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WO2020212011A1 - Roue dentée pour transmission de véhicule électrique - Google Patents

Roue dentée pour transmission de véhicule électrique Download PDF

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Publication number
WO2020212011A1
WO2020212011A1 PCT/EP2020/055601 EP2020055601W WO2020212011A1 WO 2020212011 A1 WO2020212011 A1 WO 2020212011A1 EP 2020055601 W EP2020055601 W EP 2020055601W WO 2020212011 A1 WO2020212011 A1 WO 2020212011A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
web
range
electric vehicle
axial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2020/055601
Other languages
German (de)
English (en)
Inventor
Andreas Jung
Matthias WESA
Martin Gaber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
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 WO2020212011A1 publication Critical patent/WO2020212011A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
    • 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
    • F16H55/12—Toothed members; Worms with body or rim assembled out of detachable parts

Definitions

  • the present invention relates to a gear for an electric vehicle transmission and an electric vehicle transmission with such a gear and an electric vehicle with such an electric vehicle transmission.
  • spur gears are often installed. These have advantages in the relatively simple design, since few moving parts are used and the externally toothed spur gears are comparatively easy to manufacture.
  • One disadvantage is the small translation that can be achieved in one step.
  • a spur gear is larger and therefore heavier than, for example, a planetary gear with the same transmission capacity.
  • the scope of at least one gear is kept small, while the scope of the second gear is kept large.
  • Gears that are used to transmit rotary movements and torques (power transmission) from a drive shaft to an output shaft must be dimensionally stable against forces that act in particular when transmitting power to a gear.
  • the present invention has the object of providing a weight and space-optimized gear with the lowest possible losses for an electric vehicle transmission and an electric vehicle transmission and an electric vehicle, which are preferably also suitable for use with a helical gearing.
  • an electric vehicle transmission and an electric vehicle are to be created which, due to their properties in terms of low weight and high stability, are suitable for use in electric motorsport even at very high speeds.
  • a toothed wheel for an electric vehicle transmission with: a toothed ring with external teeth;
  • a gear foot to connect the gear to a gear component in a rotationally fixed manner; and a web extending radially between the gear base and the gear ring; wherein the web has at least two axially spaced support points for supporting the toothed ring, the axial spacing of which is greater than a mean axial wall thickness of the web;
  • the web in a radially inner area has an axial extent that is less than or equal to an axial extent of the toothed ring.
  • an electric vehicle transmission for an electric vehicle with a gear arrangement made up of a predefined gear and a pinion which is in mesh with the gear, wherein
  • the pinion can be drive-connected to an electric drive machine; and a center distance between a center of the pinion and a center of the gear wheel in the range from 14.50 cm to 20.00 cm, preferably in the range from 17.00 cm to 18.50 cm, and particularly preferably in the range of 17.50 cm to 18.00 cm.
  • an electric drive machine wherein a pinion is non-rotatably arranged on an output shaft of the electric drive machine and meshes with the gear in order to translate drive power of the electric drive machine.
  • the toothed ring can advantageously be supported.
  • the lever one over the toothed ring on the force acting on the web is reduced.
  • the gear is more resistant.
  • a web that is optimized in terms of weight and at the same time resistant can be created.
  • a web, which in a radially inner area has an axial extent that is less than or equal to an axial extent of the toothed ring, enables a gearwheel that is narrow in the radial direction and therefore space-efficient.
  • a drive train for the electric vehicle can be constructed relatively easily with a few parts by a rotationally fixed connection of an output shaft of the electrical drive machine with the pinion and a rotationally fixed connection of a differential to the gear. Furthermore, this structure leads to a weight-optimized drive train, since additional gears can be dispensed with.
  • the web has a first and a further partial web.
  • An axial distance between the support points is determined by the first and the further partial web.
  • the first partial web and the further partial web are at least partially spaced apart from one another in the axial direction.
  • the first partial web and the further Lower part of the bridge is essentially constructed identically. This can simplify the manufacture of the gear.
  • the first partial web and / or the further partial web is positively, frictionally and / or non-positively connected to the toothed ring, preferably by gluing, screwing, pressing and / or welding the toothed ring to the first partial web and / or the further partial web.
  • At least the first partial web and / or the further partial web is formed integrally with the toothed ring.
  • the gear can be built with fewer individual parts, which makes the assembly faster, more efficient and less expensive, since at least some of the connecting means can be dispensed with.
  • the first partial web and the further partial web run parallel in the radial direction.
  • a gear with little axia len space requirement can be created.
  • the manufacture of the gear is simplified since no complex geometries have to be implemented for the partial webs. The gear can thereby be manufactured cost-effectively.
  • the web has a reinforcement running between the toothed ring and the toothed wheel base.
  • the web preferably has a decreasing mean axial length towards a gear center point.
  • An axial distance between the support points is determined by the reinforcement. This allows the gear to be specifically reinforced at weak points. It can also be provided to retrofit gear wheels with reinforcements in order to increase the resistance.
  • a narrow and weight-optimized gear can be created due to the cross-section which tapers inwards towards the center of the gear.
  • the web has a wave-like profile in the circumferential direction. An axial distance between the support points is determined by an axial extension of the wave-like course. In this way, a one-piece web can be created which has increased stability in relation to an axially acting force.
  • the gear can be formed from a technically simple and with a few components. The weight of the gear can be further reduced.
  • an axial distance between the support points corresponds to an axial extension of the toothed ring.
  • Support of the toothed ring can hereby be further improved. By supporting it at the outer ends of the toothed ring, there is a large lever to counteract an axial force.
  • the web has recesses, which are preferably repeated in the circumferential direction.
  • the external toothing has a module in the range from 1.0 mm to 1.8 mm, preferably in the range from 1.0 mm to 1.53 mm, and particularly preferably from 1.51 mm. Additionally or alternatively, the external toothing has a helical toothing with a helical toothing angle ⁇ (beta) in the range from 5 ° to 45 °, preferably in the range from 15 ° to 35 °, and particularly preferably in the range from 20 ° to 30 °. Additionally or alternatively, the gear wheel has an outer diameter in the range from 26 cm to 34 cm, in particular in the range from 28 cm to 32 cm, and particularly preferably from 31.48 cm.
  • the external toothing has a tooth height in the range from 1.0 mm to 2.5 mm, in particular in the range from 1.2 mm to 2.0 mm, and particularly preferably from 1.5 mm.
  • the gear is made of metal, in particular case-hardened steel.
  • a preferred compromise can be found between the manufacturability of the gearwheel, transmission of sufficient drive force / torque and reduction of the gearbox losses.
  • Choosing a helical toothing with a helical toothing angle ⁇ (beta) in the range of 5 ° to 45 ° can improve running smoothness and reduce noise, since each tooth pair runs with a continuous transition into and out of mesh and thus the transmission of the torque runs more evenly.
  • a helical toothing with a helical toothing angle ⁇ (beta) in the range of 15 ° to 35 ° a preferred range can be found that allows smooth running and low noise levels to be achieved without having to accept high axial forces must be supported by appropriate bearings and gear geometries.
  • a helical toothing with a helical toothing angle ⁇ (beta) in the range of 20 ° to 30 ° a preferred compromise can be found between the dimensioning of the bearings and the gear and adequate running.
  • a gear diameter in the range mentioned above particularly high gear ratios can be presented. Sufficient tooth engagement can be achieved by choosing the tooth height of the gearwheel in the range from 1.0 mm to 2.5 mm.
  • the tooth height in the range from 1.2 mm to 2.0 mm, a compromise can be found between the manufacturability of the gear and sufficient tooth engagement.
  • the gear wheel By choosing a tooth height of 1.5 mm, the gear wheel can have sufficient tooth engagement with efficient producibility. In addition, the rolling losses of the teeth of the gear and thus of the electric vehicle transmission are low.
  • the resistance of the gear By making the gear from metal, preferably case-hardened steel, the resistance of the gear can be increased.
  • the external toothing has a spur gear toothing or a bevel toothing.
  • the external toothing is preferably designed in the form of an involute toothing and particularly preferably with a profile shift.
  • the electric vehicle transmission has a single gear stage, which is set up by means of the gear arrangement.
  • the electric vehicle transmission can be constructed simply with a few parts.
  • this structure leads to a weight-optimized electric vehicle transmission, since further gears can be dispensed with.
  • the number of tooth meshes can be reduced, whereby transmission losses are reduced.
  • the transmission can be made narrower, cheaper and more efficient.
  • the overall efficiency can be very high, especially over 99%.
  • the gear arrangement forms a gear ratio in the range of greater than 5.5, preferably greater than 8, and particularly preferably equal to 8.9.
  • a gear ratio of greater than 5.5 for the gear arrangement, a high gear ratio can be achieved with only one gear pair.
  • a torque or speed translation can be displayed in a wide range with just one Zahnradan order.
  • a high translation of the torque of a high-torque electric drive machine can be achieved.
  • the speed of an electric drive machine can be reduced to a high level.
  • a high reduction ratio is particularly advantageous for racing cars that are designed for maximum speed and lightweight construction. Racing cars are preferably equipped with light electric drive machines that reach high speeds.
  • a ratio of 8.9 represents a compromise between a quick start and an achievable maximum speed depending on the speed of the electric drive machine Transmission ratio of 8.9 an advantageous ratio of weight and transmission.
  • the gear wheel according to the invention can also be used advantageously for setting up a gear stage in other areas of application.
  • an application in rail transport trains, trams, etc.
  • in wind power gearboxes for wind turbines
  • armaments shafts, large equipment, etc.
  • water vehicles pleasure boats, cargo ships, etc.
  • the advantages of the gear wheel according to the invention can also be used in these application areas.
  • the module m is the ratio between the pitch circle diameter of the gear and the number of teeth on the gear.
  • the pitch circle diameter is the diameter of an invisible cylinder that runs through the center of the teeth.
  • the pitch circle is defined as a circle with its center point on the gear axis that runs through the pitch point of the gear teeth. This pitch point is located between the foot of the gear tooth (root circle diameter) and the head of the gear tooth (tip circle diameter).
  • the module is therefore a measure of the distance between two neighboring gear teeth.
  • the gear wheel diameter or outer diameter is to be understood in the present case in particular as the tip diameter.
  • Gears can be designed and manufactured with a profile shift.
  • the shape of the teeth is changed without changing the underlying base curve.
  • a different part of the same curve is used as the tooth flank compared to a gear without a profile shift.
  • recuperation brake also called regenerative brake, works like any electrodynamic brake without wear.
  • the braking effect comes about when the traction motors are operated as electrical generators.
  • the electrical energy can be im Vehicle can be held in front of, for example, an accumulator or high-performance capacitor.
  • a honeycomb pattern and / or waffle pattern is preferably formed by at least one group of cutouts, the group of cutouts being formed by a repeating basic shape.
  • the group of cutouts being formed by a repeating basic shape.
  • two basic forms of a group can be mapped onto one another.
  • the recesses can be continuous and / or depressions in a disk.
  • CFRP is to be understood as carbon fiber or carbon fiber (abbreviated carbon fiber, carbon or carbon).
  • Carbon fibers can be embedded in a fabric matrix.
  • the matrix is used to connect the fibers and to fill the spaces in between. This creates a robust and lightweight material that is used in particular in motorsport.
  • Epoxy resin is usually chosen as the matrix.
  • other thermosets or thermoplastics are also possible as matrix material.
  • Wave-like is to be understood as a geometry in which a web has a profile with peaks and valleys in a circumferential plane or in the circumferential direction. The web is thus deformed in the axial direction.
  • a wave crest and / or wave trough are essentially oriented radially.
  • wave-like also includes, inter alia, trapezoidal, triangular, sinusoidal and / or circular wave geometries.
  • FIG. 1 shows a schematic representation of an electric vehicle with an electric vehicle transmission with a gear according to the present invention
  • FIG. 2 shows a schematic illustration of a gear wheel according to the invention in a first embodiment
  • 3 shows a schematic representation of a gear wheel according to the invention in a second embodiment
  • FIG. 4 shows a schematic representation of a gear wheel according to the invention in a third embodiment
  • FIG. 5 shows a schematic sectional illustration of the gear wheel from FIG. 4;
  • FIG. 6 shows a schematic representation of a gear wheel according to the invention in a fourth embodiment
  • FIG. 7 shows a schematic sectional illustration of the gear wheel of FIG. 6.
  • FIG. 8 shows a schematic side view of the gear wheel from FIG. 6.
  • FIG. 1 an electric vehicle 10 with drive wheels 12, a drive shaft 14 in operative connection with the drive wheels 12 and a drive train 16 is shown schematically.
  • the figure corresponds to a plan view.
  • the relevant components are enlarged and not shown to scale.
  • the drive train 16 has an electric vehicle transmission 18 with a gear pair with a gear 20 according to the present application, an electric drive machine 22 and a transmission component 24.
  • the gear component 24 is a differential.
  • the electric drive machine 22 is in operative connection with a pinion 26 which is non-rotatably arranged on an output shaft 28 of the electric drive machine 22.
  • the pinion 26 is in engagement with a toothed ring 30 of the gear 20, which is arranged on the gear component 24 in a rotationally fixed manner.
  • a drive force can be transmitted to the drive wheels 12 through the transmission component 24, which includes a differential.
  • the pinion 26, the gear 20 and the Ge transmission component 24 can be accommodated in a gear housing 32.
  • Fig. 2 shows a schematic representation of a gear 20 according to the present application in a first embodiment.
  • the gear 20 has the toothed ring 30, which in this example rotates by means of a screw 34 on a web 36 is fixed.
  • the web 36 has a first partial web 38 and a further partial web 40 and is arranged on the transmission component 24.
  • An axial distance D between two support points S1, S2 for the toothed ring 30 is determined by the axial distance and the wall thickness of the first partial web 38 and the further partial web 40.
  • the gear 20 is designed as a spur gear.
  • the toothed ring 30 thus has an external toothing 42 in the form of a spur gear toothing.
  • the first partial web 38 and the further partial web 40 are connected to the transmission component 24 in a rotationally fixed manner by means of a screw. This example is the first
  • Partial web 38 is designed symmetrically to the further partial web 40.
  • the outer toothing 42 can also be designed in the form of helical toothing.
  • high forces are exerted in the axial direction during operation on the gear 20.
  • the symmetrical structure of the first partial web 38 and the further partial web 40 leads to a constant resistance of the gear 20 inde pendent of the direction of rotation.
  • a weight-optimized bar can be created.
  • the wall thickness can be varied, preferably selected to be smaller, if a lower axial force is to be expected.
  • FIG. 3 shows a schematic illustration of a gear 20 according to the invention. The differences to the embodiment shown in FIG. 2 are discussed here. The same reference numerals refer to the same features and who will not be explained again.
  • the gear wheel 20 of FIG. 3 has a first partial web 38 and another
  • Partial web 40 the first partial web 38 being formed integrally with the toothed ring 30.
  • the further partial web 40 is connected to the toothed ring 30 in the example shown. welded or glued. It goes without saying that a mechanical connection, for example by means of a snap ring or hooking the further partial web 40 into the toothed ring 30, for example by means of a claw or crown toothing, is also conceivable.
  • the first partial web 38 and the further partial web 40 have an essentially parallel course in the radial direction.
  • the wall thickness of the two partial webs 38, 40 is essentially the same.
  • first partial web 38 and / or the further partial web 40 with recesses, which are preferably formed continuously in order to further minimize the weight of the gear 20.
  • provision can also be made to attach a reinforcement structure or a reinforcement means 43 to the first partial web 38 and / or the further partial web 40, for example in the form of a disk with a honeycomb and / or waffle pattern.
  • This disk can be glued onto at least one of the partial webs 38, 40, welded to it or formed integrally with one of the partial webs 38, 40. It is also conceivable to emboss such a disk in a partial web 38, 40 or to print or laminate it onto it. In general, any method known in the prior art is conceivable.
  • the gear wheel 20 is connected in a rotationally fixed manner by means of a screw 44 on a radial outside of a transmission component 24, which is a differential in the example shown.
  • the differential distributes drive power, which is made available to the differential by means of the gear 20, to the drive shaft 14.
  • a representation of a transmission housing and bearings and a detailed representation of the differential components have been omitted.
  • FIG. 4 shows a schematic representation of a gear 20 according to the invention in a third embodiment.
  • the figure shows a plan view in the axial direction.
  • the gear 20 has on its web 36 radially extending reinforcement gen 46 on. These radially extending reinforcements 46 extend in the axial direction and taper radially inward, that is to say towards a gear base 48.
  • a total of eight reinforcements 46 are shown. It will be understood that the number of reinforcements 46 can vary. The number of reinforcements 46 here preferably corresponds to the number of screwing points of the gear 20 with the transmission component 24.
  • the reinforcements 46 are designed to be mirror-symmetrical to a radial plane of the gear 20.
  • the reinforcements 46 can be glued onto the web 36, welded to it or formed integrally with the web 36. It goes without saying that such reinforcements 46 can also be created from a solid part by embossing or milling. In particular, it is also conceivable that the reinforcements 46 are designed in the form of spokes which can be spaced apart from the web 36 at least at a radially outer end thereof.
  • FIG. 5 a sectional illustration of the gear 20 from FIG. 4 is shown schematically.
  • the web 36 with the reinforcements 46 is triangular in the illustrated sectional view, with a tip of the triangle pointing radially inward.
  • a large axial distance D between two support points S1, S2 can be created for the toothed ring 30 and a toothed wheel 20 optimized in terms of weight can be created.
  • a force acting in the axial direction on the toothed ring 30 can advantageously be supported.
  • FIG. 6 shows a schematic representation of a gear wheel 20 according to the invention in a fourth embodiment.
  • the figure corresponds to a plan view in the axial direction.
  • the gear 20 has a web 36 which runs between the gear ring 30 and the gear base 48.
  • the web 36 has in the circumferential direction a wellenarti gene course, which is represented by a high or low density of radially extending ge dashed lines.
  • the wave-like profile thus has wave crests 50 and wave troughs 52.
  • a high axial distance between two support points of the web 36 can also be achieved. It is conceivable to arrange the corrugation valleys and corrugation peaks according to the screw connection points or tion points of the gear 20 with the gear component, not shown, on the gear base 48 to choose.
  • FIG. 7 shows a sectional illustration of the gear wheel from FIG. 6.
  • the section runs through a wave crest 50 or a wave trough 52.
  • wave crest 50 is used below.
  • the wave crest 50 has an axial expansion at a radially outer end resting against the toothed ring 30, which corresponds to the axial expansion of the toothed ring 30.
  • the web 36 is connected flush with the toothed ring 30 at one axial end thereof.
  • FIG. 8 A side view of the gear wheel of FIG. 6 is shown schematically in FIG. 8.
  • the Fi gur corresponds to a radial plan view of the gear 20.
  • the course of the web 36 in the circumferential direction is shown in dashed lines.
  • the sinusoidal wave shape shown here can also have a triangular, trapezoidal or other geometry in the circumferential direction.
  • the axial distance D between two support points S1 and S2 is determined by the axial extent of a wave crest 50 and wave valley 52.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Thermal Sciences (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)

Abstract

La présente invention concerne une roue dentée (20) pour une transmission de véhicule électrique (18) comprenant : une couronne dentée (30) munie d'une denture extérieure (42) ; une base de roue dentée (48) pour relier la roue dentée de manière non rotative à un composant de transmission (24) ; et une nervure (36) s'étendant radialement entre la base de la roue dentée et la couronne dentée, la nervure comportant au moins deux points d'appui (S1, S2) espacés axialement pour supporter la couronne dentée dont la distance axiale (D) est supérieure à une épaisseur de paroi axiale moyenne de la nervure ; et ladite nervure comprend une extension axiale dans une zone radialement intérieure qui est inférieure ou égale à une extension axiale de la couronne dentée. L'invention concerne également une transmission de véhicule électrique pourvue d'une telle roue dentée et un véhicule électrique (10) pourvu d'une telle transmission de véhicule électrique.
PCT/EP2020/055601 2019-04-17 2020-03-04 Roue dentée pour transmission de véhicule électrique Ceased WO2020212011A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019205599.0A DE102019205599A1 (de) 2019-04-17 2019-04-17 Zahnrad für Elektrofahrzeuggetriebe
DE102019205599.0 2019-04-17

Publications (1)

Publication Number Publication Date
WO2020212011A1 true WO2020212011A1 (fr) 2020-10-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2020/055601 Ceased WO2020212011A1 (fr) 2019-04-17 2020-03-04 Roue dentée pour transmission de véhicule électrique

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DE (1) DE102019205599A1 (fr)
WO (1) WO2020212011A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2729703A1 (de) * 1977-07-01 1979-01-04 Winkelmann & Pannhoff Gmbh Zahnriemenscheibe aus kunststoff mit metallnabe
US5347880A (en) * 1992-11-23 1994-09-20 Harnischfeger Corporation Method and apparatus for servicing a gear assembly
US20100307845A1 (en) * 2008-02-14 2010-12-09 Hisashi Ogata Hybrid electric automobile
DE102014000499A1 (de) * 2014-01-16 2015-07-16 Daimler Ag Differentialgetriebe für ein Kraftfahrzeug
DE102015220521A1 (de) * 2014-10-22 2016-04-28 Musashi Seimitsu Industry Co., Ltd. Differenzialgetriebe
US20160363206A1 (en) * 2015-06-10 2016-12-15 Bell Helicopter Textron Inc. Composite and metal hybrid gear
DE102016010084A1 (de) * 2015-10-01 2017-04-06 Sew-Eurodrive Gmbh & Co Kg Zahnrad mit Schrägverzahnung und Segment für ein Zahnrad

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE137602C (fr) *
DE29923513U1 (de) * 1999-09-16 2000-11-30 H.B. Seissenschmidt AG, 58840 Plettenberg Zahnrad
JP2003191288A (ja) * 2001-12-25 2003-07-08 Toray Ind Inc プラスチック成形品
CN101487519B (zh) * 2008-09-18 2015-03-25 孟良吉 全齿轮速度自适应无级变速器
DE102009023720A1 (de) * 2009-06-03 2010-12-09 Neumayer Tekfor Holding Gmbh Zahnrad

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2729703A1 (de) * 1977-07-01 1979-01-04 Winkelmann & Pannhoff Gmbh Zahnriemenscheibe aus kunststoff mit metallnabe
US5347880A (en) * 1992-11-23 1994-09-20 Harnischfeger Corporation Method and apparatus for servicing a gear assembly
US20100307845A1 (en) * 2008-02-14 2010-12-09 Hisashi Ogata Hybrid electric automobile
DE102014000499A1 (de) * 2014-01-16 2015-07-16 Daimler Ag Differentialgetriebe für ein Kraftfahrzeug
DE102015220521A1 (de) * 2014-10-22 2016-04-28 Musashi Seimitsu Industry Co., Ltd. Differenzialgetriebe
US20160363206A1 (en) * 2015-06-10 2016-12-15 Bell Helicopter Textron Inc. Composite and metal hybrid gear
DE102016010084A1 (de) * 2015-10-01 2017-04-06 Sew-Eurodrive Gmbh & Co Kg Zahnrad mit Schrägverzahnung und Segment für ein Zahnrad

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