WO2022179845A1 - Couronne pour un mécanisme de train planétaire - Google Patents

Couronne pour un mécanisme de train planétaire Download PDF

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Publication number
WO2022179845A1
WO2022179845A1 PCT/EP2022/053055 EP2022053055W WO2022179845A1 WO 2022179845 A1 WO2022179845 A1 WO 2022179845A1 EP 2022053055 W EP2022053055 W EP 2022053055W WO 2022179845 A1 WO2022179845 A1 WO 2022179845A1
Authority
WO
WIPO (PCT)
Prior art keywords
sun gear
gear
planetary
axis
inner ring
Prior art date
Application number
PCT/EP2022/053055
Other languages
German (de)
English (en)
Inventor
Johannes Vriesen
Original Assignee
Flender Gmbh
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 Flender Gmbh filed Critical Flender Gmbh
Publication of WO2022179845A1 publication Critical patent/WO2022179845A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a sun gear of a planetary gear bes, a planetary gear with a sun gear and a use of a sun gear, with the help of which a torque can be transmitted, in particular in a wind turbine.
  • Planetary gears which can also be called planetary gears, are used in various areas. Planetary gears can have one gear stage or a large number of gear stages.
  • the diameter of the sun gear shaft in the area of the teeth is necessarily relatively large compared to that of the planet gears.
  • the load-related deformation of the planetary gear carrier can no longer be compensated for, or only to a limited extent, by a similarly large deformation of the sun gear shaft over the torque range in the planet/sun gearing contact.
  • the planetary wheel bearing load is no longer balanced in the two planetary wheel halves over the load range, especially with helical planetary gear stages, such as those used in gearboxes for wind turbines. This problem described can lead to increased wear.
  • DE 102011 075 908 A1 discloses a sun wheel with radially outer running teeth and inner short teeth arranged centrally to the running teeth, the sun nenrad is formed symmetrically to a central axial plane.
  • An input or output shaft for a transmission is known from US 2011/0250070 A1, which has a hollow shaft, a one-piece design with the hollow shaft and a radially outwardly projecting web and a radially outwardly integral annular body connected to the web limited to both Axi almon differently shaped recesses, so that the web can yield elastically under load and allows a self-alignment of a separately executed and connected to the ring body gear with a pinion.
  • An object of the invention is to improve a sun gear or a planetary gear transmission with a sun gear.
  • One aspect of the invention relates to a sun gear for a planetary gear transmission, with an inner ring rotatable about an axis, an outer ring having running teeth and a web connecting the inner ring to the outer ring in one piece, the sun gear having a cross section along an axis intersecting radial plane, through which a load-related deformation is at least partially is equal, the cross-section being asymmetrical with respect to a central axis perpendicular to the axis.
  • the cross section relates in particular to a section through the sun gear, which falls in the axis of the sun gear.
  • the axis of the sun gear is its axis of rotation. This explains, for example, that the sun gear can also be referred to as the sun gear shaft.
  • the cross-section under consideration can in particular be a radial plane running through the axis of rotation, as would result, for example, in a sectional illustration of the sun wheel in a side view viewed in the radial direction.
  • Such an optimized configuration or design of the sun gear enables an increase in the power density of a planetary gear, a planetary gear set or a gear.
  • the cross section relates to a deformation-optimized contour design. Due to the achievable increase in power density, a smaller and lighter gear can be offered for one application, e.g. for wind turbines, which increases the economic efficiency of the wind turbine.
  • the cross section is asymmetrical with respect to a central axis.
  • the central axis does not affect any axis of rotation.
  • the central axis intersects the axis of rotation.
  • the central axis intersects the axis of rotation (rotational axis) perpendicularly, ie essentially at an angle of 90 degrees.
  • the sun gear has a width with respect to its longitudinal extent along the axis of rotation and thus also a center with respect to this width.
  • the central axis goes through this center and is perpendicular to the axis of rotation.
  • the center axis is in particular part of an axial plane running perpendicularly to the radial plane, to which the cross section of the sun wheel is designed asymmetrically.
  • the central axis and/or the axial plane preferably runs through a center of mass of the sun wheel.
  • the web can yield elastically under load, which enables self-alignment of the running gear, preferably designed as helical gearing, with a plurality of planetary gears meshing with a particular fixed ring gear. Due to the comparatively large outer diameter of the sun gear and the particularly high number of planetary carriers of a planetary gear intended for a wind turbine or a planetary gear stage of a planetary gear intended for a wind turbine, it can be ensured that there is sufficient gear engagement between the meshing gear components, even under load preserved. As a result, good toothing engagement in a planetary gear mechanism, provided in particular for a wind power plant, is possible at low cost.
  • the running teeth can be formed from the material of the outer ring, in particular by machining and/or forming a radially outwardly pointing surface of the outer ring.
  • the inner ring can, for example, be fastened to a sun shaft by means of a press fit and/or a tongue and groove connection.
  • the inner ring has short teeth, with de ren help a non-rotatable positive connection with the sun shaft, in particular via a spline, can be entered.
  • the short teeth can be formed by the material of the inner ring, in particular by machining and/or forming a surface area of the inner ring.
  • the entire sun gear can be designed in one piece and have a continuum of material from the running teeth to the inner ring or to the short teeth.
  • the outer ring, the inner ring and the web can be made in one piece from a common, in particular disc-shaped, raw component, in particular by machining. processing and uniforms, for example deep drawing and/or forging.
  • This torsionally softer and/or flexurally softer can be realized by configurations of the sun wheel. This enables better power transmission and less wear.
  • the outer ring has a wall which is directed towards the axis, the wall being in particular conical or curved. From the direction of the wall relates in particular to the surface normal of the wall.
  • the axis is in particular the axis of rotation of the sun wheel.
  • the curved wall is, for example, concavely and/or convexly curved.
  • the wall can for the most part run beveled to an axial direction and merge into the web via a rounded transition.
  • the wall can, for example, run beveled at an angle to the axial direction, in particular 1° ⁇ d 30°, preferably 2° ⁇ 20°, more preferably 3° ⁇ d 15° and particularly preferably 5° ⁇ d 10° .
  • the inner ring has a wall which is directed away from the axis, where the wall is in particular conical or curved.
  • the orientation of the wall relates in particular to the surface normal of the wall.
  • the axis is in particular the axis of rotation of the sun gear.
  • the curved wall is, for example, concavely and/or convexly curved.
  • the wall can for the most part run beveled to an axial direction and merge into the web via a rounded transition.
  • the wall can, for example, be beveled by an angle ⁇ to the axial direction, with in particular 1° ⁇ 30°, preferably 2° ⁇ 20°, more preferably 3° ⁇ 15° and particularly preferably 5° ⁇ 10° applies.
  • the cross section has a conical wall. It is due to the conical wall possible to influence the force curve in the sun gear under load and to make it torsionally or flexibly softer.
  • the web has different widths in the axial direction. Due to the web of different widths, it is possible to influence the course of force in the sun gear under load and to make it torsionally or flexibly softer.
  • the web can in particular assume the shape of a plate.
  • the web can, for example, have a wedge-shaped width profile between the inner ring and the outer ring.
  • the width of the ridge can change continuously with a substantially constant gradient or variable gradient, with a sudden change in the width of the ridge leading to notch effect effects being avoided in particular.
  • the cross section has a c-shape.
  • the c-shape reflects an asymmetrical shape. Due to the C-shape, the force can be transmitted with less torsion or bending. Correspondingly, there are other configurations of the cross section.
  • the cross section has an S-shape.
  • the cross section has a stepped shape.
  • its running teeth and its short teeth are directed radially outwards.
  • a compact design can be implemented.
  • its short toothing is axially offset from its running toothing. This results in an axial course of the power flow. This affects the axis of rotation.
  • the flow of force therefore has a directional component parallel to the axis of rotation.
  • the inner ring and the outer ring are arranged in egg nem common axial area, wherein the web is arranged completely in a common axial area with the inner ring and with the outer ring. Viewed in the radial direction, both the outer ring and the inner ring can completely cover the web. In addition, it is possible for the outer ring to completely cover the inner ring, viewed in the radial direction. This results in a particularly compact design for the sun wheel, which leads to a small installation space requirement.
  • a further aspect relates to a planetary gear, in particular for a wind turbine, with a sun gear which can be designed and developed as described above.
  • the planetary gear train has at least one planetary stage, the planetary stage having a ring gear, in particular a stationary one, the sun gear and a plurality of planetary gears meshing with the ring gear and the sun gear, with at least or exactly five, in particular at least at least or exactly six, preferably at least or exactly seven, more preferably at least or exactly eight and be particularly preferably at least or exactly nine planet gears are provided.
  • the planetary gear has in particular a plurality of planetary stages, with the sun gear adjoining one of the other planetary stages.
  • the sun gear is in particular part of another planetary level.
  • the sun gear is connected to a sun gear shaft, which protrudes into two successively arranged planetary stages.
  • the sun gear has a feather key connection or a shrink fit to the next element of the power transmission instead of short teeth.
  • a further aspect relates to the use of a sun wheel, which can be designed and developed as described above, for transmitting torque in a wind turbine.
  • the sun gear can be used for a planetary gear set with five or more planetary gears, the planetary gears meshing with the sun gear and with a preferably stationary ring gear.
  • FIG. 1 shows, in a partial cross section, a planetary gear 1 or a planetary gear stage (can also be referred to as a planetary gear stage), which is designed according to the invention with respect to a sun gear 5 .
  • a planetary gear set with a housing-fixed ring gear 2 and opposing torque introduction and Rejection to a planetary gear carrier 4 and a sun gear shaft (sun gear for short) 5.
  • the planetary gear 1 has a planetary gear 3, which is carried by a planetary gear carrier 4 (also shown symbolically).
  • the sun wheel 5 is designed differently from a disc wheel.
  • the sun gear 5 has a cross section with a c-shape.
  • Sun gear 5 can thus be designed to be softer in torsion or flexible.
  • the basic body of the sun toothing is contour-optimized below the toothing, so that the deformation can vary across the wheel width.
  • the contour optimization therefore relates to an outer ring 15 which forms a unit via a web 16 with an inner ring 14 .
  • the outer ring 15 shows a conical wall 22.
  • the conical wall 22 results in different heights 24 for the outer ring 15.
  • a load-related deformation of a large sun gear can also be reduced within certain limits by the advantageous use of Geometries compensate for the load-related deformation of a planetary gear carrier and, in the end, with a good design of the microgeometry, the load in the gear meshes and the planetary gear bearing halves are evened out over the torque range of the stage. In particular, this involves a radial load 9 and/or a lateral load 10.
  • the sun wheel 5 has a running gear 6 and a short gear 7 .
  • the outer ring 15 has a first width 11 ßer.
  • the inner ring 14 has a second width 12 .
  • the web 16 has a third width 13 .
  • the maximum width 11 of the outer ring 15 is smaller than the maximum width 12 of the inner ring 14.
  • the maximum width 12 of the inner ring 14 is smaller than the maximum width 13 of the web 16.
  • Figure one also shows an output shaft 21, which engages with the spline is 7.
  • the geometry of the sun wheel 5 is designed in such a way that it has a kind of circumferential trench from a first end face 26, which is formed symmetrically about an axis 8, the axis 8 being the axis of rotation of the drive shaft 21 from.
  • the sun gear 5 has a flat configuration on a second end face 27 . Between Faces 26 and 27 extends the sun gear 5 is ner width. With regard to this width, there is also an imaginary center, in particular an imaginary central axis 29.
  • the central axis 29 is perpendicular to the axis of rotation 8.
  • FIGS. 2 to 5 show other different options for designing a sun wheel 5. Sections of a cross section are shown in each case.
  • the cross section relates in particular to a section through the sun wheel 5 which falls into the axis 8 of the sun wheel 5 .
  • the load distribution in a clutch toothing can also be favorably influenced using the same principle.
  • other forms of sun coupling may also be applicable. Appropriate micro-modifications can increase the effect on gear meshing and clutch gearing.
  • the representation according to FIG. The width 13 of the web 17 mimics radially inwards towards the axis 8 .
  • This shape of the sun gear 5 also enables load-specific bending properties and/or torsional properties.
  • FIG. 3 shows a sun gear 5, the cross section of which has an S-shape.
  • the web 18 is inclined to the axis 8 and has an angle between 25 degrees and 65 degrees to this.
  • FIG. 4 shows a sun gear 5 in which the outer ring 15 is axially offset relative to the inner ring 14 in such a way that running teeth 6 and short teeth 7 do not overlap in the axial direction.
  • the representation according to FIG. sets is that running teeth 6 and short teeth 7 do not overlap in the axial direction. Furthermore, both the running teeth 6 and the short teeth 7' are directed radially outwards. The two toothings are therefore directed in the same direction.
  • the representations of sun gears 5 according to FIGS. 1 to 5 show cross sections of the respective sun gear 5.
  • cross sections that have a mirrored shape of the shape shown can also be realized for the sun gear.
  • the mirrored form or shape of the cross section results, for example, from a mirroring on one of the end faces.
  • a further change in the shape of the cross section of the sun wheel results from a rotation about the respective central axis 29. This results in further possible shapes of cross sections of sun wheels, through which in particular a flexural softness and/or a torsional softness can be influenced.

Abstract

L'invention concerne une couronne (5) pour un mécanisme de train planétaire, comportant une bague interne (14) qui peut être entraînée en rotation autour d'un axe (8), une bague externe (15) présentant une denture d'entraînement (6), et une bande (13) reliant la bague interne (14) à la bague externe (15) en une seule pièce, la couronne (5) présentant une section transversale le long d'un plan radial coupant l'axe (8), à travers laquelle section transversale une déformation induite par charge est au moins partiellement compensée, la section transversale étant asymétrique par rapport à un axe central (29) s'étendant perpendiculairement à l'axe (8). Ceci permet d'obtenir de manière économique un bon engrènement de denture dans un mécanisme de train planétaire prévu en particulier pour une éolienne.
PCT/EP2022/053055 2021-02-26 2022-02-09 Couronne pour un mécanisme de train planétaire WO2022179845A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021201862.9A DE102021201862A1 (de) 2021-02-26 2021-02-26 Sonnenrad eines Planetenradgetriebes
DE102021201862.9 2021-02-26

Publications (1)

Publication Number Publication Date
WO2022179845A1 true WO2022179845A1 (fr) 2022-09-01

Family

ID=80682408

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/053055 WO2022179845A1 (fr) 2021-02-26 2022-02-09 Couronne pour un mécanisme de train planétaire

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DE (1) DE102021201862A1 (fr)
WO (1) WO2022179845A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022113555A1 (de) 2022-05-30 2023-11-30 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Antriebsanordnung

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09310751A (ja) * 1996-05-22 1997-12-02 Sumitomo Metal Ind Ltd 鉄道車両用歯車
EP0875697A2 (fr) * 1997-04-30 1998-11-04 Robert Bosch Gmbh Roue dentée
US20020014133A1 (en) * 2000-07-06 2002-02-07 Genichi Kimizuka Gear made of resin, and mold structure
DE102006012861A1 (de) * 2006-03-21 2007-09-27 Robert Bosch Gmbh Zahnrad
DE102006014997A1 (de) * 2006-03-31 2007-10-04 Robert Bosch Gmbh In Umfangsrichtung gezacktes oder gewelltes Zahnrad
US20110250070A1 (en) 2008-12-10 2011-10-13 Vestas Wind Systems A/S Composite gear part for a gear arrangement and a method of forming a composite gear part
KR20120008614A (ko) * 2010-07-19 2012-02-01 현대자동차주식회사 변속기의 기어 구조
DE102011075908A1 (de) 2011-05-16 2012-11-22 Zf Friedrichshafen Ag Flexibles Sonnenrad
WO2019113325A1 (fr) * 2017-12-06 2019-06-13 S.P.M. Flow Control, Inc. Engrenage de pompe
DE112019000782T5 (de) * 2018-04-11 2020-11-05 Hitachi Automotive Systems, Ltd. Scheibenbremse und planetengetriebeuntersetzungsmechanismus
WO2021019030A1 (fr) * 2019-07-31 2021-02-04 Rolls-Royce Deutschland Ltd & Co Kg Roue dentée

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201113571D0 (en) 2011-08-05 2011-09-21 David Brown Gear Systems Ltd A drive arrangement for a wind turbine
DE102011116427A1 (de) 2011-10-19 2013-04-25 Daimler Ag Stelleinrichtung zum variablen Einstellen wenigstens eines Verdichtungsverhältnisses einer Verbrennungskraftmaschine
DE102017217311A1 (de) 2017-09-28 2019-03-28 Zf Friedrichshafen Ag Zahnrad-Welle-Anordnung für ein Planetengetriebe

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09310751A (ja) * 1996-05-22 1997-12-02 Sumitomo Metal Ind Ltd 鉄道車両用歯車
EP0875697A2 (fr) * 1997-04-30 1998-11-04 Robert Bosch Gmbh Roue dentée
US20020014133A1 (en) * 2000-07-06 2002-02-07 Genichi Kimizuka Gear made of resin, and mold structure
DE102006012861A1 (de) * 2006-03-21 2007-09-27 Robert Bosch Gmbh Zahnrad
DE102006014997A1 (de) * 2006-03-31 2007-10-04 Robert Bosch Gmbh In Umfangsrichtung gezacktes oder gewelltes Zahnrad
US20110250070A1 (en) 2008-12-10 2011-10-13 Vestas Wind Systems A/S Composite gear part for a gear arrangement and a method of forming a composite gear part
KR20120008614A (ko) * 2010-07-19 2012-02-01 현대자동차주식회사 변속기의 기어 구조
DE102011075908A1 (de) 2011-05-16 2012-11-22 Zf Friedrichshafen Ag Flexibles Sonnenrad
WO2019113325A1 (fr) * 2017-12-06 2019-06-13 S.P.M. Flow Control, Inc. Engrenage de pompe
DE112019000782T5 (de) * 2018-04-11 2020-11-05 Hitachi Automotive Systems, Ltd. Scheibenbremse und planetengetriebeuntersetzungsmechanismus
WO2021019030A1 (fr) * 2019-07-31 2021-02-04 Rolls-Royce Deutschland Ltd & Co Kg Roue dentée

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