EP3554933A1 - Transmission pour bicyclette - Google Patents

Transmission pour bicyclette

Info

Publication number
EP3554933A1
EP3554933A1 EP17804884.9A EP17804884A EP3554933A1 EP 3554933 A1 EP3554933 A1 EP 3554933A1 EP 17804884 A EP17804884 A EP 17804884A EP 3554933 A1 EP3554933 A1 EP 3554933A1
Authority
EP
European Patent Office
Prior art keywords
planetary
transmission
gear set
planetary gear
rotatably connected
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.)
Withdrawn
Application number
EP17804884.9A
Other languages
German (de)
English (en)
Inventor
Johannes Kaltenbach
Valerie Engel
Uwe Griesmeier
Matthias Nitsch
Michael Wechs
Jens Moraw
Gerhard Niederbrucker
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 EP3554933A1 publication Critical patent/EP3554933A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • B62M11/18—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears with a plurality of planetary gear units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
    • B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
    • B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
    • B62M11/145—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears built in, or adjacent to, the bottom bracket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • B62M6/00—Rider propulsion of wheeled vehicles with additional source of power, e.g. combustion engine or electric motor
    • B62M6/40—Rider propelled cycles with auxiliary electric motor
    • B62M6/55—Rider propelled cycles with auxiliary electric motor power-driven at crank shafts parts
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears

Definitions

  • the invention relates to a transmission for a bicycle, with at least four switching elements, a drive shaft, a first planetary set, which is operatively connected to the drive shaft, a second planetary set, which is operatively connected to the drive shaft, and an output shaft.
  • the invention relates to a bottom bracket with such a transmission. Moreover, the invention relates to a bicycle with the bottom bracket or the transmission.
  • US 201 1 177 91 1 A1 discloses a transmission that has three series-connected planetary gear with a speed ratio.
  • the transmission has a total of seven planetary gear plane, including numerous stepped planets, so that the construction cost of the transmission is very high.
  • the object of the invention is therefore to provide a transmission which has a low construction cost.
  • the object is achieved by a transmission of the type mentioned, which is characterized in that the drive shaft is rotatably connected to a ring gear of the first planetary gear set and which is rotatably connected to a web of the first planetary gear set.
  • the transmission according to the invention has the advantage that a 4-speed transmission can be provided which does not require stepped stages.
  • the transmission has a simple and compact structure and the assembly of the transmission can be done quickly.
  • the transmission has a good efficiency and can be produced inexpensively.
  • the transmission according to the invention also has the advantage that it is suitable for a bicycle application, in particular in conjunction with an upstream or downstream group described in more detail below.
  • Under a shaft is not exclusive to understand, for example, a cylindrical, rotatably mounted machine element for transmitting torque, but these are also general connecting elements to understand that connect individual components or elements together, in particular connecting elements that connect a plurality of elements rotationally fixed to each other.
  • the first planetary gearset may be a plus planetary gearset and / or the second planetary gearset may be a minus planetary gearset.
  • a minus planetary gear set corresponds to a planetary gear set with a web on which the planet gears are rotatably mounted, a sun gear and a ring gear, wherein the teeth of at least one of the planetary gears meshes with both the teeth of the sun gear and with the teeth of the ring gear, whereby the ring gear and rotate the sun gear in the opposite direction when the sun gear is rotating at a fixed land.
  • a plus planetary set differs from the minus planetary set in that the plus planetary set has inner and outer planetary gears rotatably supported on the bridge.
  • the toothing of the inner planet gears meshes on the one hand with the teeth of the sun gear and on the other hand with the teeth of the outer planetary gears.
  • the toothing of the outer planetary gears also meshes with the teeth of the ring gear. This has the consequence that rotate at fixed land, the ring gear and the sun gear in the same direction.
  • a sun gear of the second planetary gear set can be rotatably connected to the drive shaft by means of a first switching element of the at least four switching elements.
  • the sun gear by means of a second switching element of at least four switching elements with a transmission housing rotatably connected.
  • a web of the second planetary gear set may be rotatably connected to a sun gear of the first planetary gear set.
  • a ring gear of the second planetary gearset can be connected in a rotationally fixed manner to the transmission housing by means of a third shifting element of the at least four shifting elements.
  • the ring gear of the second planetary gear set by means of a fourth Switching element of the at least four switching elements with the output shaft rotatably connected.
  • the gear housing may be part of a bottom bracket, so be carried out in one piece with the bottom bracket shell.
  • the transmission housing may be designed separately from the bottom bracket shell and be arranged in the assembled state of the transmission in a cavity of the bottom bracket.
  • the gear housing may be arranged and designed such that it does not rotate during operation of the transmission, but is stationary.
  • the first planetary gearset and the second planetary gearset may be arranged such that the drive shaft does not extend through a plane having the second planetary gearset.
  • the first planetary gearset and the second planetary gearset may be arranged such that the drive shaft extends through the plane having the second planetary gearset.
  • the plane may include the ring gear, the land and the sun gear of the second planetary gearset.
  • the transmission according to the invention has the advantage that the switching elements for an actuator are easily accessible.
  • the second and third switching element can be designed as a brake and / or arranged in a radially outer region of the transmission, which simplifies the accessibility.
  • the first and fourth switching element can each be designed as a clutch or freewheel.
  • the first and fourth switching element in each case as a freewheel advantageously no switching operation or actuator is necessary.
  • the first and fourth switching element only have to apply low support moments, so that the freewheels can be made small.
  • the drive shaft can be rotatably connected to the bottom bracket crankshaft.
  • the output shaft may be rotatably connected to a Switzerlandstoffchu, such as a sprocket or a pulley. It can when using the transmission in the bicycle, a torque applied to the traction means carrier by means of a traction means, such as a chain or a belt, are transmitted to a rear wheel.
  • a transmission is realized in which exactly four gears can be provided by exactly two planetary gear sets and / or exactly four switching elements.
  • a first gear can be a direct gear, ie has a ratio of 1.
  • the remaining gears can have a translation into the fast, so a translation of less than 1.
  • the transmission may include a third planetary gearset that is operatively connected to the first planetary gearset and / or second planetary gearset.
  • the third planetary gear set may be upstream or downstream of the first and second planetary gear set.
  • the third planetary gear set may be a minus planetary gear set.
  • An element of the third planetary gearset can be connected in a rotationally fixed manner to another element of the third planetary gearset by means of a fifth shifting element.
  • a closed fifth switching element of the third planetary gear set is blocked, so has a ratio of 1 on.
  • the ring gear of the third planetary gear set is rotatably connected by means of the fifth switching element with the sun gear of the third planetary gear set. This is advantageous since, in this case, small supporting moments are to be applied by the fifth switching element.
  • the ring gear of the third planetary gearset can be rotatably connected by means of a sixth switching element with the transmission housing.
  • the sixth switching element can be designed as a brake and the fifth switching element as a clutch or freewheel.
  • the third planetary gear set may be connected upstream of the first and second planetary gear set in a traction mechanism operation of the transmission, thus forming a front-end group.
  • the drive shaft, the first planetary gear set, the second planetary gear set, the output shaft and the four shift elements form a main group in this embodiment.
  • a web of the third planetary gearset can be connected in a rotationally fixed manner to the bottom bracket crankshaft by means of a further drive shaft, and a sun gear of the third planetary gearset can be rotatably connected to the drive shaft.
  • the output shaft may be rotatably connected to the traction means.
  • the third planetary gear set is downstream of the first and second planetary gear set in a traction mechanism operation of the transmission, ie forms a rear-mounted group.
  • the drive shaft, the first planetary gear set, the second planetary gear set, the output shaft and the four shift elements form a main group in this embodiment.
  • the output shaft may be rotatably connected to the web of the third planetary gear set and the sun gear of the third planetary gear set may be rotatably connected to a further output shaft.
  • the further output shaft may be rotatably connected to the traction means.
  • the drive shaft with the bottom bracket crankshaft rotatably connected.
  • the front group or rear group can provide exactly two gears and / or exactly two switching elements, namely the fifth and sixth switching element, have.
  • a first gear may be a direct gear and a second gear may have a gear ratio to the quick.
  • the front group or rear group can have exactly one planetary set, namely the third planetary set.
  • the third planetary gear set does not have a stepped planet.
  • the clutches or brakes used in the gearbox can be designed to be positive or frictional. If the above-mentioned switching elements are designed as freewheels, it is advantageous that on the one hand the main group and / or on the other hand, the upstream or downstream group not blocked to prevent blocking of the transmission when reversing the direction of the drive or the output. This can be realized in that the fifth switching element of the Vorschalt- or Nachschalttica and / or the second and third switching element of the main group are designed as a single-acting brake, such as a switchable freewheeling brake.
  • an 8-speed transmission can be realized.
  • the transmission is advantageous because eight gears can be realized with exactly three planetary gear sets, so that the transmission has a small overall length.
  • the transmission has suitable values for the stand ratios, so that the planetary gear sets can have a small diameter.
  • Another advantage is that exactly three switching elements can be designed as brakes. The remaining switching elements can be designed as freewheels. This is advantageous since at least one, in particular exactly three, actuators for operating the three designed as a brake switching elements must be present.
  • the transmission may comprise an electric machine, which is downstream of the first and / or second and / or third planetary gear set.
  • the electric machine can be used with the drive shaft or the other output shaft operatively operatively connected.
  • the drive technical downstream of the electric machine has the advantage that the planetary gear sets are not burdened with the torque provided by the electric machine.
  • the electric machine also has the advantage that it can support the cyclist while driving. As a result, a fine gear gradation is not necessary because due to the electric machine, the muscle power has little importance for the drive.
  • the electric machine consists at least of a non-rotatable stator and a rotatably mounted rotor which is arranged in a motor operation to convert electrical energy into mechanical energy in the form of speed and torque, and in a regenerative operation mechanical energy into electrical energy in the form of To transform electricity and voltage.
  • the electric machine can, in particular in the radial direction, be arranged offset to a central axis of the transmission and / or the bottom bracket crankshaft.
  • a central axis of the electric machine can run parallel to a central axis of the transmission. This offers the advantage that the electric machine can be arranged in a region of the transmission and / or the bottom bracket shell, in which sufficient space for receiving the electric machine is available.
  • an inner diameter of the electric machine can be chosen freely, since the non-gearbox crankshaft bearing crankshaft does not pass through the electric machine.
  • connection of the electric machine to the output shaft or further output shaft can be done by means of a chain drive and / or belt drive and / or a spur gear and / or a transmission gear.
  • a freewheel can be arranged in the power flow between the electric machine and the output shaft or the other output shaft.
  • the freewheel has the advantage that during operation without electrical machine no losses caused by the rotating rotor of the electric machine.
  • a bottom bracket with the transmission according to the invention wherein the drive shaft or the further drive shaft is rotatably connected to the bottom bracket crankshaft.
  • the bottom bracket may have a bottom bracket shell, wherein the transmission is arranged in a cavity of the bottom bracket.
  • the transmission can be modular. Therefore, the transmission as a whole can be inserted or removed from the cavity.
  • a bicycle with the gear or the bottom bracket is a bicycle with the gear or the bottom bracket.
  • FIGS. 1 and 2 show a switching matrix of the gears shown in FIGS. 1 and 2,
  • FIG. 5 shows a schematic representation of the transmission according to the invention according to a fourth embodiment
  • Fig. 1 shows an inventive transmission according to a first embodiment, which is rotationally symmetrical with respect to a bottom bracket crankshaft 5. In Fig. 1, only the upper half of the transmission is shown.
  • the transmission has four switching elements, namely a first switching element S1, a second switching element S2, a third switching element S3 and a fourth switching element S4.
  • the first and fourth switching elements S1, S4 are designed as clutches.
  • the second and third switching elements S2, S3 are designed as brakes.
  • the transmission has a drive shaft 1, a first planetary set PS1, which is operatively connected to the drive shaft 1, a second planetary gear set PS2 and an output shaft 2.
  • the drive shaft 1 is rotatably connected to a ring gear of the first planetary gearset PS1 and a web of the first planetary gearset PS1 is rotatably connected to the output shaft 2.
  • the output shaft 2 is arranged coaxially to the bottom bracket crankshaft 5 and rotatably connected to a traction means carrier, not shown.
  • the first planetary gearset PS1 is designed as a plus-planetary gearset and the second planetary gearset PS2 is designed as a minus-planetary gearset.
  • the drive shaft 1 is rotatably connected by means of the first switching element S1 with a sun gear of the second planetary gear set PS2.
  • the sun gear of the second planetary gearset PS2 is additionally rotatably connected by a second switching element S2 with a transmission housing 3.
  • a web of the second planetary gearset PS2 is rotatably connected to a sun gear of the first planetary gear set PS1.
  • a ring gear of the second planetary gearset PS2 is connected in a rotationally fixed manner to the transmission housing 3 by means of a third shifting element S3 and can be connected in a rotationally fixed manner to the output shaft 2 by means of the fourth shifting element S4.
  • the first and second planetary gear sets PS1, PS2 are arranged coaxially with each other.
  • the first and second planetary gear set PS1, PS2 are arranged coaxially with the bottom bracket crankshaft 5.
  • the first and second planetary gear set PS1, PS2 are arranged such that the drive shaft 1 for connecting to the ring gear of the first planetary gearset PS1 extends through a plane E therethrough.
  • the plane E is perpendicular to the bottom bracket crankshaft. 5
  • the transmission is arranged in a cavity of a bottom bracket 9.
  • the transmission shown in Fig. 1 forms a main group HG, which, as can be seen from Figures 4 and 5, is operatively connected to other area groups.
  • Fig. 2 shows a transmission according to a second embodiment.
  • the transmission shown in Fig. 2 differs from the transmission shown in Fig. 1 in the arrangement of the first and second planetary gear set PS1, PS2 relative to each other.
  • the second planetary gear set PS2 is arranged such that the drive shaft 1 does not extend through the plane E for connection to the ring gear of the first planetary gearset PS1.
  • Fig. 3 shows the switching matrix for the transmission shown in Figures 1 and 2. It is characterized by the character “x” that the respective switching element is closed ..
  • the switching matrix for each gear ratio "i" between the drive shaft 1 and the output shaft 2 and thus called the traction means.
  • the transmission has exactly four gears, wherein a first gear is a direct gear.
  • the remaining gears have a translation in quick.
  • the first planetary gearset PS1 may have a gear ratio of 2.0 and the second planetary gearset PS2 may have a gear ratio of -1, 6.
  • the stand translation corresponds to a minus planetary gear set the negative gear ratio of ring gear and sun. With a plus planetary gear set, the gear ratio corresponds to the positive gear ratio of gear and sun.
  • Fig. 4 shows the transmission according to a third embodiment.
  • the transmission differs from the transmission shown in FIG. 1 in that the transmission has a third planetary gearset PS3, which forms a front-gear group VG, which is upstream of the main group HG.
  • the third is Planet set PS3 upstream of the first planetary gearset PS1 and the second planetary gearset PS2, when considering a power flow from the bottom bracket crankshaft 5 to the output shaft 2 in a train operation.
  • a ring gear of the third planetary gearset PS3 is rotatably connected by means of a fifth switching element S5 with a sun gear of the third planetary gear set PS3.
  • the ring gear of the third planetary gearset PS3 by means of a sixth switching element S6 with the transmission housing 3 rotatably connected.
  • a web of the third planetary gearset PS3 is rotatably connected by means of a further drive shaft 6 with the bottom bracket crankshaft 5.
  • the sun gear of the third planetary gearset PS3 is rotatably connected to the drive shaft 1.
  • the fifth switching element S5 is designed as a freewheel and the sixth switching element S6 is designed as a brake. Another difference to the transmission shown in Fig. 1 is that the first switching element S1 and fourth switching element S4 are each designed as a freewheel.
  • the transmission shown in Fig. 5 according to a fourth embodiment differs from the transmission shown in Fig. 4 in that the third planetary gear set PS3 not a Vorschaltement VG, but forms a Nachschaltxx NG.
  • the third planetary gear set PS3 of the main group HG is downstream of the drive technology when considering the power flow from the bottom bracket crankshaft 2 to a further output shaft 7 in a traction operation.
  • the output shaft 2 is rotatably connected to the web of the third planetary gearset PS3.
  • the sun gear of the third planetary gearset PS3 is rotatably connected to the further output shaft 7, which is rotatably connected to the traction means carrier, not shown in the figure.
  • the drive shaft 1 is rotatably connected to the bottom bracket crankshaft 5.
  • the transmission has an electric machine 8, which is operatively connected to the output shaft 7, as shown by the dashed line.
  • the connection of the electric machine 8 with the Ab- Drive shaft 7 can be made via a superposition gear, a spur gear, a chain drive and / or a belt drive, wherein the connection in Fig. 4 is not shown. In this case, the connection of the electric machine 8 in one of the rear-NG NG droving technically downstream area.
  • the electric machine 8 is not rotationally symmetrical to the bottom bracket crankshaft 5.
  • the electric machine 8 is arranged offset in the radial direction to the bottom bracket crankshaft 5.
  • the transmission has a torque sensor 4, by means of which the transmitted from the bottom bracket crankshaft 5 to the drive shaft 1 torque can be measured.
  • the torque sensor 9 may be designed disk-shaped. Of course, another embodiment and / or arrangement of the torque sensor 9 is possible.
  • FIG. 6 shows a table with values for the state translation of the three planetary gear sets shown in FIGS. 4 and 5.
  • the first planetary gear set PS1 has a stand ratio of 2.0
  • the second planetary gear set PS2 has a gear ratio of -1.6
  • the third planetary gear set PS3 has a gear ratio of -1.5.
  • FIG. 7 shows a switching matrix for the transmissions illustrated in FIGS. 4 and 5.
  • the symbol “x” denotes the switching elements which are closed in the respective gear, provided that the switching element is designed as a freewheel, the symbol “x” means that the freewheel locks. This is done automatically without external operation.
  • the switching elements designed as a brake are closed by at least one actuator.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une transmission pour bicyclette, comprenant au moins quatre éléments de changement de vitesse, un arbre d'entrée (1), un premier train épicycloïdal (PS1) qui coopère avec l'arbre d'entrée (1), un deuxième train épicycloïdal (PS2) qui peut coopérer avec l'arbre d'entrée (1), et un arbre de sortie (2). Ladite transmission est caractérisée en ce que l'arbre d'entrée (1) est relié solidaire en rotation à une couronne du premier train épicycloïdal (PS1) et l'arbre de sortie (2) est relié solidaire en rotation à un porte-satellites du premier train épicycloïdal (PS1).
EP17804884.9A 2016-12-15 2017-11-24 Transmission pour bicyclette Withdrawn EP3554933A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016225145.7A DE102016225145A1 (de) 2016-12-15 2016-12-15 Getriebe für ein Fahrrad
PCT/EP2017/080369 WO2018108487A1 (fr) 2016-12-15 2017-11-24 Transmission pour bicyclette

Publications (1)

Publication Number Publication Date
EP3554933A1 true EP3554933A1 (fr) 2019-10-23

Family

ID=60480310

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17804884.9A Withdrawn EP3554933A1 (fr) 2016-12-15 2017-11-24 Transmission pour bicyclette

Country Status (5)

Country Link
US (1) US20190382080A1 (fr)
EP (1) EP3554933A1 (fr)
CN (1) CN110072767A (fr)
DE (1) DE102016225145A1 (fr)
WO (1) WO2018108487A1 (fr)

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DE102018217883B4 (de) * 2018-09-25 2020-06-04 Zf Friedrichshafen Ag Antriebsanordnung für ein Fahrrad oder Pedelec
DE102019218617B4 (de) * 2019-11-29 2022-10-27 Zf Friedrichshafen Ag Getriebeanordnung für ein Fahrrad und ein Fahrrad
CN111071383B (zh) * 2020-01-09 2022-02-22 浙江大学 自行车轴传动多级变速装置
DE102021204634B3 (de) 2021-05-07 2022-08-18 Zf Friedrichshafen Ag Getriebe für ein Fahrrad und Fahrrad
DE102021208705B4 (de) 2021-08-10 2023-08-17 Zf Friedrichshafen Ag Radsatzanordnung und Fahrradgetriebe
DE102021209258A1 (de) 2021-08-24 2023-03-02 Zf Friedrichshafen Ag Getriebe für ein Fahrrad und Fahrrad
DE102021211853A1 (de) 2021-10-21 2022-11-24 Zf Friedrichshafen Ag Tretlagergetriebe für ein Mikromobilitätsfahrzeug
DE102022209138B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022209135B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022209141B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022209139B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022211598B4 (de) 2022-11-03 2024-05-29 Zf Friedrichshafen Ag Antriebsanordnung für ein Fahrrad oder Pedelec

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DE102013226473B4 (de) * 2013-12-18 2022-02-03 Zf Friedrichshafen Ag Getriebe

Also Published As

Publication number Publication date
US20190382080A1 (en) 2019-12-19
CN110072767A (zh) 2019-07-30
DE102016225145A1 (de) 2018-06-21
WO2018108487A1 (fr) 2018-06-21

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