EP3554934A1 - Transmission pour bicyclette - Google Patents

Transmission pour bicyclette

Info

Publication number
EP3554934A1
EP3554934A1 EP17807815.0A EP17807815A EP3554934A1 EP 3554934 A1 EP3554934 A1 EP 3554934A1 EP 17807815 A EP17807815 A EP 17807815A EP 3554934 A1 EP3554934 A1 EP 3554934A1
Authority
EP
European Patent Office
Prior art keywords
planetary
planetary gear
gear set
transmission
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Withdrawn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
EP17807815.0A
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 EP3554934A1 publication Critical patent/EP3554934A1/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Withdrawn legal-status Critical Current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
    • B62M11/145—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
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • 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
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4816—Electric machine connected or connectable to gearbox internal shaft
    • 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
    • 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
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four engaging means
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2071—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using three freewheel mechanism
    • 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
    • F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
    • F16H2200/2087—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches three freewheel mechanisms
    • 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
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Definitions

  • the invention relates to a transmission for a bicycle, with at least four switching elements, a drive shaft, a first planetary gear set, which is operatively connected to the drive shaft, and a second planetary gear set.
  • the invention relates to a bottom bracket with such a transmission. Moreover, the invention relates to a bicycle with the transmission or the bottom bracket.
  • the object of the invention is to provide a transmission that is simple and can be easily assembled.
  • the object is achieved by a transmission of the aforementioned type, which is characterized in that a web of the first planetary gear set is rotatably connected to a web of the second 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. In this case, the transmission has a simple structure and the assembly of the transmission can be done quickly. In addition, the transmission has a good efficiency.
  • the transmission according to the invention also has the advantage that it is suitable for a bicycle application, in particular in conjunction with a ballast or rear group described in more detail below.
  • a shaft Under a shaft is not exclusively an example cylindrical, rotatably mounted machine element for transmitting torque to understand but rather, 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 web of the first planetary gear set and the web of the second planetary gear set may be made in one piece.
  • the one-piece design offers the advantage that a common component can be used for both planetary gear sets, which reduces the cost of the transmission and simplifies the assembly.
  • the transmission is compact by the common component.
  • the first planetary gear set may be a plus planetary gearset and / or the second planetary gearset may be an inus 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 a fixed land, the ring gear and the sun gear in the same direction.
  • the drive shaft can rotatably connected to a ring gear of the first planetary gear set.
  • the drive shaft can be operatively connected to the second planetary gear set and operatively connected.
  • the drive shaft can be indirectly operatively connected to the web of the second planetary gear set by means of the first planetary gearset.
  • a ring gear of the second planetary gear set by means of a first switching element of at least four switching elements with the drive shaft rotatably connected and / or be rotatably connected by a second switching element of the at least four switching elements with a transmission housing.
  • a sun 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 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 designed and arranged such that it does not rotate during operation of the transmission, but is stationary.
  • An output shaft of the transmission may be operatively connected to the first planetary gearset.
  • the output shaft may be rotatably connected to a sun gear of the first planetary gear set.
  • the output shaft can be operatively connected to the second planetary gear set and operatively connected.
  • the output shaft by means of a fourth switching element of the at least four switching elements with a sun gear of the second planetary set can be rotatably connected.
  • a web of the second planetary gear set may be indirectly operatively connected to the output shaft by means of the first planetary gear set.
  • 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. In an embodiment of the first and fourth switching element in each case as a clutch, no switching operation or actuator is necessary. In addition, the first and fourth switching element on low supporting moments, so that the first and fourth switching element 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.
  • a torque applied to the traction means carrier can be transmitted to a rear wheel by means of a traction means, such as a chain or a belt.
  • 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 the 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.
  • a ring gear of the third planetary gearset can be rotatably connected by means of a fifth switching element with the transmission housing.
  • an element of the third planetary gear set by means of a sixth switching element with another element of the third planetary gearset be rotatably connected.
  • In a closed sixth switching element of the third planetary gear set is blocked, so has a ratio of 1 on.
  • the sixth switching element may be arranged such that the ring gear of the third planetary gear set is rotatably connected to a sun gear of the third planetary gear set. Such an arrangement has the advantage that the sixth switching element has to apply a small supporting moment. Of course, it is alternatively possible to arrange the sixth switching element such that a web of the third planetary gear set by means of the sixth switching element with the ring gear of the third planetary gear Tensatzes or rotatably connected to the sun gear of the third planetary gear set.
  • the fifth switching element can be designed as a brake.
  • the sixth switching element can be designed as a clutch or freewheel.
  • the third planetary gearset may be upstream of the first and second planetary gear set in a traction mode, ie form a ballast group.
  • the first and second planetary gear, the drive shaft, the output shaft and the four switching elements form a main group in this embodiment.
  • a web of the third planetary gear set can be rotatably connected by means of a further drive shaft with the bottom bracket crankshaft.
  • the sun gear of the third planetary gear set may be rotatably connected to the drive shaft.
  • the output shaft may be rotatably connected to the traction means.
  • the third planetary gear set is connected downstream of the first and second planetary gear set in a traction mode, that is to say forms a downstream group.
  • the first and second planetary gear, the drive shaft, the output shaft and the four switching elements form a main group in this embodiment.
  • the output shaft may be rotatably connected to a web of the third planetary gear set and / or a 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 switching elements used in the transmission can be executed positively or frictionally. If the above-mentioned switching elements are each 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 gearbox when reversing the direction of the drive or on 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 must be present for actuating the three switching elements designed as a brake.
  • the transmission may comprise an electric machine, which is operatively connected or operatively connected to the output shaft or the further output shaft.
  • the electric machine may be the first and / or second and / or third planetary gear set downstream.
  • 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 and is set up 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.
  • FIG. 1 shows a schematic representation of the transmission according to the invention according to a first embodiment
  • FIG. 2 shows a switching matrix of the transmission shown in FIG. 1, FIG.
  • FIG. 3 shows a schematic representation of the transmission according to the invention according to a second embodiment
  • FIG. 6 shows a switching matrix for the transmissions illustrated in FIGS. 3 and 4.
  • Fig. 1 shows an inventive transmission according to a first embodiment, which is rotationally symmetrical with respect to a bottom bracket crankshaft 2. In Fig. 1, only the upper half of the transmission is shown.
  • the transmission has a drive shaft 1, which is rotatably connected to the bottom bracket crankshaft 2.
  • the transmission has a first planetary gearset PS1, the is operatively connected to the drive shaft 1, and a second planetary gear set PS2.
  • a web of the first planetary gearset PS1 is rotatably connected to a web of the second planetary gear set PS2.
  • the web of the first planetary gearset PS1 and the web of the second planetary gearset PS2 are made in one piece, that is, as a common component.
  • the first planetary gearset PS1 is designed as a plus-planetary gearset and the second planetary gearset PS2 as a minus-planetary gearset.
  • the drive shaft 1 is rotatably connected to a ring gear of the first planetary gear set PS1.
  • a sun gear of the first planetary gearset PS1 is rotatably connected to an output shaft 3.
  • a ring gear of the second planetary gearset PS2 is rotatably connected by means of a first switching element S3 with the drive shaft 1.
  • the ring gear of the second planetary gear set PS2 by means of a second switching element S2 with a transmission housing 4 rotatably connected.
  • a sun gear of the second planetary gearset PS2 can be connected in a rotationally fixed manner to the transmission housing 4 by means of a third shifting element S1 and can be connected in a rotationally fixed manner to the output shaft 3 by means of a fourth shifting element S4.
  • the output shaft 3 is rotatably connected to a Switzerlandstoffangell in Fig. 1.
  • the first planetary gearset PS1 and the second planetary gearset PS2 are arranged coaxially with one another.
  • the output shaft 3 is arranged coaxially with the bottom bracket crankshaft 2.
  • the second switching element S2 and the third switching element S1 are each designed as brakes.
  • the first switching element S3 and the fourth switching element S4 are each designed as clutches.
  • the transmission is arranged in a cavity of a bottom bracket 8.
  • the transmission shown in Fig. 1 forms a main group HG, which, as can be seen from Figures 3 and 4, is operatively connected to other area groups.
  • Fig. 2 shows a switching matrix for the transmission shown in Fig. 1.
  • the symbol “X” denotes the switching elements which are closed in the respective gear
  • the switching elements are actuated by a suitable actuator system.
  • the ratio "i" between the drive shaft 1 and the output shaft 3 is indicated for each gear in Fig. 2.
  • the transmission has four gears, the first gear being a direct gear further courses are translated quickly.
  • the first planetary gearset PS1 can have a stationary gear ratio of 2 and the second planetary gearset can have a gear ratio of -2.6.
  • the stand translation corresponds to a minus planetary gear set the negative gear ratio of ring gear and sun.
  • the gear ratio corresponds to the positive gear ratio of the ring gear and the sun.
  • Fig. 3 shows the transmission according to the invention according to a second embodiment.
  • the transmission differs from the transmission illustrated in FIG. 1 in that the transmission has a third planetary gear set PS3, which forms a ballast group VG, which is upstream of the main group HG in terms of drive technology.
  • the third planetary gear set PS3 is connected upstream of the first planetary gearset PS1 and the second planetary gearset PS2 when considering a force flow from the bottom bracket crankshaft 2 to the output shaft 3 during a traction operation.
  • a web of the third planetary gearset PS3 is rotatably connected by means of a further drive shaft 5 with the bottom bracket crankshaft 2.
  • the drive shaft 1 is rotatably connected to a sun gear of the third planetary gearset PS3.
  • a ring gear of the third planetary gearset PS3 can be connected in a rotationally fixed manner to the transmission housing 4 by means of a fifth shifting element S5.
  • the ring gear by means of a sixth switching element S6 with the sun gear of the third planetary gearset PS3 rotatably connected.
  • the third planetary set PS3 is arranged coaxially with the first planetary set PS1 and / or the second planetary set PS2.
  • the fifth switching element S5 is designed as a brake and the sixth switching element S6 is designed as a freewheel.
  • the first switching element S3 and fourth switching element S4 are each designed as a freewheel.
  • Fig. 4 shows a transmission according to a third embodiment.
  • the transmission illustrated in FIG. 4 differs from the transmission illustrated in FIG. 3 in that the third planetary gearset PS3 does not form a front-end group VG but rather a rear-end group 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 6 in a traction operation.
  • the web of the third planetary gear set PS3 is rotatably connected to the output shaft 3.
  • the sun gear of the third planetary gearset PS3 is rotatably connected to the other output shaft 6.
  • the further output shaft 6 is rotatably connected to a traction means carrier, not shown.
  • the further output shaft 6 is arranged coaxially with the bottom bracket crankshaft 2.
  • the ring gear of the third planetary gearset PS3 is rotatably connected by means of the fifth switching element S5 to the transmission housing 4 and by means of the sixth switching element S6 with the sun gear.
  • the transmission has an electric machine 7, which is operatively connected to the other output shaft 6, as shown by the dashed line.
  • the connection of the electric machine 7 to the further output shaft 6 can take place via a superposition gear, a spur gear, a chain drive and / or a belt drive, wherein the connection in Fig. 4 is not shown.
  • the connection of the electric machine 7 takes place in one of the rear-mounted group NG downstream technical area.
  • the electric machine 7 is not rotationally symmetrical to the bottom bracket crankshaft 2.
  • the electric machine 7 is arranged offset in the radial direction to the bottom bracket crankshaft 2.
  • the transmission has a torque sensor 9, by means of which the transmitted from the bottom bracket crankshaft 2 to the drive shaft 1 torque can be measured.
  • the torque sensor 9 can be made disc-shaped. Of course, another embodiment and / or arrangement of the torque sensor 9 is possible.
  • FIG. 5 shows a table with values for the state translation of the planetary gear sets shown in FIGS. 3 and 4.
  • the first planetary gear set PS1 has a stand ratio of 2.0
  • the second planetary gear set PS2 has a stand ratio of -2.6
  • the third planetary gear set PS3 has a stand ratio of -1, 6.
  • FIG. 6 shows a switching matrix for the transmissions illustrated in FIGS. 3 and 4.
  • the switching elements which are closed in the respective gear are identified by the symbol "X.” If the switching element is designed as a freewheel, "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.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (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), et un deuxième train épicycloïdal (PS2). Cette transmission est caractérisée en ce qu'un porte-satellites du premier train épicycloïdal est relié solidaire en rotation à un porte-satellites du deuxième train épicycloïdal (PS2).
EP17807815.0A 2016-12-15 2017-11-27 Transmission pour bicyclette Withdrawn EP3554934A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016225169.4A DE102016225169A1 (de) 2016-12-15 2016-12-15 Getriebe für ein Fahrrad
PCT/EP2017/080448 WO2018108496A1 (fr) 2016-12-15 2017-11-27 Transmission pour bicyclette

Publications (1)

Publication Number Publication Date
EP3554934A1 true EP3554934A1 (fr) 2019-10-23

Family

ID=60515374

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17807815.0A Withdrawn EP3554934A1 (fr) 2016-12-15 2017-11-27 Transmission pour bicyclette

Country Status (5)

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US (1) US11649009B2 (fr)
EP (1) EP3554934A1 (fr)
CN (1) CN110072766A (fr)
DE (1) DE102016225169A1 (fr)
WO (1) WO2018108496A1 (fr)

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DE102020210928A1 (de) 2020-08-31 2022-03-03 Zf Friedrichshafen Ag Mehrstufengetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
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DE102021208705B4 (de) 2021-08-10 2023-08-17 Zf Friedrichshafen Ag Radsatzanordnung und Fahrradgetriebe
DE102021212513B4 (de) 2021-08-13 2023-03-23 Zf Friedrichshafen Ag Planetengetriebe sowie Fahrrad
DE102021209258A1 (de) 2021-08-24 2023-03-02 Zf Friedrichshafen Ag Getriebe für ein Fahrrad und Fahrrad
DE102022203243B3 (de) 2022-04-01 2023-06-01 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022203241B3 (de) 2022-04-01 2023-05-25 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022203240B3 (de) 2022-04-01 2023-05-25 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022203246B3 (de) 2022-04-01 2023-06-01 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022203245B3 (de) 2022-04-01 2023-06-01 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022206682B3 (de) 2022-06-30 2023-06-22 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
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DE102022206690B3 (de) 2022-06-30 2023-08-17 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022206685B3 (de) 2022-06-30 2023-08-17 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022207262B3 (de) 2022-07-15 2023-10-05 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022209143B3 (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
DE102022209136B3 (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
DE102022209135B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022209134B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022209142B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad und Fahrrad
DE102022209144B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102022209138B3 (de) 2022-09-02 2023-12-07 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec
DE102023204588B3 (de) 2023-05-17 2024-08-08 Zf Friedrichshafen Ag Tretlagergetriebe in Planetenbauweise für ein Fahrrad oder ein Pedelec

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Also Published As

Publication number Publication date
CN110072766A (zh) 2019-07-30
US20190351972A1 (en) 2019-11-21
DE102016225169A1 (de) 2018-06-21
US11649009B2 (en) 2023-05-16
WO2018108496A1 (fr) 2018-06-21

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