WO2012007461A1 - Transmission multi-étagée et système de réglage - Google Patents

Transmission multi-étagée et système de réglage Download PDF

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Publication number
WO2012007461A1
WO2012007461A1 PCT/EP2011/061852 EP2011061852W WO2012007461A1 WO 2012007461 A1 WO2012007461 A1 WO 2012007461A1 EP 2011061852 W EP2011061852 W EP 2011061852W WO 2012007461 A1 WO2012007461 A1 WO 2012007461A1
Authority
WO
WIPO (PCT)
Prior art keywords
worm
transmission according
gear
sleeve
speed transmission
Prior art date
Application number
PCT/EP2011/061852
Other languages
German (de)
English (en)
Inventor
Frank Richter
Yueksel Ekoez
Ewald Schmitz
Ilja Imgrunt
Original Assignee
Zf Friedrichshafen Ag
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 filed Critical Zf Friedrichshafen Ag
Publication of WO2012007461A1 publication Critical patent/WO2012007461A1/fr

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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
    • F16H55/22—Toothed members; Worms for transmissions with crossing shafts, especially worms, worm-gears
    • F16H55/24—Special devices for taking up backlash
    • 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
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H57/022—Adjustment of gear shafts or bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S30/00—Arrangements for moving or orienting solar heat collector modules
    • F24S30/40—Arrangements for moving or orienting solar heat collector modules for rotary movement
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F16H2057/0213—Support of worm gear 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
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/126—Self-adjusting during operation, e.g. by a spring
    • F16H2057/127—Self-adjusting during operation, e.g. by a spring using springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S30/00—Arrangements for moving or orienting solar heat collector modules
    • F24S2030/10—Special components
    • F24S2030/13—Transmissions
    • F24S2030/134—Transmissions in the form of gearings or rack-and-pinion transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S30/00—Arrangements for moving or orienting solar heat collector modules
    • F24S2030/10—Special components
    • F24S2030/15—Bearings
    • 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
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/47—Mountings or tracking

Definitions

  • the invention relates to a multi-speed transmission according to the preamble of claim 1.
  • the invention further relates to a control system, in particular for heliostats, according to the preamble of claim 14.
  • the multi-speed transmission according to the invention for driving at least one adjustable element of a solar energy recovery system is characterized in that a self-locking and backlash running worm gear forms the output stage of the multi-speed transmission, and that the output member of the worm gear is rotatably connected to the adjustable element.
  • the adjustable element is for example the reflector of a heliostat as part of a solar tower power plant.
  • the reflector should hold as free of play a certain position and then, after a certain residence time, follow the wandering sun with an adjusting movement.
  • the exact alignment of the inflected solar radiation essential for the efficiency of the solar tower power plant.
  • the worm gear is self-locking, d. H.
  • Rotary movements from the output side are not transmitted as rotary movements to the drive side, but decelerated due to the self-locking design of the worm.
  • This allows any positions of the worm wheel shaft to be held without additional brake.
  • This is particularly advantageous for actuators.
  • this aspect is particularly important because in the outdoor mounted elements, the wind applies a significant force to the elements and thereby into the drive train of the adjustment system. If an element is attached playfully and movably, then it can not be kept in a fixed position because of the wind and by repeatedly reciprocating by the wind, the ele- ment and its drive train can be damaged.
  • Worm gear connected element e.g. the reflector of a heliostat precisely follows a predetermined trajectory and is held rigidly in intermediate positions, because there is no backlash-related gear stage on the output side.
  • the arranged in the drive train of the multi-speed transmission in front of the worm gear units which may for example be designed as a multi-stage planetary gear, have no particularly high clearance requirements and can therefore be produced inexpensively with lower manufacturing precision.
  • the efficiency of the multi-speed transmission is relatively high in relation to the high overall ratio, because the worm gear upstream gear ratios allow a higher tooth and bearing clearance and thereby internal friction losses are kept low in the transmission.
  • worm gears are already known from other applications.
  • a worm gear for a steering gear wherein the worm shaft is formed as a bending beam and the front side - in the adjacent region of the screw - is biased by a spring-loaded pressure piece in the direction worm wheel. The worm is thus pressed into the flanks of the worm wheel, so that the worm gear operates without play.
  • Such a worm gear is in principle suitable for the proposed multi-speed transmission according to the invention.
  • a worm gear is preferably provided, in which the worm shaft bearing is firmly held in a guide element, by which the radial movement of the bearing - in the direction of the worm wheel - is determined inevitably.
  • the advantage is achieved that the worm is guided in a predetermined movement path and direction of movement in the teeth of the worm wheel until a two-flank contact made, ie game freedom between worm and worm wheel is reached.
  • the guide element is thus part of a kinematic transmission, which determines the path of movement of the bearing. This results depending on the application, a number of different constructively complex or less complex solutions to achieve the backlash of the worm gear.
  • the guide element is designed as a sleeve which elastically in a bore, d. H. is supported with a circular cylindrical cross-section of the gear housing.
  • the sleeve is supported via at least one elastic element with respect to the bore.
  • the sleeve is thus on the one hand centered with respect to the bore and on the other hand displaceable in one direction.
  • the at least one elastic element is formed as an O-ring, which is arranged between the bore and the sleeve, preferably in an annular groove.
  • the sleeve is thus guided parallel to the direction of movement in the housing bore and can perform radial movements in the radial gap, wherein the elastic elements, respectively O-rings are deformed.
  • two diametrically opposed flattenings are provided.
  • the sleeve is loaded on its side facing away from the worm wheel, flattened side by a spring element which presses the worm shaft bearing in the tooth flanks of the worm wheel.
  • the backlash and the self-locking effect particularly advantageous on the multi-speed transmission and a positioning system of the element.
  • Intermediate positions can be held on the output side backlash and without parking brake and this over a long service life, since the worm shaft is tracked even when wearing and thus the backlash is maintained.
  • the guide element is designed as a pivoting arm, eccentric or link, which is mounted in the gear housing and is rotatable about a pivot axis arranged parallel to the axis of the worm shaft.
  • the center of the worm shaft bearing is thus guided on a circular path about the pivot axis in the direction of the worm wheel, so that backlash is achieved.
  • the swing radius, d. H. The distance between the pivot axis and the center of the worm shaft can be chosen sufficiently large, so that the curvature of the circular path is negligible in terms of the distance covered.
  • the swivel arm which may also be formed as an eccentric, loaded at its opposite end of the pivot axis by a spring element which exerts a torque on the pivot arm with respect to its pivot axis in the direction of the worm wheel.
  • the bearing is between the pivot axis and the resultant of the spring force, so that there is a maximum lever arm for the spring force.
  • the guide element is designed as a sliding element, which is guided in straight guideways of the transmission housing. This achieves exactly radial guidance of the worm in the direction of the worm wheel in order to achieve freedom from play.
  • the solution is structurally relatively simple and therefore inexpensive.
  • the sliding element is preferably provided by a spring derelement, for example, a compression spring, loaded with direction on the worm wheel.
  • the present invention comprises an adjusting system for at least one adjustable element of a solar energy production plant, in particular a heliostat, with a multi-speed transmission according to the preceding description.
  • a servo motor and a control device is provided, wherein the servo motor is designed as a stepper motor which can be controlled by the control means by means of an incremental control. Due to a relatively high gear ratio, many increments can be used for a positioning operation for very small angular degrees. Therefore, the system can be executed as a controlled system, since a step not executed by the engine is not of great importance in terms of accuracy. This facilitates the effort in the sensor and the engine control and thus offers further cost advantages.
  • the proposed control system adjusts via a standard transmission with low tolerance requirements and over a self-locking, i. self-locking and backlash-free transmission output stage, e.g. a reflector of a heliostat.
  • a self-locking and backlash-free transmission output stage e.g. a reflector of a heliostat.
  • the reflector of the heliostat follows the course of the sun in always the same direction of rotation.
  • Worm gear is adjusted by the springing backlash and can thus very precisely hold the position approached by the servomotor. Vibration and alternating loads from the heliostat are thus absorbed in the output stage.
  • the drive-side components of the drive train arranged on the worm gear are not affected by this. As a result, peak loads from wind incidence only need to be absorbed by the output stage.
  • the drive-side gear stages and the servomotor only the actuating forces derived from normal operation become relevant.
  • the described springing the self-locking worm gear is for the control system of great importance, because the worm wheel with slight vibrations on the worm, caused for example by the wind, due to load changes or edge changes in the screw stage can not reach the computationally detectable self-locking and so continuously lose the position would be necessary for a correct incremental control.
  • FIG. 1 shows a worm gear with an elastic worm shaft bearing
  • FIG. 2 shows a worm shaft bearing which can be used within the scope of the invention
  • FIG. 2 a shows a schematic illustration of the worm shaft bearing
  • FIG. 2b shows a sleeve with O-rings for the worm shaft bearing according to FIG. 2
  • FIG. 3 shows a second embodiment of a worm shaft bearing applicable within the scope of the invention
  • FIG. 3a is a 3-D view of the worm gear according to Fig. 3,
  • Fig. 4 shows a third embodiment of an applicable within the scope of the invention screw shaft bearing and
  • Fig. 5 is a schematic representation of an actuating system according to the invention with a multi-speed transmission according to the invention.
  • Fig. 1 shows a sectional view of a worm gear 1, which comprises a worm 2 and a worm wheel 3.
  • the worm 2 is rotationally fixed, preferably integrally connected to a drive or worm shaft 4, which is in a bearing 5 designed as a rolling bearing, also called worm shaft bearing 5, is mounted.
  • the worm wheel 3 is rotatably mounted on an output shaft 6, which is mounted in a transmission housing 7.
  • the worm shaft bearing 5 is received in a sleeve 8, which in turn is supported in the transmission housing 7.
  • Fig. 2 shows the worm shaft bearing 5, which is designed as a deep groove ball bearing and rotatably mounted on the drive shaft 4 and the worm shaft 4 is fixed.
  • a spring element 10, designed as a compression spring arranged on the one hand on the housing side and on the other hand supported on the sleeve 8 and a force in the radial direction, represented by an arrow R, on the sleeve 8 exerts.
  • the sleeve 8 is partially flattened and therefore displaceable within the bore 9 in the direction of the arrow R.
  • Fig. 2a shows the sleeve 8, which is received in the bore 9 and in turn receives the worm shaft bearing 5, in a schematic representation.
  • the sleeve 8 has a top flattened in the drawing area 8a and a lower flattened in the drawing area 8b, which are thus arranged diametrically opposite each other.
  • the flattenings 8a, 8b form with the circular cross section of the bore 9 partial radial gaps 1 1, 12, which have approximately the shape of sickle columns.
  • the central axis of the bearing 5, the sleeve 8 and the bore 9 shown perpendicularly in the drawing is designated by r and corresponds to the radial direction R in Fig. 2.
  • the flattened sleeve 8 is thus laterally, ie parallel to the central axis r relatively narrow in the Drilled hole 9, while in the field of sickle column 1 1, 12 space for a shift is available.
  • Between the sleeve 8 and the bore 9 is - which is not apparent in Fig. 2a, but in the following with reference to Fig. 2b is described - arranged at least one elastic element, ie, the sleeve 8 is elastically received in the bore 9.
  • Fig. 2b shows the sleeve 8 in an axial section, without the Schneckenwellenla- ger 5.
  • O-rings 13, 14 formed elastic elements are arranged, which are held in annular grooves 15, 16.
  • the O-rings 13, 14 lie with their outer circumference - which is not shown in Fig. 2 b - to the inner wall of the bore 9 (see Fig .. 2a). They thus cause an elastic Abstützung the flattened sleeve 8 relative to the bore 9 and leave under the action of the spring 16, a displacement of the sleeve 8 in the direction of the diameter r - in the direction of the worm wheel, not shown - to. This presses the worm into the toothing of the worm wheel so that a two-flank contact (simultaneous contact with two flanks) and thus freedom from play are produced.
  • FIG. 3 shows a second exemplary embodiment of the invention for a worm gear 17, which comprises a worm 19 and a worm wheel 20 arranged on a worm or drive shaft 18.
  • the worm shaft 18 is received in a worm shaft bearing 21, which in turn is fixedly arranged in a pivot arm 22, for example, fixed by a press fit.
  • the pivot arm 22, shown schematically in the figure, may also be formed as an eccentric or link, which is pivotally mounted about a pivot axis or a pivot pin 23.
  • the pivot arm 22 is loaded at its end facing away from the pivot axis 23 by a spring 24 which exerts a torque in the clockwise direction on the pivot arm 22 and thus presses the worm 9 in the direction of the arrow R in the toothing of the worm wheel 20.
  • backlash between screw 19 and worm wheel 20 is produced.
  • Fig. 3a shows a 3-D representation of the worm gear according to FIG. 3, wherein the same reference numerals are used for the same parts.
  • the worm shaft 18 is mounted twice in the gear housing, by the arranged in the pivot arm 22 bearing 21 and by another bearing 25, which is designed as a deep groove ball bearing and an angular mobility of the worm shaft 18 allows.
  • the worm wheel 20 is rotatably mounted on an output shaft 26 and via two bearings 27 and 28 relative to the transmission housing (not shown here) stored.
  • the worm 19 engages the worm wheel 20.
  • the pivot arm 22, also called eccentric 22, has a bore 22a for a pivot pin 23 (see Fig. 3), which is supported on the housing side.
  • the pivot arm 22 also has a shoulder 22b, on which the spring element 24 engages, which is also supported on the housing side.
  • the spring element 24 causes a rotating in Fig. 3a counterclockwise torque, so that the worm 19 is pressed into the toothing of the worm wheel 20.
  • FIG. 3b shows an enlarged section of the swivel arm 22 with the spring element 24 cut open, which acts on the shoulder 22b of the swivel arm 22.
  • the spring element 24 comprises a housing-side supported pin 24a, a cap 24b movable thereon, which is loaded by a compression spring 22c.
  • a worm gear 29 which comprises a worm 30, a worm wheel 31, a worm shaft 32 and a worm shaft bearing 33.
  • a transmission housing 34 designed as a sliding block 35 sliding element is arranged and not shown by rectilinear guideways in the direction of the arrow R, d. H. guided in the radial direction.
  • the worm shaft bearing 33 is fixed, z. B. on the worm wheel 31 side facing away from the sliding block 35, a spring element 36 is arranged, which exerts a spring force in the direction of the arrow R on the slider 35 and thus the Worm 30 presses against the worm wheel 31. This achieves a play-free worm drive.
  • Fig. 5 shows a multi-stage transmission 60 as part of a control system for adjusting the position of a reflector of a heliostat in a solar tower power plant, so that the reflector, not shown, follows the course of the sun in always the same direction of rotation.
  • the multistage transmission comprises a two-stage planetary gear 42 and the worm gear 1 as a driven member. Starting from an electric servomotor 40, the torque and the rotational movement for adjusting the position of the reflector via a motor output shaft 41 in the multi-stage transmission 60 is passed. There, the rotational movement of two planetary gears and finally by a worm gear 1 is translated into slow.
  • the output shaft 6 of the worm gear 1 is rotatably and rigidly connected to the reflector.
  • a first planetary gear stage of the planetary gear 42 is essentially formed by the sun gear 43, a plurality of planet wheels 44 mounted in a planet carrier 45, and the ring gear 46.
  • the sun gear 43 is rotatably connected to the engine output shaft 41 and forms the input member of the planetary gear 42.
  • a second planetary gear of the planetary gear 42 is essentially formed by the sun gear 47, a plurality of mounted in a planet carrier 49 planetary gears 48 and the ring gear 46.
  • the planet carrier 45 as the output member of the first planetary gear is rotatably connected to the sun gear 47, the input member of the second planetary gear.
  • the planet carrier 49 of the second planetary gear forms the output member of the planetary gear 42 and is rigidly connected to the screw 2 of the downstream worm gear 1.
  • the ring gear 46 is made in one piece for the first and the second planetary gear in this example. It is also possible to provide two separate ring gears for the two planetary gear stages.
  • the worm 2 together with the worm wheel 3 forms the worm gear 1.
  • the worm wheel 3 is rotatably mounted on the output shaft 6, which in turn is rigidly connected to the reflector of the heliostat, not shown.
  • a spring element 10 presses the teeth of the worm 2 and the worm wheel 3 into one another such that the worm gear 1 reliably works free of play and self-locking.
  • the control system further comprises a control device 50 and a position sensor 51, the signal-transmitting by a control line 52 with each other are connected.
  • Another control line 53 connects the control device 50 with the servomotor 40.
  • the normal operation begins with an initialization of the system on the worm wheel 3.
  • the position is always determined by the sensor 51 and from this initialization edge follows a continuous readjustment by means of the incremental control of the electrical servomotor 40.
  • the game in the control system which changes over the lifetime, regulated daily updated and balanced in the adjustment process.
  • Due to the self-locking and backlash-free worm gear 1, the wind loads occurring at the heliostat or reflector, can cause no provision for the servo motor 40.
  • the blocking worm gear 1 is set free of play by the spring and thus can very precisely hold the position approached by the positioning motor 40. Vibration and alternating loads from the heliostat are thus absorbed in the output stage.
  • the drive side of the worm gear 1 arranged components of the drive train are not affected. As a result, peak loads from wind incidence only need to be absorbed by the output stage. For the drive-side planetary gear 42 and the servo motor 40 only derived from normal operation actuating forces are relevant.
  • the springing 10 of the self-locking worm gear 1 is for the control system of great importance, because the worm wheel with slight vibrations on the worm wheel 3, caused for example by the wind, because of load changes or edge changes in worm gear 1 can not reach the computationally detectable self-locking and so continuously the Lose position that is necessary for correct incremental control.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)

Abstract

L'invention concerne une transmission multi-étagée pour entraîner au moins un élément réglable d'une installation de production d'énergie solaire. Un engrenage à vis sans fin (1, 17, 29) réalisé autobloquant et sans jeu, forme l'étage de sortie de la transmission multi-étagée, l'organe de sortie de l'engrenage à vis sans fin étant relié solidaire en rotation avec l'élément réglable. L'invention concerne également un système de réglage pour au moins un élément réglable d'une installation de production d'énergie solaire, notamment un héliostat, ledit système de réglage comportant un moteur de réglage pouvant être commandé, un dispositif de commande et une transmission multi-étagée.
PCT/EP2011/061852 2010-07-16 2011-07-12 Transmission multi-étagée et système de réglage WO2012007461A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010031425A DE102010031425A1 (de) 2010-07-16 2010-07-16 Schneckengetriebe, Mehrstufengetriebe und Verwendung
DE102010031425.0 2010-07-16

Publications (1)

Publication Number Publication Date
WO2012007461A1 true WO2012007461A1 (fr) 2012-01-19

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Application Number Title Priority Date Filing Date
PCT/EP2011/061852 WO2012007461A1 (fr) 2010-07-16 2011-07-12 Transmission multi-étagée et système de réglage

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DE (1) DE102010031425A1 (fr)
WO (1) WO2012007461A1 (fr)

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DE102014118429A1 (de) * 2014-09-10 2016-03-10 Timotion Technology Co., Ltd. Lenkvorrichtung zur Verwendung in einer Solarnachführungsanlage
DE102017215941A1 (de) 2017-09-11 2019-03-14 Festo Ag & Co. Kg Antriebseinheit, Verwendung dafür und damit ausgestatteter Roboter
CN109916096A (zh) * 2019-02-14 2019-06-21 浙江中控太阳能技术有限公司 一种用于塔式太阳能热发电的定日镜的仰角驱动装置
CN113153979A (zh) * 2021-05-18 2021-07-23 成都理工大学 一种减速器
CN113175497A (zh) * 2021-05-18 2021-07-27 成都理工大学 用于回转台的传动装置

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DE102012103857A1 (de) * 2012-05-03 2013-11-07 Zf Lenksysteme Gmbh Vorrichtung zum Andrücken einer Schnecke oder eines Schraubritzels an ein Schneckenrad oder an ein Schraubrad
KR102281674B1 (ko) 2015-01-12 2021-07-27 주식회사 만도 자동차의 감속기
DE102017200008B4 (de) * 2017-01-02 2022-09-29 Ford Global Technologies, Llc Getriebeeinheit für ein Kraftfahrzeug
DE102017109834A1 (de) * 2017-05-08 2018-11-08 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Schneckengetriebeanordnung für Antriebssysteme im KFZ-Bereich
DE102017117724A1 (de) * 2017-08-04 2019-02-07 Thyssenkrupp Ag Spielreduktion eines Schneckengetriebes einer elektromechanischen Servolenkung mittels Bimetallfeder
NL2025061B1 (en) 2020-03-05 2021-10-14 Mci Mirror Controls Int Netherlands B V Adjustment device, and method for assembling

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