2a may also have a different shape from the partially cylindrical shape, the
  • each toothed element 3a is associated in each case with a driver body 2a, which engages in the recess 12 of the toothed element 3a assigned to it.
  • the respective driver body 2a is received with circumferential clearance in its associated recess 12.
  • the recesses 12 are arranged at the radially outer end regions 38 (FIG. 1) of the tooth elements 3 a relative to the central transmission axis 10.
  • the recesses 12 open out respectively at the end face 31 of the tooth element, which faces away from the central axis 10 of the gear.
  • this recess 12 is shown in detail view according to Figure 2 and Figure 5, which shows only one toothed element 3a completely, which will be explained in more detail below, the remaining tooth elements 3a are executed in the same way.
  • the single toothed element 3a or a detail of the toothed element 3a is shown. It is symmetrical about the Z-line. In the middle is in the upper part of the contact surface 3c, with the Carrier pin 2a is in contact. Then there are teeth 3d on the left side of the Z line and teeth 3e on the right side.
  • the recesses 12 are mitigiated radially outwardly by a portion of the internal toothing 26 of the ring gear 1.
  • the recess 12 is also through the
  • the driver bodies 2a each have one of the central transmission axis
  • Carrier body 2a is supported when the ring gear 1 in the one direction of rotation
  • Rotation direction 30 is rotated, as the right side of the contact surface 3c
  • Ring gear 1 are guided on the toothed element 3a. Then there is the force FM, which is guided by the driving pin 2a on the tooth element 3a.
  • the wave generator 4 then directs the force FW to the tooth element 3a.
  • the force FW is a pure normal force, at the point P2 there are none
  • the resulting transverse forces and torques support the toothed element 3a on the ring gear 1.
  • the point P1 is the instantaneous pole of the toothed element 3a between the driving pin 2a and the wave generator 4. Because the point P1 lies between the lines of action of the FL forces and the FR forces, the force FW is a pure normal force.
  • the FL forces and the FR forces divide as a function of the distance to the point P1 and in total form a total force that gives rise to the output torque.
  • the toothed element 3a is thus only in contact with the driving wheel 2 at one point, and the connecting elements 3b do not transmit load-dependent torques.
  • This gear is therefore a
  • the recess 12 is mitbe friendship of the contact surface 3c, respectively of the two webs 16,18.
  • the webs 16, 18 are arranged on both sides of a plane of symmetry of the toothed element 3a, that of the Z-line and the transmission central axis 10 is clamped.
  • Each web 16, 18 has three teeth of the external toothing 24.
  • Pusher 2 slightly pivots about the instantaneous center P1, slide the tooth flanks of the external teeth 24 slightly on the tooth flanks of the internal teeth 26 from.
  • the teeth of the teeth 24, 26 have for this purpose a non-standard free-form surface, wherein the internal toothing 26 of the ring gear 1 has convex tooth flanks and the external toothing 24 of the
  • Tooth element 3a has concave tooth flanks.
  • the internal teeth 26 of the ring gear 1 has concave tooth flanks, whereas the
  • External teeth 24 of the toothed element 3a has convex tooth flanks.
  • Tooth element 3a assigned point P2 on the lateral surface of the outer sleeve 4c of the wave generator 4 is on the way of the return stroke.
  • the point P2 lies at the interface between the tooth element 3a and the outer sleeve 4c.
  • FIG. 3 shows an alternative embodiment variant of an adjusting gear, in which the spur gear part 14 is made of plastic, in particular by injection molding.
  • the spur gear part 14 is made of plastic, in particular by injection molding.
  • a flexible spur gear 3 has a one-piece spur gear part 14, which
  • Webs 16, 18, a the two webs 16, 18 of the respective tooth element 3a connecting region 20, an applied to the wave generator 4 investment piece 21 and leaf spring-shaped connecting elements 3b comprises.
  • the wave generator 4 is as a disk
  • the connecting elements 3b are formed and contains no rolling elements.
  • FIG. 4 is an exploded view of that shown in FIG.
  • the Mit Sprint 21 is formed as a cage.
  • the cover 2b has the shape of a disk, just like a main body 2d of the driving wheel.
  • the Mit supportiverad 2 has two discs 2b, 2d, which are interconnected by means of the driver body 2a, wherein the one of the two discs 2b, 2d has a central recess 61 through which a drive 62 for the wave generator 4 engages.
  • FIG. 6 shows an alternative embodiment of the toothed element. This is
  • Reference numeral 103a designated toothed element is preferably
  • FIG. 7 shows a further embodiment of the toothed element.
  • the toothed element 203a has a shape that is different from the above
  • driver body 202a has a different one
  • the driver body 202a has a bore 250 which
  • Bore 250 may be threaded, into which a screw
  • the leaf spring-shaped connecting element 203b has analogous to
  • Embodiment according to Figure 6 a cup-shaped profile on that, however
  • the corrugated profile is mirror-symmetrical to another plane 47 or 147 and 247, the
  • the spur gear 3 shown in Figure 4 is mainly plastic to replace the spur gear 3 shown in Figure 1 and 2 of metal to to come to a perspective detailed view of the variable transmission according to Figures 1, 2 and 5.
  • the inner part 4a of the wave generator 4 can each input and output elements in different
  • each of the twenty tooth elements 3a a total of six teeth, so that from the calculation
  • the said 120 teeth of the spur gear 3 result.
  • the tooth gap 27 on the respective tooth element 3a six teeth are missing on the outer toothing 24 of each tooth element 3a, so that the spur gear 3 has approximately, but not exactly, half as many teeth as the ring gear 1.
  • the ring gear 1 has two more teeth, as the double number of teeth of the spur gear 3, since a difference is necessary to one Gear ratio not equal to one produce.
  • the ring gear 1 at least one more tooth than the spur gear 3, since in this case the
  • the wave generator 4 has an ellipse shape, so that two humps 51, 59 are formed, whereby two partial transmissions 48, 50 are formed. The two
  • Partial gear 48, 50 are on opposite sides of a
  • Adjusting gear arranged in a bisecting plane 36 which is the
  • Central transmission axis 10 includes. Each partial transmission 48, 50 goes through one cycle, so that each toothed element 3a is moved one half turn of the inner part 4a relative to the ring gear 1 by one tooth.
  • the wave generator 4 could also have three humps distributed uniformly around the circumference.
  • the adjusting gear also has three partial transmissions.
  • the ring gear 1 rotates when considered standing standing Mitauerrad 2 in the same direction as the driven Inner part 4a.
  • the ring gear 1 rotates when considered as standing Mitauerrad 2 in the direction of rotation 28 and 30, the direction of rotation 30 and 28 of the driven inner part 4a
  • the adjusting gear has a relatively poor efficiency, for example, compared to conventional planetary gears, as
  • Ring gear 1 are adjusted relative to the driving wheel 2. In this case
  • Wave generator is with a drive motor, for example
  • Inner part 4a driven by the drive motor or rotated about the transmission central axis 10, so can be an extreme reduction
  • Ring gear 1 are implemented relative to the Mitschrad 2, wherein
  • variable speed gear is used to high speed of a drive motor with low torque in one
  • Gear member is the output shaft, whereas the inner part of
  • Such transmission can, for example, for the seat adjustment of Automobiles used to drive robot arms or other parts of a robot.
  • a gear member instead of holding a gear member, of course, a gear member or it can be braked two gear members. In this case, an output torque is split between the two braked gear elements.
  • two, three, four or five teeth are arranged on the respective web of the tooth elements. But it is also possible to provide only one tooth per bridge.
  • Wave generator or Wave Generatora inner part

Landscapes

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

Abstract

L'invention concerne un mécanisme de réglage, destiné à régler deux composants, comprenant une couronne dentée (1), une roue d'entraînement (2), un générateur d'ondes (4) et un pignon droit élastique (3) qui se compose de plusieurs éléments dentés (3a) qui sont en contact par la surface de contact (3c) avec une broche d'entraînement (2a) et qui sont en contact par les dents (3e) et (3d) avec une couronne dentée (1) et qui s'appuie sur le générateur d'ondes.
EP16735983.5A 2015-04-11 2016-04-10 Mécanisme de réglage Withdrawn EP3283789A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20020227.3A EP3751174A1 (fr) 2015-04-11 2016-04-10 Mécanisme de réglage

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015004405.2A DE102015004405A1 (de) 2015-04-11 2015-04-11 Verstellgetriebe
PCT/DE2016/000155 WO2016165684A2 (fr) 2015-04-11 2016-04-10 Mécanisme de réglage

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP20020227.3A Division EP3751174A1 (fr) 2015-04-11 2016-04-10 Mécanisme de réglage

Publications (1)

Publication Number Publication Date
EP3283789A2 true EP3283789A2 (fr) 2018-02-21

Family

ID=56368740

Family Applications (2)

Application Number Title Priority Date Filing Date
EP20020227.3A Withdrawn EP3751174A1 (fr) 2015-04-11 2016-04-10 Mécanisme de réglage
EP16735983.5A Withdrawn EP3283789A2 (fr) 2015-04-11 2016-04-10 Mécanisme de réglage

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP20020227.3A Withdrawn EP3751174A1 (fr) 2015-04-11 2016-04-10 Mécanisme de réglage

Country Status (3)

Country Link
EP (2) EP3751174A1 (fr)
DE (2) DE102015004405A1 (fr)
WO (1) WO2016165684A2 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109473083B (zh) * 2018-11-27 2023-12-19 河南科技大学 一种少齿差行星齿轮传动的琴弦微调机构
EP3779239B1 (fr) 2019-08-13 2021-08-11 maxon international ag Engrenage à grande démultiplication
EP3828442A1 (fr) 2019-11-26 2021-06-02 Maxon International AG Roue dentée souple et boîte de vitesses dotée d'une telle roue dentée souple
DE102020002965A1 (de) 2020-05-18 2021-11-18 Jan Klindworth Stellgetriebe
DE102020132794A1 (de) * 2020-12-09 2022-06-09 Wittenstein Se Koaxialgetriebe
DE102021004124A1 (de) 2021-08-11 2023-02-16 Jan Klindworth Stellgetriebe und Wellgenerator für ein Stellgetriebe
DE102024108025A1 (de) 2024-03-20 2024-05-16 Jan Klindworth Stellgetriebe und Verfahren zur Bestimmung einer Innenkontur eines Zahnelements eines Stellgetriebes
DE202024101745U1 (de) 2024-03-20 2024-05-25 Jan Klindworth Stellgetriebe

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE214393C (fr)
GB153982A (en) 1919-08-27 1920-11-25 Walter Charles Pitter Improvements in transmission gearing
DE2143493A1 (de) 1971-08-31 1973-03-08 Konrad Grebe Untersetzungsgetriebe
DE10010156C1 (de) 2000-03-04 2001-10-31 Oechsler Ag Wellgetriebe und Innenrad für ein solches Getriebe
DE10247207A1 (de) 2002-10-10 2004-04-22 Jan Klindworth Fahrzeugsitz
DE102006042786B4 (de) 2006-09-08 2008-09-11 Wittenstein Ag Hohlwellengetriebe
DE102009024418A1 (de) 2009-06-09 2010-12-16 Klindworth, Jan, Dipl.-Ing. Exzenterverstellgetriebe zum Verstellen zweier Bauteile
DE102012102802B4 (de) 2012-03-30 2016-07-07 Wittenstein Ag Getriebe
DE102013110015A1 (de) 2013-09-12 2015-03-12 Jan Klindworth Nockenwellenversteller

Also Published As

Publication number Publication date
EP3751174A1 (fr) 2020-12-16
DE202016009022U1 (de) 2021-10-20
WO2016165684A2 (fr) 2016-10-20
WO2016165684A3 (fr) 2016-12-08
DE102015004405A1 (de) 2016-10-13

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