WO2019115202A1 - Étage de train planétaire muni d'un système de palier lisse, en particulier pour un logement de pignon satellite dans une transmission d'éolienne - Google Patents

Étage de train planétaire muni d'un système de palier lisse, en particulier pour un logement de pignon satellite dans une transmission d'éolienne Download PDF

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Publication number
WO2019115202A1
WO2019115202A1 PCT/EP2018/082284 EP2018082284W WO2019115202A1 WO 2019115202 A1 WO2019115202 A1 WO 2019115202A1 EP 2018082284 W EP2018082284 W EP 2018082284W WO 2019115202 A1 WO2019115202 A1 WO 2019115202A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
planetary gear
gear stage
conical
stage according
Prior art date
Application number
PCT/EP2018/082284
Other languages
German (de)
English (en)
Inventor
Maarten OOMS
Koen Krieckemans
Roger Bogaert
Original Assignee
Zf Friedrichshafen Ag
Zf Wind Power Antwerpen N.V.
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 Zf Friedrichshafen Ag, Zf Wind Power Antwerpen N.V. filed Critical Zf Friedrichshafen Ag
Publication of WO2019115202A1 publication Critical patent/WO2019115202A1/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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0479—Gears or bearings on planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears
    • 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 planetary gear stage, in particular for a wind power transmission of a wind turbine, comprising a sliding bearing arrangement for the planetary gear within the planetary gear, comprising at least three Planetenradwellen, on each of which at least one planet gear is rotatably supported by the sliding bearing assembly, which is mounted on the respective Planetenradwelle bearing bushing unit for Combined axial and radial bearing of the planetary gear has.
  • wind turbine transmissions usually include at least one planetary gear stage for the translation of a gear input side generated by a windbeetzschlagten rotor rotational movement in rapid to drive the output side to drive an electric generator for generating electrical energy.
  • the bearings of such transmissions such as the planet carrier bearing, the Sonnenradwellenlagerung and in particular the Planetenradlagerung, may be equipped with bearings or plain bearings.
  • the bearing takes place via a lubricating oil film produced between a stationary component and a component rotating relative thereto, which is maintained in operation via a transmission-internal lubricating oil supply.
  • the above-mentioned Planetenradlagerung is charged because of the most helical planet gears both in the radial direction and in the axial direction and therefore to store.
  • a generic planetary gear stage with a slide bearing arrangement which ensures both a radial bearing and an axial bearing of the planetary gears.
  • the slide bearing arrangement has a radial contact surface and on both sides adjacent axial contact surfaces.
  • two bearing sleeves are provided, which are fixedly connected to the Planetenradwelle.
  • Each bearing sleeve has an L-shaped cross-section and has the above-mentioned radial contact surface as well the axial contact surfaces.
  • the L-shaped bearing sleeves form a U-shaped cross-section in the mounted state. In the axial direction, the bearing clearance is blocked by double-sided attacks.
  • a part of the planetary gear is located within the U-shaped cross section, which is formed by the bearing sleeves.
  • a radial slide carrier consisting of plain bearing material is arranged between the radial contact surface of the stationary, L-shaped bearing sleeves and the radial contact surface of the planetary gear.
  • an existing also plain bearing material axial slide between the axial contact surface of the fixed L-shaped bearing sleeves and the axial contact surface of the planet gear is arranged. In this slide bearing assembly, a precise production of the L-shaped sleeves is required to ensure the most constant possible lubricant film thickness.
  • the bearing bush unit for combined axial and radial bearing comprises a pair of tapered bearing rings, each having a cylindrical inner surface and an outer surface inclined thereto, the inner surface attached to the Planetenradwelle or at least one of them inner plain bearing bush comes into abutment, whereas the outer surface cooperates with a bearing surface corresponding thereto formed on the part of the planetary gear or a similar component to form a sliding bearing.
  • the advantage of the solution according to the invention lies in the fact that, in contrast to the prior art, in which a total of three bearing surfaces for the combined axial and radial bearings are used in the interest here special application of a Planetenradlagerung only two beveled from each other arranged bearing surfaces part of the standing Component and - opposite - be used by the relatively rotating component. Due to the conical bearing rings used in the bearing bushing unit according to the invention, the deformations occurring during operation can be functionally compensated within the planetary gear stage. In particular, this applies to the complex loads that arise in a wind turbine by the forces and moments introduced by the rotor into the wind turbine gearbox. As a result, the wear is minimized and the sliding bearing assembly according to the invention consequently has a longer service life, in contrast to the prior art.
  • the conical bearing ring to form the bearing bush unit according to the invention has a triangular cross-section.
  • This is not based on the strict geometric shape of a triangle. Rather, rounding in the edge region thereof are also included.
  • the triangular cross-section also includes geometric shapes in which acute-angled end portions of the cross-section are truncated so that, strictly speaking, this results in a polygonal cross-sectional geometry.
  • two conical bearing rings are joined together with their acute-angled side, so that this forms an O-arrangement for the sliding bearing assembly.
  • the slide bearing assembly can be realized with or without floating plain bearing bushing.
  • the two conical bearing rings are in principle back-to-back positioned to each other and form so far an X-arrangement for the sliding bearing assembly.
  • a design with or without floating plain bearing bush is conceivable.
  • the two embodiments of a sliding bearing arrangement allow a particular radial bearing of the planetary gear and also ensure a sufficient axial bearing thereof, wherein the geometries of the components of the sliding bearing assembly can be produced easily manufacturing technology.
  • the two bearing bushing unit forming conical bearing rings in the O-arrangement or the X-arrangement are releasably fixed to the Planetenradwelle.
  • This can for example take place via a screw.
  • the bearing bush unit is secured against rotation relative to the Planetenradwelle. This rotation can also be done by way of example, via a tongue and groove connection or a profile toothing.
  • the two conical bearing rings releasably together, for example, to screw.
  • the so far attached bearing rings form a stable bearing bush unit.
  • at least one intermediate ring is arranged axially between the conical bearing rings in order to bridge any larger bearing widths or to create a lubricant oil supply or removal to or from the bearing gap by means of a transverse channel extending through the intermediate ring.
  • the two conical bearing rings are arranged in a corresponding thereto receiving groove of the planetary, which is at least partially formed together with a planet carrier.
  • the two conical bearing rings can be mounted. After assembly, the substantially U-shaped receiving groove is formed, in which the two conical bearing rings are positioned functionally.
  • additional connecting means can - be dispensed with - except for a rotation.
  • each conical bearing ring is assigned an inner plain bearing bush with an L-shaped cross-section, which together form a substantially chen U-shaped receiving groove forming attached to the Planetenradwelle, wherein the conical bearing rings form a floating plain bearing bushing arrangement with respect to the inner plain bearing bushes on the one hand and the planet or a thereto attached additional plain bearing bush on the other.
  • the conical bearing rings themselves form a floating plain bearing bush arrangement, wherein both their outer surfaces and their inner surfaces define a sliding bearing gap.
  • the angle a between the cylindrical inner surface and the obliquely extending outer surface of each conical bearing ring is in the range between 2 ° to 45 °.
  • Another essential variable design feature is the ratio between the width of the conical bearing ring and the outer diameter of the Planetenradwelle. This ratio is preferably> 0.2, more preferably> 0.6 or> 0.8. In this measurement ratio, the sliding bearing assembly has a sufficiently large load capacity at the same time compact geometric dimensions.
  • the sliding bearing surfaces of the sliding bearing arrangement - with or without an additional floating plain bearing bush - be at least partially provided with a vapor-deposited hard material layer.
  • a vapor-deposited hard material layer when the plain bearing parts of a conventional plain bearing material - for example, a white metal or brass material - are made, it is advisable to apply to extend the bearing life such a hard material layer.
  • it is proposed to deposit the hard material layer from the vapor phase, for example by means of the PVD coating method known per se (PVD Physical Vapor Deposition).
  • the plain bearing arrangement according to the invention for planet gears of a planetary gear stage can be used in conjunction with all types of planet carriers, that is, for example, for single-sided planetary carrier, double-sided planet carrier or planet carrier with a back plate, which is also referred to as a bogie plate.
  • FIG. 1 shows a longitudinal section through a schematic wind power transmission, the transmission input-side planetary gear stage is equipped with a sliding bearing assembly according to the invention in the region of the planetary gear,
  • FIG. 2 shows a schematic longitudinal section of a first embodiment of a sliding bearing arrangement
  • FIG. 3 shows a schematic longitudinal section of a second embodiment of a sliding bearing arrangement
  • FIG. 4 shows a schematic longitudinal section of a third embodiment of a slide bearing arrangement
  • Fig. 5 is a schematic longitudinal section of a fourth embodiment of a sliding bearing assembly
  • Fig. 6 is a schematic longitudinal section of a fifth embodiment of a sliding bearing assembly.
  • the schematized wind power transmission essentially comprises an input shaft 2 which is rotatably mounted in a transmission housing 1 and which is formed integrally with a planet carrier 3 of a transmission input side planetary gear stage 4.
  • the transmission-input-side planetary gear stage 4 forms a output via a sun gear shaft 5, which drives a downstream second planetary gear stage 6.
  • a sun gear 7 of this second planetary gear 4 forms the output to a gear output side spur gear 8 with output shaft 9, which serves to drive a - not shown here - electric generator of the wind turbine with respect to the input speed higher speed.
  • the transmission input-side planetary gear stage 4 has a slide bearing arrangement 10 in the region of the planetary gear shafts 11 (by way of example) for supporting the planetary gear 12 associated therewith.
  • Each planetary gear 12 is in the context of the planetary gear 4 on the one hand in meshing with the sun gear 5 and on the other hand in meshing engagement with a ring gear 13 which is fixedly mounted on the transmission housing 1.
  • a slide bearing assembly 10a is formed in the form of an O-arrangement.
  • a bearing bush unit for combined axial and radial bearing of the planetary gear 12 with respect to the Planetenradwelle 11 is formed from a pair of conical bearing rings 100a and 100b.
  • the two conical bearing rings 100a and 100b come to rest against each other via their respective acute-angled side surface.
  • Each conical bearing ring 100a and 100b has a cylindrical inner surface 110 (by way of example) and an outer surface 120 extending at an angle thereto (by way of example).
  • the inner surface is opposite the outer surface at an angle a of 15 °.
  • the inner surface 110 comes to the Planetenradwelle 11 to the plant.
  • the outer surface 122 corresponds in this embodiment with a floating bushing 130 (exemplary), which on the other hand corresponds to the associated bearing surface on the planet gear 12.
  • the bearing bushing unit forming conical bearing rings 100a and 100b are releasably and non-rotatably fixed to the Planetenradwelle 11.
  • the planetary gear shaft 11 is further traversed by an oil feed 140 for lubricating oil supply of the bearing column of the sliding bearing assembly 10 a, which is fed from - not shown here - external body ago.
  • the two bearing bushing unit forming conical bearing rings 200a and 200b are also provided with a triangular cross-section, but the facing acute-angled corner regions are flattened, so that the two conical bearing rings 200a and 200b via mutually corresponding annular abutment surfaces abut each other , Over several circumferentially distributed screws 210 (exemplified), the two conical bearing rings 200a and 200b are releasably secured together.
  • the consisting of the two interconnected conical bearing rings 200a and 200b bearing bush unit is arranged in a corresponding thereto receiving groove 220 of the Planetenradwelle 11. This substantially U-shaped receiving groove 220 serves to position the bearing bush unit.
  • the receiving groove 220 is bounded by the planet carrier 3.
  • the bearing bush unit can be mounted by inserting the Planetenradwelle 11 in the space provided for breakthroughs in the planet carrier 3.
  • the sliding bearing assembly 10b also includes the conical bearing rings 200a and 200b each associated floating plain bearing bushes 230 (exemplary), which is arranged between each conical bearing ring 200a and 200b and the bearing surface corresponding thereto bearing side 12 of the planet.
  • a pair of tapered bearing rings 300a and 300b form a slide bearing assembly 10c in an X arrangement.
  • an intermediate ring 310 is arranged, via the transverse channel and an oil drain from the bearing gap.
  • the outer face of the bearing bush unit a stop ring 320 is provided in each case to guide the here also for slide bearing assembly 10c associated floating plain bearing bushes 330.
  • a pair of conical bearing rings 400a and 400b are provided in an O arrangement which are fixed to the planetary gear shaft 1 1.
  • the sliding bearing surfaces of the two conical bearing rings 400a and 400b are each provided with a hard material layer 410 (by way of example), for example designed as a PVD coating, the course of which is indicated by a dashed-dotted line.
  • the slide bearing assembly 10d of this embodiment does not require a floating plain bearing bush, wherein the lubricating oil supply of the lubricating gap, which here is formed directly between the two conical bearing rings 400a and 400b on the one hand and the corresponding bearing surface on the part of the planetary gear 12, is supplied via an oil feed channel 440.
  • each conical bearing ring 500a and 500b is associated with an inner plain bearing bush 510a or 510b with an L-shaped cross section, which form a U-shaped receiving groove 520.
  • the two inner plain bearing bushes 510a and 510b are fixed to the Planetenradwelle 1 1, whereas the two conical bearing rings 500a and 500b here form a floating plain bearing bushing arrangement.
  • the floating bearing conical bearing rings 500a and 500b between the inner plain bearing bushes 510a and 510b on the one hand and the planet gear 12 are arranged.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un étage de train planétaire muni d'un système de palier lisse (10 ; 10a-10e), en particulier pour un logement d'un pignon satellite, comprenant au moins deux arbres (11) de pignon satellite sur lesquels au moins un pignon satellite (12) est logé rotatif par le biais d'un système de palier lisse (10 ; 10a-10e) qui présente une unité douille de palier montée sur l'arbre (11) de pignon satellite concerné pour le logement combiné radial et axial du pignon satellite (12). L'unité douille de palier comprend une paire de bagues de palier coniques (100a, 100b - 500a, 500b) qui présentent chacune une surface intérieure (110) cylindrique ainsi qu'une surface extérieure (120) inclinée par rapport à cette dernière, la surface intérieure (110) venant en appui sur l'arbre (11) de pignon satellite ou sur au moins une douille de palier lisse intérieure (510a, 510b) montée sur ce dernier, et la surface extérieure (120) coopérant avec une surface de palier complémentaire réalisée à cette fin côté pignon satellite (12) pour former un palier lisse.
PCT/EP2018/082284 2017-12-15 2018-11-22 Étage de train planétaire muni d'un système de palier lisse, en particulier pour un logement de pignon satellite dans une transmission d'éolienne WO2019115202A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017222901.2A DE102017222901A1 (de) 2017-12-15 2017-12-15 Planetengetriebestufe mit einer Gleitlageranordnung, insbesondere für eine Planetenradlagerung in einem Windkraftgetriebe
DE102017222901.2 2017-12-15

Publications (1)

Publication Number Publication Date
WO2019115202A1 true WO2019115202A1 (fr) 2019-06-20

Family

ID=64564845

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/082284 WO2019115202A1 (fr) 2017-12-15 2018-11-22 Étage de train planétaire muni d'un système de palier lisse, en particulier pour un logement de pignon satellite dans une transmission d'éolienne

Country Status (2)

Country Link
DE (1) DE102017222901A1 (fr)
WO (1) WO2019115202A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020116588A1 (de) 2020-06-24 2021-12-30 Schaeffler Technologies AG & Co. KG Schräggleitlager
DE102020129063A1 (de) 2020-11-04 2022-05-05 Schaeffler Technologies AG & Co. KG Planetenradlagerung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2662598A1 (fr) 2012-05-08 2013-11-13 ZF Wind Power Antwerpen NV Étage d'engrenage planétaire avec des paliers lisses en tant que roulements planétaires
WO2014117197A1 (fr) * 2013-01-30 2014-08-07 Miba Gleitlager Gmbh Transmission d'éolienne
EP3091255A1 (fr) * 2015-05-07 2016-11-09 Siemens Aktiengesellschaft Train épicycloïdal
CN107299966A (zh) * 2016-04-15 2017-10-27 南京高速齿轮制造有限公司 一种行星齿轮变速器
EP3290751A1 (fr) * 2016-09-02 2018-03-07 Flender GmbH Train épicycloïdal

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52112055A (en) * 1976-03-16 1977-09-20 Mitsubishi Electric Corp Planetary gears
AT509624B1 (de) * 2010-04-14 2012-04-15 Miba Gleitlager Gmbh Windkraftanlage
DE102014110907A1 (de) * 2014-07-31 2016-02-04 Rolls-Royce Deutschland Ltd & Co Kg Gleitlagervorrichtung

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2662598A1 (fr) 2012-05-08 2013-11-13 ZF Wind Power Antwerpen NV Étage d'engrenage planétaire avec des paliers lisses en tant que roulements planétaires
WO2014117197A1 (fr) * 2013-01-30 2014-08-07 Miba Gleitlager Gmbh Transmission d'éolienne
EP3091255A1 (fr) * 2015-05-07 2016-11-09 Siemens Aktiengesellschaft Train épicycloïdal
CN107299966A (zh) * 2016-04-15 2017-10-27 南京高速齿轮制造有限公司 一种行星齿轮变速器
EP3290751A1 (fr) * 2016-09-02 2018-03-07 Flender GmbH Train épicycloïdal

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