WO2024056204A1 - Roue d'engrenage et transmission planétaire la comprenant - Google Patents

Roue d'engrenage et transmission planétaire la comprenant Download PDF

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Publication number
WO2024056204A1
WO2024056204A1 PCT/EP2023/025361 EP2023025361W WO2024056204A1 WO 2024056204 A1 WO2024056204 A1 WO 2024056204A1 EP 2023025361 W EP2023025361 W EP 2023025361W WO 2024056204 A1 WO2024056204 A1 WO 2024056204A1
Authority
WO
WIPO (PCT)
Prior art keywords
sun gear
toothing
gear
transmission according
thrust washer
Prior art date
Application number
PCT/EP2023/025361
Other languages
German (de)
English (en)
Inventor
Rafael RODARTE
Ramon de Assis
Antonio Ventriglia VIEIRA
Original Assignee
Sew-Eurodrive Gmbh & 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 Sew-Eurodrive Gmbh & Co. Kg filed Critical Sew-Eurodrive Gmbh & Co. Kg
Publication of WO2024056204A1 publication Critical patent/WO2024056204A1/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
    • 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
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/0204—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor for orientation in relation to wind direction
    • 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
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/10—Arrangements or devices for absorbing overload or preventing damage by overload
    • 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
    • F16H57/00—General details of gearing
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
    • 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
    • F05B2260/50—Kinematic linkage, i.e. transmission of position
    • F05B2260/503—Kinematic linkage, i.e. transmission of position using 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
    • 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
    • F16H2057/0081—Fixing of, or adapting to transmission failure
    • 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
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • F16H57/0424—Lubricant guiding means in the wall of or integrated with the casing, e.g. grooves, channels, holes
    • 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
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • 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
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • 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
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0486—Gearings with gears having orbital motion with fixed gear ratio

Definitions

  • the invention relates to a gearbox, in particular a planetary gearbox, with a sun wheel and a wind turbine with a rotatably arranged nacelle.
  • a planetary gear has a sun gear meshing with planetary gears meshing with a ring gear.
  • a wind turbine is known from AT 512 436 A1.
  • the invention is therefore based on the object of efficiently operating a device driven by the planetary gear, in particular a wind turbine.
  • the object is achieved in the transmission according to the features specified in claim 1 and in the wind turbine according to the features specified in claim 15.
  • toothing of the sun gear has an interruption such that a first toothing region of the toothing is spaced from a second toothing region of the toothing in the axial direction, wherein a predetermined breaking point is arranged in the axial direction between the first toothing region and the second toothing region, in particular wherein the axial direction is aligned parallel to the axis of rotation of the sun gear.
  • the predetermined breaking point is designed as a narrowing, with the smallest outside diameter of the predetermined breaking point being smaller than the root diameter of the toothing.
  • the predetermined breaking point is formed as a rotating body section, the axis of rotational symmetry of which is aligned coaxially with the rotational axis of the sun gear, the curve generating the rotating body being a semicircle or a semi-ellipse.
  • the advantage here is that with a generating curve with a semicircle the production is very simple and with a generating curve with a semi-ellipse the predetermined breaking point can be made more well-defined than with a version with a semicircle. In any case, the predetermined breaking point is concave.
  • the axial position of that point of the predetermined breaking point which has the smallest outside diameter is preferably arranged axially centrally, so that the outside diameter increases in both axial directions starting from this point.
  • the rotating body is concavely shaped and/or the outer diameter of the rotating body section increases strictly monotonically with increasing axial distance to the narrowest point of the rotating body, i.e. to the axial position at which the rotating body has the smallest outer diameter.
  • the toothing is designed as a straight toothing.
  • the advantage here is that simple, cost-effective production is possible.
  • a shaft is connected to the sun gear in a rotationally fixed manner, in that the toothing is in engagement with an internal toothing of the shaft.
  • the sun gear also functions as a toothed coupling part.
  • the shaft has an internally toothed blind hole into which the teeth of the sun gear are partially inserted.
  • the sun gear has a collar on its side axially remote from the shaft, in particular a cylindrical section, the outer diameter of which is smaller than the root diameter of the toothing and larger than the smallest outer diameter of the predetermined breaking point, in particular with the collar being axially spaced is from the breaking point.
  • the teeth are spaced apart from the thrust washer and are therefore protected.
  • the end face of the first sun gear can be designed as a flat surface, so that the radially directed depressions incorporated into the thrust washer form channels through which oil that has passed axially through the thrust washer can be guided.
  • the first sun gear is a solid part, in particular the first sun gear is not a hollow part.
  • the advantage here is that no oil can flow through the first sun gear in the axial direction and thus a radial one Flowing out is forced. The oil therefore flows through the hollow second sun gear and then through the thrust washer, where it is then deflected in the radial direction and flows out. This not only improves lubrication, but also spreads lost heat, so that peak temperatures in the gearbox are reduced and heat dissipation to the environment is improved.
  • the material of the first sun gear is gap-free and/or radially within the smallest outer diameter of the predetermined breaking point continuously formed and/or evenly executed.
  • the semi-ellipse has a major semi-axis, in particular the main axis, which has at least twice the length of the minor semi-axis, in particular the minor axis.
  • the first sun gear is in engagement with planet gears which are in engagement with an internally toothed ring gear, the planet gears being rotatably mounted on a planet carrier which has an internally toothed bore into which the teeth of a second sun gear are partially inserted.
  • the advantage here is that a high gear ratio can be achieved in a small area of space.
  • the second sun gear has an axial, continuous, in particular centrally arranged recess. The advantage here is that material can be saved, the dynamics of the transmission are increased, the moment of inertia is reduced and the lubrication and cooling are improved as a result of the oil flowing through axially.
  • the first sun wheel is not hollow, but is designed as a solid part. This is the only way to achieve a well-defined breaking point.
  • oil cannot flow through the first sun gear and the heat dissipation must be effected by the oil surrounding the second toothing area and the oil flowing through the predetermined breaking point designed as a constriction.
  • the second sun gear is designed to be hollow.
  • the advantage here is that material can be saved, the dynamics of the transmission are increased, the moment of inertia is reduced and the lubrication and cooling are improved as a result of the oil flowing through axially.
  • the first sun wheel is not hollow, but is designed as a solid part. This is the only way to achieve a well-defined breaking point.
  • oil cannot flow through the first sun gear and the heat dissipation must be effected by the oil surrounding the second toothing area and the oil flowing through the predetermined breaking point designed as a constriction.
  • a thrust washer is accommodated in the first planet carrier, which axially limits the first sun gear, in particular the collar of the first sun gear.
  • the advantage here is that the thrust washer is made of a hardened material and thus the friction is reduced.
  • the radially directed channels are flowed through with oil, which is also conveyed by centrifugal force and forms a hydrodynamic cushion for the first sun gear. This means that the axial limitation is achieved with little effort and friction despite the different speeds.
  • the thrust washer is held non-positively in the first planet carrier, in particular by means of a snap ring.
  • the first planet carrier has an axially continuous stepped bore, wherein the thrust washer rests against a first stage of the stepped bore, in particular wherein a bearing of a first planet rests against a second stage of the stepped bore.
  • the thrust washer can be securely fastened.
  • the first sun gear rests against the thrust washer on the side of the thrust washer facing away from the first stage. This means that the thrust washer is pressed against the first stage and is therefore held securely.
  • the advantage here is that efficient operation can be achieved since the first sun gear is kept at a distance from the second sun gear, i.e. the central gear of the second planetary gear stage, by a thrust washer that has a greater hardness than the end face of the second sun gear.
  • the material of the thrust washer is therefore different in hardness compared to the material of the second sun gear, in particular which is made of the same material as the first sun gear.
  • the thrust washer is made of steel and treated with nitriding.
  • the advantage here is that simple production and low coefficients of friction can be achieved.
  • the thrust washer has a centrally arranged, axially continuous hole.
  • the advantage here is that lubricating oil passes through the hole, i.e. without the influence of centrifugal force. Because the radial distance disappears here, the centrifugal force also disappears.
  • one or more recesses are formed on the side of the thrust washer facing the first sun gear, each of which extends from the centrally arranged, axially continuous hole to the radially outer edge of the thrust washer, in particular in such a way that one of the thrust washer and the first Sun wheel limited channel is formed, in particular wherein the depressions and / or channels are regularly spaced from one another in the circumferential direction.
  • the advantage here is that lubricating oil passes through the hole and can then be conveyed radially. That way they're not on Planets arranged with vanishing radial distance can be easily lubricated, especially their needle bearings; because the planets are mounted using needle bearings that are pushed onto bolts on the planet carrier.
  • the channel cross section initially increases and then decreases as the radial distance increases.
  • the advantage here is that the channel cross-section, which increases up to a maximum value with increasing radial distance, creates a buffer volume that enables a constant outflow at an even larger radial distance even when filled with lubricating oil unsteadily, since the channel cross-section decreases again from the maximum value when the radial distance continues to increase. The channel then opens at this greatest radial distance towards the planets, especially towards their bearings.
  • the transmission has more than two planetary gear stages arranged in series.
  • the advantage is that a high gear ratio can be achieved.
  • wind turbine with a rotatably arranged nacelle, in which a generator is arranged, are that the wind turbine has a transmission driven by an electric motor according to one of the preceding claims, the output shaft of which is connected in a rotationally fixed manner to a pinion, which is connected to a ring gear is in engagement, in particular wherein the toothing of the pinion is in engagement with the external toothing of a gear ring, in particular wherein the rotational position of the gear ring is and/determines the rotational position of the nacelle, in particular wherein the gear is connected to the nacelle and the rotational position of the nacelle is in particular relative to the sprocket, can be controlled by the rotational position of the sprocket related to the gearbox.
  • a planetary gear according to the invention is shown in a sectional view in FIG.
  • a shaft 5 in particular the driving shaft of the planetary gear, is rotatably mounted via a bearing 2 accommodated in a housing part, in particular a bearing flange 9.
  • a shaft sealing ring 4 which is also accommodated in the bearing flange 2, seals against the shaft 5.
  • the bearing 2 is thus sealed with oil from the interior of the planetary gear.
  • the positioning flange has a hollow cylindrically shaped support section which projects into the interior of the planetary gear.
  • the bearing 2 and the shaft sealing ring 4 are spaced apart from one another in the axial direction, in particular in the direction of the axis of rotation of the shaft 5.
  • a channel 3 running radially through the hollow cylindrical support section enables oil to be filled on the outer circumference of the hollow cylindrical support section.
  • Another radially continuous channel 6 is arranged diametrically opposite the first channel 3 on the hollow cylindrical section. This means that overfilling with oil can be avoided.
  • the shaft 5 is connected to a first sun gear 1 in a rotationally fixed manner.
  • the first sun gear 1 has teeth that are interrupted in the axial direction, that is to say in the direction of the axis of rotation of the first sun gear 1.
  • the first sun gear 1 has a first toothing region 20 and a second toothing region 21 which is spaced apart from the first toothing region 20 in the axial direction.
  • Both toothing areas (20, 21) have the same number of teeth, modules and parameters of the involute toothing; only the tip circle diameter is different, since the first toothing area 20 has a smaller tip circle diameter than the second toothing area 21.
  • first toothing area has an insertion chamfer at its end area axially remote from the second toothing area 21, in particular beveled head areas.
  • the tip circle diameter of the first toothing area 20 therefore increases monotonically as the distance to the second toothing area 21 decreases.
  • the second toothing region 21 is in engagement with the toothing of first planets 7, which in turn are in engagement with an internally toothed first ring gear 8, which is non-rotatably connected to the bearing flange 9.
  • the first planets 7 are rotatably arranged on a first planet carrier 11, which drives further gear stages.
  • a second sun gear 12 with its running teeth is inserted into an internally toothed area of the first planet carrier 11 in the first planet carrier 11, the running teeth being manufactured uninterrupted.
  • the second sun gear 12 is thus connected to the first planet carrier 11 in a rotationally fixed manner.
  • a first thrust washer 10 is accommodated, the outer diameter of which is larger than the tip circle diameter of the second toothing region of the first sun gear 1.
  • the second sun gear 12 is in engagement with second planet gears 13, which in turn are in engagement with the internally toothed ring gear 8 or alternatively, in further exemplary embodiments according to the invention, with another ring gear.
  • the second planet gears 13 are rotatably mounted on a second planet carrier 16, which in turn is connected in a rotationally fixed manner to a third sun gear 15, in that its running teeth are in turn inserted into an internally toothed region of the second planet carrier 16.
  • the first sun gear 1 is not hollow, in particular, but as a solid part.
  • the second sun gear 12 is axially continuously hollow, in particular as a hollow part.
  • the clear inside diameter of the second sun gear 12 is in particular larger than the smallest outside diameter of the predetermined breaking point 30 of the first sun gear 1, which is designed as a narrowing.
  • the tip circle diameter of the second toothing region 21 is larger than the clear inside diameter of the hollow second sun gear 12.
  • the maximum transferable torque of the first sun gear 1 is therefore determined by the predetermined breaking point 30.
  • this maximum transferable torque is at least five or ten times smaller than the maximum torque that can be passed through the second sun gear 12.
  • a second thrust washer 14 is accommodated in the second planet carrier 16, which axially delimits the second sun gear 12.
  • the first thrust washer 10 limits the first sun gear 1 axially.
  • the first sun gear 1 has a collar 31 on its axial end region facing the first thrust washer 10, so that the axial end face of the first gear 1, which can abut the thrust washer 10, has an outer diameter that is smaller than the tip circle diameter of the second toothing region 21 of the first sun gear 1.
  • the predetermined breaking point 30 is designed as a constriction, the smallest outer diameter of which is smaller than the smallest root diameter of the first toothing area 20 and is also smaller than the smallest root diameter of the second toothing area 21. As can be seen in Figure 3, the predetermined breaking point 30 has a rounding which is semicircular in cross section. This enables simple production using a radius.
  • a rounding which has a semi-elliptical rounding instead of the semicircular rounding is particularly advantageous.
  • the rounding is designed as a rotating body section with a semi-ellipse-shaped rounded cross-section, a maximum transferable torque can be specified as precisely as possible and, in the event of a predetermined break, a vanishing or at least as minimal number of particles breaking off can be achieved in the event of an overload.
  • the first sun gear 1 is broken and the input shaft 5 can rotate freely relative to the output shaft of the transmission, but there are only a few metal particles in the oil-filled interior of the transmission, so that when the first sun gear 1 is repaired, i.e. replaced, there is only one Replacing the first sun gear 1 is sufficient to enable recommissioning.
  • the transmission according to the invention is preferably used in a yaw angle adjustment mechanism of a wind turbine, in particular in an arrangement for rotating the nacelle of the wind turbine.
  • an electric motor drives the input shaft 5 and the output shaft is therefore only rotated slowly, but a sufficiently high torque is generated for the yaw angle adjustment of the wind turbine.
  • the yaw angle adjustment requires a torque that exceeds a threshold value, for example because the yaw angle adjustment mechanism is blocked, the torque passed through the first sun gear 1 exceeds the threshold value and destroys the first sun gear 1 at the predetermined breaking point 30.
  • This means that further ones are particularly more expensive to produce Parts protected because after the destruction of the first sun gear 1, the output shaft of the transmission is arranged to rotate freely. This then aligns the nacelle according to the air resistance and the wind turbine can go out of operation.
  • the output shaft of the gearbox is connected in a rotationally fixed manner to a pinion, which is in mesh with a ring gear.
  • a pinion which is in mesh with a ring gear.
  • the outer diameter of the ring gear is at least five times larger than the outer diameter of the pinion, which is non-rotatably connected to the driving shaft.
  • the expensively manufactured ring gear is protected by destroying the first sun gear 1 arranged in a driving manner at the predetermined breaking point 30.
  • geared motors according to the invention are arranged in the wind turbine, all of which act on the same gear ring, in particular to rotate the nacelle.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne une transmission, en particulier une transmission planétaire, comprenant un pignon planétaire et une éolienne pourvue d'une nacelle agencée de manière rotative, la denture du pignon planétaire présentant une interruption de sorte qu'une première région de denture de la denture est espacée d'une seconde région de denture de la denture dans la direction axiale, un point de rupture défini étant disposé entre la première région de denture et la seconde région de denture dans la direction axiale.
PCT/EP2023/025361 2022-09-13 2023-08-01 Roue d'engrenage et transmission planétaire la comprenant WO2024056204A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102022003370.4A DE102022003370B3 (de) 2022-09-13 2022-09-13 Getriebe, insbesondere Planetengetriebe, mit Sonnenrad und Windkraftanlage mit einer drehbar angeordneten Gondel
DE102022003370.4 2022-09-13

Publications (1)

Publication Number Publication Date
WO2024056204A1 true WO2024056204A1 (fr) 2024-03-21

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ID=86317374

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2023/025361 WO2024056204A1 (fr) 2022-09-13 2023-08-01 Roue d'engrenage et transmission planétaire la comprenant

Country Status (2)

Country Link
DE (2) DE102022003370B3 (fr)
WO (1) WO2024056204A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004048805A1 (fr) * 2002-11-22 2004-06-10 Joachim Arndt Procede de transmission de couple a faibles pertes dans les boites a engrenages planetaires
US6820727B1 (en) * 1999-05-21 2004-11-23 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Wear adjustment device for a brake
AT512436A1 (de) 2012-01-16 2013-08-15 Miba Gleitlager Gmbh Windkraftanlage
WO2015188803A2 (fr) * 2014-06-07 2015-12-17 Günther Zimmer Engrenage épicycloïdal à deux roues solaires avec minimisation du jeu d'engrènement
DE102017107892A1 (de) 2017-04-12 2018-10-18 AUMA Drives GmbH Schließvorrichtung
CN113685494A (zh) * 2021-08-30 2021-11-23 徐州徐工传动科技有限公司 蜗轮蜗杆传动箱和工程机械

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6820727B1 (en) * 1999-05-21 2004-11-23 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Wear adjustment device for a brake
WO2004048805A1 (fr) * 2002-11-22 2004-06-10 Joachim Arndt Procede de transmission de couple a faibles pertes dans les boites a engrenages planetaires
AT512436A1 (de) 2012-01-16 2013-08-15 Miba Gleitlager Gmbh Windkraftanlage
WO2015188803A2 (fr) * 2014-06-07 2015-12-17 Günther Zimmer Engrenage épicycloïdal à deux roues solaires avec minimisation du jeu d'engrènement
DE102017107892A1 (de) 2017-04-12 2018-10-18 AUMA Drives GmbH Schließvorrichtung
CN113685494A (zh) * 2021-08-30 2021-11-23 徐州徐工传动科技有限公司 蜗轮蜗杆传动箱和工程机械

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DE102023003162A1 (de) 2024-03-14
DE102022003370B3 (de) 2023-06-01

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