JP2018136002A - Transmission for bicycle, and bicycle assist system including the same - Google Patents

Transmission for bicycle, and bicycle assist system including the same Download PDF

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Publication number
JP2018136002A
JP2018136002A JP2017032602A JP2017032602A JP2018136002A JP 2018136002 A JP2018136002 A JP 2018136002A JP 2017032602 A JP2017032602 A JP 2017032602A JP 2017032602 A JP2017032602 A JP 2017032602A JP 2018136002 A JP2018136002 A JP 2018136002A
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Prior art keywords
gear
speed
ratio
bicycle
shift
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JP2018136002A5 (en
JP6756640B2 (en
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山本　貴士
Takashi Yamamoto
貴士 山本
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Shimano Inc
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Shimano Inc
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Priority to JP2017032602A priority Critical patent/JP6756640B2/en
Priority to TW107104110A priority patent/TWI742237B/en
Priority to CN202111363968.7A priority patent/CN114194327B/en
Priority to CN201810145335.0A priority patent/CN108466671B/en
Priority to DE102018202682.3A priority patent/DE102018202682A1/en
Publication of JP2018136002A publication Critical patent/JP2018136002A/en
Publication of JP2018136002A5 publication Critical patent/JP2018136002A5/ja
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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
    • 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
    • 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
    • B62M11/16—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 ground-wheel hub
    • 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
    • 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
    • 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
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • 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
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
    • F16H2200/203—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
    • F16H2200/2069—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using two 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
    • F16H2200/2084—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches two freewheel mechanisms

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)
  • Control Of Transmission Device (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a transmission for a bicycle capable of contributing to usability, and a bicycle assist system including the transmission.SOLUTION: A transmission for a bicycle includes a transmission mechanism containing five or more shift stages configured so that a transmission ratio stepwisely increases. For three continuous shift stages out of the five shift stages, when a ratio of a transmission rate of an intermediate shift stage to a transmission rate of a maximum shift stage is subtracted from a ratio of a transmission rate of a minimum shift stage to the transmission rate of the intermediate shift stage, the difference is positive or negative in all sets of the three continuous shift stages.SELECTED DRAWING: Figure 3

Description

本発明は、自転車用変速機およびこれを備える自転車用アシストシステムに関する。   The present invention relates to a bicycle transmission and a bicycle assist system including the same.

特許文献１に開示される自転車用変速機は、自転車の変速比を段階的に変更する変速機構を含む。この変速機構は、８段階の変速比に対応する変速段を含み、各変速段について、各変速段の変速比に対する各変速段よりも１段階小さい変速段の変速比の比率が所定の範囲内に含まれるように構成されている。このため、変速段を変更すると、どの変速段においても所定の比率の範囲内で変速比が変化する。   The bicycle transmission disclosed in Patent Document 1 includes a speed change mechanism that changes the speed ratio of the bicycle in stages. This speed change mechanism includes speed stages corresponding to eight speed ratios, and the ratio of the speed ratio of the speed stage that is one stage smaller than each speed stage to the speed ratio of each speed stage is within a predetermined range. It is comprised so that it may be included in. For this reason, when the gear position is changed, the gear ratio changes within a predetermined ratio range at any gear position.

特許第４５６４９７８号公報Japanese Patent No. 4564978

自転車の車種またはユーザの要求等によって変速比の範囲ごとに変速段が変更される頻度が異なる場合がある。特許文献１では、この点について何ら検討されていない。このため、ユーザビリティにおいて改善の余地がある。   The frequency at which the gear position is changed may vary depending on the range of the gear ratio depending on the type of bicycle or the user's request. Patent Document 1 does not discuss this point at all. For this reason, there is room for improvement in usability.

本発明の目的は、ユーザビリティに貢献できる自転車用変速機およびこれを備える自転車用アシストシステムを提供することである。   An object of the present invention is to provide a bicycle transmission that can contribute to usability and a bicycle assist system including the same.

本発明の第１側面に従う自転車用変速機の一形態は、段階的に変速比が大きくなるように構成される５つ以上の変速段を含む変速機構を備え、前記５つ以上の変速段のうち連続する３つの変速段において、最小変速段の変速比に対する中間変速段の変速比の比率から、前記中間速段の変速比に対する最大変速段の変速比の比率を減算すると、その差は、いずれの前記連続する３つの変速段においても正および負の一方である。
上記構成によれば、連続する３つの変速段において、最小変速段の変速比に対する中間変速段の変速比の比率から、中間変速段の変速比に対する最大変速段の変速比の比率を減算した場合の差が「０」ではないようになる。このため、ユーザの要求等に応じて連続する変速段における変速比の比率の差（変速ステップ）を所望の割合で変化させることによってユーザビリティに貢献できる。また、変速ステップは、いずれの連続する３つの変速段においても正および負の一方であるため、変速比の比率を変速段に応じて増加、または、減少する方向に方向付けできる。 One aspect of the bicycle transmission according to the first aspect of the present invention includes a transmission mechanism including five or more shift stages configured so that a gear ratio increases stepwise, and the five or more shift stages are provided. Of the three consecutive speeds, when the ratio of the maximum gear ratio to the intermediate gear ratio is subtracted from the ratio of the intermediate gear ratio to the minimum gear ratio, the difference is: Any of the three consecutive gear positions is either positive or negative.
According to the above configuration, when the ratio of the maximum gear ratio to the intermediate gear ratio is subtracted from the ratio of the intermediate gear ratio to the minimum gear ratio in three consecutive gear speeds. The difference is not “0”. For this reason, it is possible to contribute to usability by changing the difference in the ratio of the transmission gear ratios (transmission step) in the continuous gear positions according to the user's request or the like at a desired ratio. Further, since the shift step is one of positive and negative in any three consecutive shift speeds, the ratio of the gear ratio can be increased or decreased in accordance with the shift speed.

前記第１側面に従う第２側面の自転車用変速機において、前記５つ以上の変速段は、前記変速機構において最小である変速段を含む。
上記構成によれば、最小である変速段からみて所望の変速ステップを実現でき、ユーザビリティに貢献できる。 In the bicycle transmission according to the second aspect according to the first aspect, the five or more shift stages include a shift stage that is the minimum in the transmission mechanism.
According to the above configuration, a desired shift step can be realized in view of the minimum shift stage, which can contribute to usability.

前記第１または第２側面に従う第３側面の自転車用変速機において、前記差の絶対値は、０．０３以上０．１５以下である。
上記構成によれば、変速ステップの絶対値が０．０３以上０．１５以下であるため、すなわち、変速ステップが３％以上１５％以下であるため、変速段が変更される場合のペダリング操作感覚の過度な変化を抑制できる。 In the bicycle transmission according to the third aspect according to the first or second aspect, the absolute value of the difference is 0.03 or more and 0.15 or less.
According to the above configuration, since the absolute value of the shift step is not less than 0.03 and not more than 0.15, that is, the shift step is not less than 3% and not more than 15%, the pedaling operation feeling when the shift speed is changed. The excessive change of can be suppressed.

本発明の第４側面に従う自転車用変速機の一形態は、段階的に変速比が大きくなるように構成される４つ以上の変速段を含む変速機構を備え、前記４つ以上の変速段のうち連続する３つの変速段において、最小変速段の変速比に対する中間変速段の変速比の比率から、前記中間変速段の変速比に対する最大変速段の変速比の比率を減算すると、その差は、いずれの前記連続する３つの変速段においても正および負の一方であり、かつ、その差の絶対値は、いずれも０．０３以上０．１５以下である。
上記構成によれば、連続する３つの変速段において、最小変速段の変速比に対する中間変速段の変速比の比率から、中間変速段の変速比に対する最大変速段の変速比の比率を減算した場合の差が「０」ではないようになる。このため、ユーザの要求等に応じて連続する変速段における変速比の比率の差（変速ステップ）を所望の割合で変化させることによってユーザビリティに貢献できる。また、変速ステップは、いずれの連続する３つの変速段においても正および負の一方であるため、変速比の比率を変速段に応じて増加、または、減少する方向に方向付けできる。さらに、変速ステップの絶対値が０．０３以上０．１５以下であるため、すなわち、変速ステップが３％以上１５％以下で変化するため、変速段が変更される場合のペダリング操作感覚の過度な変化を抑制できる。 One aspect of the bicycle transmission according to the fourth aspect of the present invention includes a speed change mechanism including four or more shift speeds configured so that a gear ratio increases stepwise. Of the three consecutive speeds, when the ratio of the maximum gear ratio to the intermediate gear ratio is subtracted from the ratio of the intermediate gear ratio to the minimum gear ratio, the difference is: Any of the three consecutive gear positions is positive or negative, and the absolute value of the difference is 0.03 or more and 0.15 or less.
According to the above configuration, when the ratio of the maximum gear ratio to the intermediate gear ratio is subtracted from the ratio of the intermediate gear ratio to the minimum gear ratio in three consecutive gear speeds. The difference is not “0”. For this reason, it is possible to contribute to usability by changing the difference in the ratio of the transmission gear ratios (transmission step) in the continuous gear positions according to the user's request or the like at a desired ratio. Further, since the shift step is one of positive and negative in any three consecutive shift speeds, the ratio of the gear ratio can be increased or decreased in accordance with the shift speed. Furthermore, since the absolute value of the shift step is 0.03 or more and 0.15 or less, that is, the shift step changes between 3% or more and 15% or less, the feeling of pedaling operation when the shift stage is changed is excessive. Change can be suppressed.

前記第４側面に従う第５側面の自転車用変速機において、前記４つ以上の変速段は、前記変速機構において最小である変速段を含む。
上記構成によれば、最小である変速段からみて所望の変速ステップを実現でき、ユーザビリティに貢献できる。 In the bicycle transmission according to the fifth aspect according to the fourth aspect, the four or more shift stages include a shift stage that is the minimum in the transmission mechanism.
According to the above configuration, a desired shift step can be realized in view of the minimum shift stage, which can contribute to usability.

前記第４または第５側面に従う第６側面の自転車用変速機において、前記変速機構は、段階的に変速比が大きくなるように構成される５つ以上の変速段を含み、前記連続する３つの変速段は、前記５つ以上の変速段に含まれる。
上記構成によれば、５つ以上の変速段を含む変速機構においてもユーザビリティに貢献できる。 In the bicycle transmission according to the sixth aspect according to the fourth or fifth aspect, the speed change mechanism includes five or more shift speeds configured so that a gear ratio increases stepwise, and the three Shift stages are included in the five or more shift stages.
According to the above configuration, it is possible to contribute to usability even in a speed change mechanism including five or more speed stages.

前記第３〜第６側面のいずれか一つに従う第７側面の自転車用変速機において、前記差の絶対値は、０．０４以上０．１以下である。
上記構成によれば、変速ステップの絶対値が０．０４以上０．１以下であるため、すなわち、変速ステップが４％以上１０％以下であるため、変速段が変更される場合のペダリング操作感覚の過度な変化をより一層抑制できる。 In the bicycle transmission according to the seventh aspect according to any one of the third to sixth aspects, the absolute value of the difference is 0.04 or more and 0.1 or less.
According to the above configuration, since the absolute value of the shift step is 0.04 or more and 0.1 or less, that is, the shift step is 4% or more and 10% or less, the pedaling operation feeling when the shift stage is changed. The excessive change of can be further suppressed.

前記第１〜第７側面のいずれか一つに従う第８側面の自転車用変速機において、前記差は、いずれの前記連続する３つの変速段においても正である。
上記構成によれば、変速ステップが常に正であるため、変速段が小さいほどある変速段の変速比に対するこれよりも１段階大きい変速段の変速比の比率は大きい。このため、ケイデンスを一定の範囲内に保持する走行を行う場合において、自転車の車速が低い領域での変速段の変更頻度を少なくできる。 In the bicycle transmission according to the eighth aspect according to any one of the first to seventh aspects, the difference is positive in any of the three consecutive gear positions.
According to the above configuration, since the shift step is always positive, the smaller the shift step, the larger the ratio of the gear ratio of the gear step that is one step larger than the gear ratio of a certain gear step. For this reason, in the case of running while keeping the cadence within a certain range, it is possible to reduce the frequency of changing the gear position in the region where the bicycle speed is low.

前記第１〜第８側面のいずれか一つに従う第９側面の自転車用変速機において、前記差のうちの１つから前記差のうちの他の１つを減算した値の絶対値は、０．００５以上０．０２以下である。
上記構成によれば、連続する３つの変速段における２つの変速ステップのうちの１つから他の１つを減算した値の絶対値は、０．００５以上０．０２以下である。このため、所定の変速段の変速比に対する所定の変速段よりも一段階大きい変速段の変速比の比率をグラフ上にプロットした場合、平坦な線によって近似することができる。このため、ケイデンスを一定の範囲内に保持する走行を行う場合において、自転車の車速の上昇に応じた変速段を切り替えるタイミングが一定になる。 In the bicycle transmission according to the ninth aspect according to any one of the first to eighth aspects, an absolute value of a value obtained by subtracting the other one of the differences from one of the differences is 0. 0.005 or more and 0.02 or less.
According to the above configuration, the absolute value of the value obtained by subtracting the other one from the two shift steps in the three consecutive shift speeds is 0.005 or more and 0.02 or less. For this reason, when the ratio of the gear ratio of the gear stage that is one step larger than the predetermined gear stage to the gear ratio of the predetermined gear stage is plotted on the graph, it can be approximated by a flat line. For this reason, in the case of running while keeping the cadence within a certain range, the timing for switching the gear position according to the increase in the vehicle speed of the bicycle is constant.

前記第１〜第９側面のいずれか一つに従う第１０側面の自転車用変速機において、前記変速機構は、内装変速機構である。
上記構成によれば、内装変速機構においても、ユーザビリティに貢献できる。 In the bicycle transmission according to the tenth aspect according to any one of the first to ninth aspects, the transmission mechanism is an internal transmission mechanism.
According to the above configuration, the internal speed change mechanism can also contribute to usability.

前記第１０側面に従う第１１側面の自転車用変速機において、前記内装変速機構を収容するハブをさらに備える。
上記構成によれば、ハブに設けられる内装変速機構においても、すなわち内装変速ハブにおいても、ユーザビリティに貢献できる。 The bicycle transmission according to the eleventh aspect according to the tenth aspect further includes a hub that accommodates the internal transmission mechanism.
According to the above configuration, even in the internal transmission mechanism provided in the hub, that is, in the internal transmission hub, it is possible to contribute to usability.

本発明の第１２側面に従う自転車用アシストシステムの一形態は、前記第１〜第１１側面のいずれか一つに記載の自転車用変速機と、人力駆動力をアシストするモータと、を備える。
上記構成によれば、モータによって人力駆動力がアシストされるため、車速に対して変速比が低い状態であっても運転者の負荷を低減できる。また、自転車用アシストシステムによれば、モータによって人力駆動力がアシストされるため、自転車の車速が低い領域での変速段の変更頻度が少なくなる。このため、前記第１〜第１１側面のいずれか一つに記載の自転車用変速機を用いることによって変速段の変更タイミングを最適化できる。 One aspect of the bicycle assist system according to the twelfth aspect of the present invention includes the bicycle transmission according to any one of the first to eleventh aspects, and a motor that assists human driving force.
According to the above configuration, since the human driving force is assisted by the motor, it is possible to reduce the driver's load even when the speed ratio is low with respect to the vehicle speed. Further, according to the bicycle assist system, since the human power driving force is assisted by the motor, the frequency of changing the gear position in the region where the bicycle vehicle speed is low is reduced. For this reason, the change timing of the gear position can be optimized by using the bicycle transmission according to any one of the first to eleventh aspects.

前記第１２側面に従う第１３側面の自転車用変速機において、前記自転車用変速機を操作するために人の手によって操作される操作部をさらに備え、前記自転車用変速機は、前記操作部への操作に応じて自転車の変速比を変更する。
上記構成によれば、変速段の変更タイミングを最適化できるため、運転者による操作部操作の負荷を低減できる。 The bicycle transmission of the thirteenth side according to the twelfth side further includes an operation unit operated by a human hand to operate the bicycle transmission, and the bicycle transmission is connected to the operation unit. Change the gear ratio of the bicycle according to the operation.
According to the above configuration, the change timing of the gear position can be optimized, so that the load on the operation unit by the driver can be reduced.

本自転車用変速機およびこれを備える自転車用アシストシステムは、ユーザビリティに貢献できる。   The bicycle transmission and the bicycle assist system including the same can contribute to usability.

実施形態の自転車用アシストシステムが搭載された自転車の側面図。The side view of the bicycle carrying the bicycle assist system of embodiment. 図１の自転車用アシストシステムの自転車用変速機の正面図。The front view of the bicycle transmission of the bicycle assist system of FIG. 図２の自転車用変速機の部分断面図。FIG. 3 is a partial cross-sectional view of the bicycle transmission of FIG. 2. 図３の自転車用変速機のスリーブの斜視図。FIG. 4 is a perspective view of a sleeve of the bicycle transmission of FIG. 3. 図２のスリーブと第１設定部材との関係を示す模式図。The schematic diagram which shows the relationship between the sleeve of FIG. 2, and a 1st setting member. 図３の自転車用変速機のスケルトン図。FIG. 4 is a skeleton diagram of the bicycle transmission of FIG. 3. 図３の自転車用変速機の第１変速段における変速経路を示す模式図。FIG. 4 is a schematic diagram showing a shift path in a first shift stage of the bicycle transmission of FIG. 3. 図３の自転車用変速機の第２変速段における変速経路を示す模式図。FIG. 4 is a schematic diagram showing a shift path in a second shift stage of the bicycle transmission of FIG. 3. 図３の自転車用変速機の第３変速段における変速経路を示す模式図。FIG. 4 is a schematic diagram showing a shift path in a third shift stage of the bicycle transmission of FIG. 3. 図３の自転車用変速機の第４変速段における変速経路を示す模式図。FIG. 4 is a schematic diagram showing a shift path in a fourth shift stage of the bicycle transmission of FIG. 3. 図３の自転車用変速機の第５変速段における変速経路を示す模式図。FIG. 4 is a schematic diagram showing a shift path in a fifth shift stage of the bicycle transmission of FIG. 3. 図３の自転車用変速機の変速段とケイデンスおよび車速との関係を示すグラフ。The graph which shows the relationship between the gear stage of the bicycle transmission of FIG. 3, a cadence, and a vehicle speed.

図１〜図１２を参照して、実施形態の自転車用アシストシステム４０を搭載する自転車１０について説明する。
図１に示されるとおり、自転車１０は、車体１２、駆動機構１４、前輪１６、後輪１８、および、自転車用アシストシステム４０を備える。車体１２は、フレーム１２Ａおよびフレーム１２Ａに取り付けられるハンドルバー１２Ｂを備える。 With reference to FIGS. 1-12, the bicycle 10 carrying the bicycle assist system 40 of embodiment is demonstrated.
As shown in FIG. 1, the bicycle 10 includes a vehicle body 12, a drive mechanism 14, a front wheel 16, a rear wheel 18, and a bicycle assist system 40. The vehicle body 12 includes a frame 12A and a handle bar 12B attached to the frame 12A.

駆動機構１４は、クランク２０、ペダル２２、フロント回転体２４、伝達部材２６、リア回転体２８を備える。クランク２０は、クランク軸２０Ａおよびクランクアーム２０Ｂを含む。駆動機構１４は、ペダル２２に加えられた人力駆動力を後輪１８に伝達する。フロント回転体２４は、スプロケット、プーリーまたはベベルギアを含む。リア回転体２８は、スプロケット、プーリーまたはベベルギアを含む。伝達部材２６は、例えば、チェーン、ベルト、またはシャフトを介して、クランク２０の回転を後輪１８に伝達するように構成される。フロント回転体２４は、クランク軸２０Ａにワンウェイクラッチ（図示略）を介して結合される。ワンウェイクラッチは、クランク２０が前転した場合に、フロント回転体２４を前転させ、クランク２０が後転した場合に、フロント回転体２４を後転させないように構成される。フロント回転体２４は、クランク軸２０Ａにワンウェイクラッチを介さずに結合してもよい。   The drive mechanism 14 includes a crank 20, a pedal 22, a front rotating body 24, a transmission member 26, and a rear rotating body 28. The crank 20 includes a crankshaft 20A and a crank arm 20B. The drive mechanism 14 transmits the manpower driving force applied to the pedal 22 to the rear wheel 18. The front rotating body 24 includes a sprocket, a pulley, or a bevel gear. The rear rotating body 28 includes a sprocket, a pulley, or a bevel gear. The transmission member 26 is configured to transmit the rotation of the crank 20 to the rear wheel 18 via, for example, a chain, a belt, or a shaft. The front rotating body 24 is coupled to the crankshaft 20A via a one-way clutch (not shown). The one-way clutch is configured to rotate the front rotating body 24 forward when the crank 20 rotates forward, and not to rotate the front rotating body 24 when the crank 20 rotates backward. The front rotating body 24 may be coupled to the crankshaft 20A without using a one-way clutch.

自転車用アシストシステム４０は、自転車用変速機５０と、モータ４２と、を備える。自転車用アシストシステム４０は、操作部４４およびバッテリユニット４６をさらに備える。自転車用アシストシステム４０は、自転車１０に搭載される。   The bicycle assist system 40 includes a bicycle transmission 50 and a motor 42. The bicycle assist system 40 further includes an operation unit 44 and a battery unit 46. The bicycle assist system 40 is mounted on the bicycle 10.

モータ４２は、人力駆動力をアシストする。モータ４２は、フレーム１２Ａに支持される。一例では、モータ４２は、クランク軸２０Ａまわりに設けられて、クランク軸２０Ａにモータ４２のトルクを伝達する。別の例では、モータ４２は、前輪１６の車軸１６Ａまたは後輪１８の車軸１８Ａのまわりに設けられて前輪１６または後輪１８にモータ４２のトルクを伝達する。   The motor 42 assists the human driving force. The motor 42 is supported by the frame 12A. In one example, the motor 42 is provided around the crankshaft 20A and transmits the torque of the motor 42 to the crankshaft 20A. In another example, the motor 42 is provided around the axle 16 </ b> A of the front wheel 16 or the axle 18 </ b> A of the rear wheel 18 to transmit the torque of the motor 42 to the front wheel 16 or the rear wheel 18.

操作部４４は、自転車用変速機５０を操作するために人の手によって操作される。一例では、操作部４４は、ハンドルバー１２Ｂに設けられる。操作部４４は、ボーデンケーブル（図示略）の一端が取り付けられる。操作部４４をユーザが操作することによって、ボーデンケーブルのインナケーブルＣ１（図２参照）が移動する。ボーデンケーブルの他端は、自転車用変速機５０に取り付けられる。   The operation unit 44 is operated by a human hand to operate the bicycle transmission 50. In one example, the operation unit 44 is provided on the handle bar 12B. One end of a Bowden cable (not shown) is attached to the operation unit 44. When the user operates the operation unit 44, the inner cable C1 (see FIG. 2) of the Bowden cable moves. The other end of the Bowden cable is attached to the bicycle transmission 50.

バッテリユニット４６は、モータ４２に電力を供給する。バッテリユニット４６は、バッテリセル４６Ａおよびバッテリユニット４６をフレーム１２Ａに取り付けるためのホルダ４６Ｂを備える。   The battery unit 46 supplies power to the motor 42. The battery unit 46 includes a battery cell 46A and a holder 46B for attaching the battery unit 46 to the frame 12A.

自転車用変速機５０は、操作部４４への操作に応じて自転車１０の変速比を変更する。自転車用変速機５０は、変速機構６２を備える。変速機構６２は、内装変速機構である。自転車用変速機５０は、ハブ１８Ｃを備える。ハブ１８Ｃは、内装変速機構を収容する。すなわち、図２に示されるとおり、自転車用変速機５０は、ハブ１８Ｃに一体的に設けられる内装ハブである。   The bicycle transmission 50 changes the speed ratio of the bicycle 10 in accordance with an operation on the operation unit 44. The bicycle transmission 50 includes a speed change mechanism 62. The transmission mechanism 62 is an internal transmission mechanism. The bicycle transmission 50 includes a hub 18C. Hub 18C houses the internal transmission mechanism. That is, as shown in FIG. 2, the bicycle transmission 50 is an internal hub provided integrally with the hub 18C.

図３に示されるとおり、内装変速ハブである自転車用変速機５０は、伝達機構５２および設定機構５４を備える。自転車用変速機５０は、支持部材５６、入力体５８、および、出力体６０をさらに備える。支持部材５６は、後輪１８の車軸１８Ａと一体化されている。入力体５８は、リア回転体２８と一体的に回転可能に支持部材５６まわりに設けられる。出力体６０は、ハブシェルである。出力体６０は、後輪１８のスポーク１８Ｂを取り付けるためのフランジ６０Ａを備える。自転車用変速機５０は、入力体５８の回転を変速して出力体６０に伝達する。   As shown in FIG. 3, the bicycle transmission 50 that is an internal transmission hub includes a transmission mechanism 52 and a setting mechanism 54. The bicycle transmission 50 further includes a support member 56, an input body 58, and an output body 60. The support member 56 is integrated with the axle 18 </ b> A of the rear wheel 18. The input body 58 is provided around the support member 56 so as to be rotatable integrally with the rear rotating body 28. The output body 60 is a hub shell. The output body 60 includes a flange 60 </ b> A for attaching the spoke 18 </ b> B of the rear wheel 18. The bicycle transmission 50 changes the rotation of the input body 58 and transmits it to the output body 60.

図３に示されるとおり、伝達機構５２は、複数の変速機構６２を含む。複数の変速機構６２は、少なくとも第１変速機構６２Ａを含む。複数の変速機構６２は、第２変速機構６２Ｂをさらに含む。伝達機構５２は、入力体５８からの回転を３段階以上の変速比で出力体６０に伝達する。変速機構６２は、入力体５８からの回転を変速して出力体６０に出力可能である。変速機構６２は、段階的に変速比が大きくなるように構成される４つ以上の変速段を含む。変速機構６２は、段階的に変速比が大きくなるように構成される５つ以上の変速段を含む。図３に示す変速機構６２は、５つの変速段を含む。   As shown in FIG. 3, the transmission mechanism 52 includes a plurality of speed change mechanisms 62. The plurality of transmission mechanisms 62 includes at least a first transmission mechanism 62A. The plurality of transmission mechanisms 62 further include a second transmission mechanism 62B. The transmission mechanism 52 transmits the rotation from the input body 58 to the output body 60 at a gear ratio of three or more steps. The speed change mechanism 62 can change the rotation from the input body 58 and output it to the output body 60. The speed change mechanism 62 includes four or more speed stages that are configured so that the speed ratio increases stepwise. The speed change mechanism 62 includes five or more speed stages configured so that the speed ratio increases stepwise. The transmission mechanism 62 shown in FIG. 3 includes five shift stages.

複数の変速機構６２は、それぞれ少なくとも１つの遊星機構６４，６６，６８，７０を含む。複数の変速機構６２は、第１遊星機構６４および第２遊星機構６６を含む。複数の変速機構６２は、第３遊星機構６８および第４遊星機構７０をさらに含む。具体的には、第１変速機構６２Ａは、第１遊星機構６４および第２遊星機構６６を含む。第２変速機構６２Ｂは、第３遊星機構６８および第４遊星機構７０を含む。第１遊星機構６４は、自転車用変速機５０の軸方向において入力体５８の隣に配置される。第２遊星機構６６は、自転車用変速機５０の軸方向において第１遊星機構６４の隣かつ、入力体５８とは反対側に配置される。第４遊星機構７０は、自転車用変速機５０の軸方向において第２遊星機構６６の隣かつ、第１遊星機構６４とは反対側に配置される。第３遊星機構６８は、自転車用変速機５０の軸方向において第３遊星機構６８の隣かつ、第２遊星機構６６とは反対側に配置される。   Each of the plurality of speed change mechanisms 62 includes at least one planetary mechanism 64, 66, 68, 70. The plurality of speed change mechanisms 62 includes a first planetary mechanism 64 and a second planetary mechanism 66. The plurality of speed change mechanisms 62 further include a third planetary mechanism 68 and a fourth planetary mechanism 70. Specifically, the first speed change mechanism 62A includes a first planetary mechanism 64 and a second planetary mechanism 66. The second speed change mechanism 62B includes a third planetary mechanism 68 and a fourth planetary mechanism 70. The first planetary mechanism 64 is disposed next to the input body 58 in the axial direction of the bicycle transmission 50. The second planetary mechanism 66 is disposed next to the first planetary mechanism 64 and on the side opposite to the input body 58 in the axial direction of the bicycle transmission 50. The fourth planetary mechanism 70 is disposed next to the second planetary mechanism 66 and on the opposite side of the first planetary mechanism 64 in the axial direction of the bicycle transmission 50. The third planetary mechanism 68 is arranged next to the third planetary mechanism 68 and on the opposite side of the second planetary mechanism 66 in the axial direction of the bicycle transmission 50.

第１遊星機構６４は、第１太陽ギア７２、第１リングギア７４、第１遊星ギア７６、および、第１キャリア７８を含む。第１太陽ギア７２は、支持部材５６の軸まわりに支持部材５６に回転可能に支持される。第１リングギア７４は、第１太陽ギア７２まわりに配置される。第１遊星ギア７６は、第１太陽ギア７２と係合し第１太陽ギア７２および第１リングギア７４に対して公転可能である。第１遊星機構６４は、複数の第１遊星ギア７６を含む。第１キャリア７８は、複数の第１遊星ギア７６をそれぞれ回転可能に支持する。第１キャリア７８は、支持部材５６の軸まわりに回転可能に設けられる。複数の第１遊星ギア７６はそれぞれ、第１キャリア７８の回転に伴って第１太陽ギア７２まわりで公転する。第１キャリア７８は、入力体５８に接続されて、入力体５８からの回転が伝達される。第１遊星機構６４は、入力体５８からの回転を増速して出力するように構成される。   The first planetary mechanism 64 includes a first sun gear 72, a first ring gear 74, a first planetary gear 76, and a first carrier 78. The first sun gear 72 is rotatably supported by the support member 56 around the axis of the support member 56. The first ring gear 74 is disposed around the first sun gear 72. The first planetary gear 76 engages with the first sun gear 72 and can revolve with respect to the first sun gear 72 and the first ring gear 74. The first planetary mechanism 64 includes a plurality of first planetary gears 76. The first carrier 78 rotatably supports the plurality of first planetary gears 76. The first carrier 78 is provided to be rotatable around the axis of the support member 56. The plurality of first planetary gears 76 revolve around the first sun gear 72 as the first carrier 78 rotates. The first carrier 78 is connected to the input body 58 and the rotation from the input body 58 is transmitted. The first planetary mechanism 64 is configured to accelerate and output the rotation from the input body 58.

第２遊星機構６６は、第２太陽ギア８０、第２リングギア８２、第２遊星ギア８４、および、第２キャリア８６を含む。第２太陽ギア８０は、支持部材５６の軸まわりに支持部材５６に回転可能に支持される。第２リングギア８２は、第２太陽ギア８０まわりに配置される。第２遊星ギア８４は、第２太陽ギア８０と係合し第２太陽ギア８０および第２リングギア８２に対して公転可能である。第２遊星機構６６は、複数の第２遊星ギア８４を含む。第２キャリア８６は、複数の第２遊星ギア８４をそれぞれ回転可能に支持する。第２キャリア８６は、支持部材５６の軸まわりに回転可能に設けられる。複数の第２遊星ギア８４はそれぞれ、第２キャリア８６の回転に伴って第２太陽ギア８０まわりで公転する。第２遊星機構６６は、入力体５８からの回転を増速して出力するように構成される。第２キャリア８６は、入力体５８に接続されて、入力体５８からの回転が伝達される。   The second planetary mechanism 66 includes a second sun gear 80, a second ring gear 82, a second planetary gear 84, and a second carrier 86. The second sun gear 80 is rotatably supported by the support member 56 around the axis of the support member 56. The second ring gear 82 is disposed around the second sun gear 80. The second planetary gear 84 engages with the second sun gear 80 and can revolve with respect to the second sun gear 80 and the second ring gear 82. The second planetary mechanism 66 includes a plurality of second planetary gears 84. The second carrier 86 rotatably supports the plurality of second planetary gears 84, respectively. The second carrier 86 is provided to be rotatable around the axis of the support member 56. The plurality of second planetary gears 84 revolve around the second sun gear 80 as the second carrier 86 rotates. The second planetary mechanism 66 is configured to accelerate and output the rotation from the input body 58. The second carrier 86 is connected to the input body 58 and the rotation from the input body 58 is transmitted.

第１遊星機構６４および第２遊星機構６６は、いずれも入力体５８からの回転を増速して出力するように構成される。第１太陽ギア７２の歯数は、第２太陽ギア８０の歯数よりも少ない。第１遊星ギア７６の歯数は、第２遊星ギア８４の歯数よりも多い。第１リングギア７４の歯数および第２リングギア８２の歯数は等しい。第１リングギア７４および第２リングギア８２は、第１リングギア部材８８に形成される。第１リングギア部材８８は、第１ギア部８８Ａを含む。第１ギア部８８Ａは、第１リングギア７４および第２リングギア８２として共用される。第１遊星ギア７６および第２遊星ギア８４は、第１遊星ギア部材９０に形成される。第１遊星ギア部材９０は、いわゆる段付きの遊星ギアを構成する。第１キャリア７８および第２キャリア８６は、一体に形成される。   Both the first planetary mechanism 64 and the second planetary mechanism 66 are configured to increase the speed of rotation from the input body 58 and output it. The number of teeth of the first sun gear 72 is smaller than the number of teeth of the second sun gear 80. The number of teeth of the first planetary gear 76 is larger than the number of teeth of the second planetary gear 84. The number of teeth of the first ring gear 74 and the number of teeth of the second ring gear 82 are equal. The first ring gear 74 and the second ring gear 82 are formed on the first ring gear member 88. The first ring gear member 88 includes a first gear portion 88A. The first gear portion 88 </ b> A is shared as the first ring gear 74 and the second ring gear 82. The first planetary gear 76 and the second planetary gear 84 are formed on the first planetary gear member 90. The first planetary gear member 90 constitutes a so-called stepped planetary gear. The first carrier 78 and the second carrier 86 are integrally formed.

第３遊星機構６８は、第３太陽ギア９２、第３リングギア９４、第３遊星ギア９６、および、第３キャリア９８を含む。第３太陽ギア９２は、支持部材５６の軸まわりに支持部材５６に回転可能に支持される。第３リングギア９４は、第３太陽ギア９２まわりに配置される。第３遊星ギア９６は、第３太陽ギア９２と係合し第３太陽ギア９２および第３リングギア９４に対して公転可能である。第３遊星機構６８は、複数の第３遊星ギア９６を含む。第３キャリア９８は、複数の第３遊星ギア９６をそれぞれ回転可能に支持する。第３キャリア９８は、支持部材５６の軸まわりに回転可能に設けられる。複数の第３遊星ギア９６はそれぞれ、第３キャリア９８の回転に伴って第３太陽ギア９２まわりで公転する。第３キャリア９８は、第１リングギア部材８８に接続されて、第１リングギア部材８８からの回転が伝達される。   The third planetary mechanism 68 includes a third sun gear 92, a third ring gear 94, a third planetary gear 96, and a third carrier 98. The third sun gear 92 is rotatably supported by the support member 56 around the axis of the support member 56. The third ring gear 94 is disposed around the third sun gear 92. The third planetary gear 96 engages with the third sun gear 92 and can revolve with respect to the third sun gear 92 and the third ring gear 94. The third planetary mechanism 68 includes a plurality of third planetary gears 96. The third carrier 98 supports the plurality of third planetary gears 96 in a rotatable manner. The third carrier 98 is provided to be rotatable around the axis of the support member 56. Each of the plurality of third planetary gears 96 revolves around the third sun gear 92 as the third carrier 98 rotates. The third carrier 98 is connected to the first ring gear member 88 and the rotation from the first ring gear member 88 is transmitted.

第４遊星機構７０は、第４太陽ギア１００、第４リングギア１０２、第４遊星ギア１０４、および、第４キャリア１０６を含む。第４太陽ギア１００は、支持部材５６の軸まわりに支持部材５６に回転可能に支持される。第４リングギア１０２は、第４太陽ギア１００まわりに配置される。第４遊星ギア１０４は、第４太陽ギア１００と係合し第４太陽ギア１００および第４リングギア１０２に対して公転可能である。第４遊星機構７０は、複数の第４遊星ギア１０４を含む。第４キャリア１０６は、複数の第４遊星ギア１０４をそれぞれ回転可能に支持する。第４キャリア１０６は、支持部材５６の軸まわりに回転可能に設けられる。複数の第４遊星ギア１０４はそれぞれ、第４キャリア１０６の回転に伴って第４太陽ギア１００まわりで公転する。第４キャリア１０６は、第１リングギア部材８８に接続されて、第１リングギア部材８８からの回転が伝達される。   The fourth planetary mechanism 70 includes a fourth sun gear 100, a fourth ring gear 102, a fourth planetary gear 104, and a fourth carrier 106. The fourth sun gear 100 is rotatably supported by the support member 56 around the axis of the support member 56. The fourth ring gear 102 is arranged around the fourth sun gear 100. The fourth planetary gear 104 engages with the fourth sun gear 100 and can revolve with respect to the fourth sun gear 100 and the fourth ring gear 102. The fourth planetary mechanism 70 includes a plurality of fourth planetary gears 104. The fourth carrier 106 supports the plurality of fourth planetary gears 104 in a rotatable manner. The fourth carrier 106 is provided to be rotatable around the axis of the support member 56. Each of the plurality of fourth planetary gears 104 revolves around the fourth sun gear 100 as the fourth carrier 106 rotates. The fourth carrier 106 is connected to the first ring gear member 88, and the rotation from the first ring gear member 88 is transmitted.

第３遊星機構６８は、入力体５８からの回転を増速して出力するように構成される。第４遊星機構７０は、入力体５８からの回転を増速して出力するように構成される。第３太陽ギア９２の歯数は、第４太陽ギア１００の歯数よりも少ない。第３遊星ギア９６の歯数は、第４遊星ギア１０４の歯数よりも多い。第３リングギア９４の歯数および第４リングギア１０２の歯数は等しい。第３リングギア９４および第４リングギア１０２は、第２リングギア部材１０８に形成される。第２リングギア部材１０８は、第２ギア部１０８Ａを含む。第２ギア部１０８Ａは、第３リングギア９４および第４リングギア１０２として共用される。第３遊星ギア９６および第４遊星ギア１０４は、第２遊星ギア部材１１０に形成される。第２遊星ギア部材１１０は、いわゆる段付きの遊星ギアを構成する。第３キャリア９８および第４キャリア１０６は、一体に形成される。   The third planetary mechanism 68 is configured to accelerate and output the rotation from the input body 58. The fourth planetary mechanism 70 is configured to accelerate and output the rotation from the input body 58. The number of teeth of the third sun gear 92 is smaller than the number of teeth of the fourth sun gear 100. The number of teeth of the third planetary gear 96 is larger than the number of teeth of the fourth planetary gear 104. The number of teeth of the third ring gear 94 and the number of teeth of the fourth ring gear 102 are equal. The third ring gear 94 and the fourth ring gear 102 are formed on the second ring gear member 108. The second ring gear member 108 includes a second gear portion 108A. The second gear portion 108 </ b> A is shared as the third ring gear 94 and the fourth ring gear 102. The third planetary gear 96 and the fourth planetary gear 104 are formed on the second planetary gear member 110. The second planetary gear member 110 constitutes a so-called stepped planetary gear. The third carrier 98 and the fourth carrier 106 are integrally formed.

設定機構５４は、入力体５８の回転の伝達機構５２における変速経路Ｓを設定する。設定機構５４は、複数の変速経路Ｓのうちの１つを設定する。複数の変速経路Ｓは、第１変速経路Ｓ１０（図８）を含む。複数の変速経路Ｓは、第２変速経路Ｓ２０（図９）をさらに含む。伝達機構５２は、入力体５８の回転を変速せずに出力体６０に出力する無変速経路Ｓ０（図７）をさらに形成する。   The setting mechanism 54 sets the speed change path S in the rotation transmission mechanism 52 of the input body 58. The setting mechanism 54 sets one of the plurality of shift paths S. The plurality of shift paths S include a first shift path S10 (FIG. 8). The plurality of shift paths S further includes a second shift path S20 (FIG. 9). The transmission mechanism 52 further forms a non-transmission path S0 (FIG. 7) for outputting the rotation of the input body 58 to the output body 60 without shifting.

図３に示されるとおり、設定機構５４は、第１設定部材１１２、第２設定部材１１４、第３設定部材１１６、第４設定部材１１８、制御部材１２０、スリーブ１２２、第１切替部１２４、および、第２切替部１２６を含む。   As shown in FIG. 3, the setting mechanism 54 includes a first setting member 112, a second setting member 114, a third setting member 116, a fourth setting member 118, a control member 120, a sleeve 122, a first switching unit 124, and The second switching unit 126 is included.

第１設定部材１１２は、支持部材５６に対して回転可能な回転状態と回転不能な規制状態とのいずれか一方に第１太陽ギア７２を設定する。第２設定部材１１４は、支持部材５６に対して回転可能な回転状態と回転不能な規制状態とのいずれか一方に第２太陽ギア８０を設定する。第３設定部材１１６は、支持部材５６に対して回転可能な回転状態と回転不能な規制状態とのいずれか一方に第３太陽ギア９２を設定する。第４設定部材１１８は、支持部材５６に対して回転可能な回転状態と回転不能な規制状態とのいずれか一方に第４太陽ギア１００を設定する。   The first setting member 112 sets the first sun gear 72 in one of a rotation state that is rotatable with respect to the support member 56 and a restriction state that is not rotatable. The second setting member 114 sets the second sun gear 80 in either one of a rotation state that is rotatable with respect to the support member 56 and a restriction state that is not rotatable. The third setting member 116 sets the third sun gear 92 in one of a rotation state that is rotatable with respect to the support member 56 and a restriction state that is not rotatable. The fourth setting member 118 sets the fourth sun gear 100 in one of a rotation state that is rotatable with respect to the support member 56 and a restriction state that is not rotatable.

制御部材１２０は、支持部材５６まわりに支持部材５６に対して回転可能に設けられる。制御部材１２０は、インナケーブルＣ１の端部が接続される回転体Ｃ２（図２参照）に接続されて、回転体Ｃ２と一体に回転する。回転体Ｃ２は、操作部４４（図１参照）の操作によってインナケーブルＣ１が移動すると回転する。このため、制御部材１２０も回転体Ｃ２の回転に伴って支持部材５６まわりで回転する。   The control member 120 is provided around the support member 56 so as to be rotatable with respect to the support member 56. The control member 120 is connected to a rotating body C2 (see FIG. 2) to which an end of the inner cable C1 is connected, and rotates integrally with the rotating body C2. The rotating body C2 rotates when the inner cable C1 moves by operating the operation unit 44 (see FIG. 1). For this reason, the control member 120 also rotates around the support member 56 with the rotation of the rotating body C2.

図４に示されるとおり、スリーブ１２２は、第１アーム部１２２Ａ、第２アーム部１２２Ｂ、第３アーム部１２２Ｃ、第４アーム部１２２Ｄ、および、ベース部１２２Ｅを備える。各アーム部１２２Ａ〜１２２Ｄは、支持部材５６の周方向に沿うように湾曲する。ベース部１２２Ｅは、支持部材５６の軸方向に延びて各アーム部１２２Ａ〜１２２Ｄを接続する。アーム部１２２Ａ〜１２２Ｄの数は、設定部材１１２，１１４，１１６，１１８の数と等しい。各アーム部１２２Ａ〜１２２Ｄには、各アーム部１２２Ａ〜１２２Ｄの延びる方向における端部または中間部に傾斜面が形成される。スリーブ１２２は、制御部材１２０に嵌め込まれ、支持部材５６まわりで制御部材１２０と一体に回転する。   As shown in FIG. 4, the sleeve 122 includes a first arm part 122A, a second arm part 122B, a third arm part 122C, a fourth arm part 122D, and a base part 122E. Each arm part 122A-122D curves so that the circumferential direction of support member 56 may be met. The base portion 122E extends in the axial direction of the support member 56 and connects the arm portions 122A to 122D. The number of arm portions 122A to 122D is equal to the number of setting members 112, 114, 116, and 118. Each arm part 122A-122D is formed with an inclined surface at an end or an intermediate part in the extending direction of each arm part 122A-122D. The sleeve 122 is fitted into the control member 120 and rotates integrally with the control member 120 around the support member 56.

図５に示されるとおり、第１設定部材１１２は、第１太陽ギア７２と支持部材５６との間に配置される。第１設定部材１１２は、爪部１１２Ａおよび第１アーム部１２２Ａの内周面に係合する係合部１１２Ｂを備える。第１アーム部１２２Ａが支持部材５６まわりで回転すると、係合部１１２Ｂが第１アーム部１２２Ａの傾斜面に沿って移動して、第１設定部材１１２が回転する。爪部１１２Ａが第１太陽ギア７２の内周部の凹部に向かって突出した状態（図５の実線）は、第１太陽ギア７２の支持部材５６に対して回転不能な規制状態を形成する。爪部１１２Ａが第１太陽ギア７２の内周部の凹部から抜け出した状態（図５の二点鎖線）は、第１太陽ギア７２の支持部材５６に対して回転可能な回転状態を形成する。図５では、第１設定部材１１２と第１太陽ギア７２と第１アーム部１２２Ａとの関係について説明したが、他の部材についても同様の構成によって太陽ギア８０，９２，１００を回転状態と規制状態とを形成する。第２太陽ギア８０は、第２設定部材１１４および第２アーム部１２２Ｂによって回転状態と規制状態とが形成される。第３太陽ギア９２は、第３設定部材１１６および第３アーム部１２２Ｃによって回転状態と規制状態とが形成される。第４太陽ギア１００は、第４設定部材１１８および第４アーム部１２２Ｄによって回転状態と規制状態とが形成される。   As shown in FIG. 5, the first setting member 112 is disposed between the first sun gear 72 and the support member 56. The first setting member 112 includes an engaging portion 112B that engages with the claw portion 112A and the inner peripheral surface of the first arm portion 122A. When the first arm portion 122A rotates around the support member 56, the engaging portion 112B moves along the inclined surface of the first arm portion 122A, and the first setting member 112 rotates. The state in which the claw portion 112 </ b> A protrudes toward the concave portion of the inner peripheral portion of the first sun gear 72 (a solid line in FIG. 5) forms a non-rotatable restricted state with respect to the support member 56 of the first sun gear 72. The state in which the claw portion 112 </ b> A has come out of the concave portion of the inner peripheral portion of the first sun gear 72 (two-dot chain line in FIG. 5) forms a rotational state that can rotate with respect to the support member 56 of the first sun gear 72. Although the relationship between the first setting member 112, the first sun gear 72, and the first arm portion 122A has been described with reference to FIG. State and form. The second sun gear 80 is rotated and regulated by the second setting member 114 and the second arm portion 122B. The third sun gear 92 is rotated and restricted by the third setting member 116 and the third arm portion 122C. As for the 4th sun gear 100, the rotation state and the regulation state are formed by the 4th setting member 118 and the 4th arm part 122D.

図４に示す設定機構５４は、第１太陽ギア７２および第２太陽ギア８０の一方が規制状態であれば、第１太陽ギア７２および第２太陽ギア８０の他方が回転状態であるように第１設定部材１１２と第２設定部材１１４とを制御する。設定機構５４は、第３太陽ギア９２および第４太陽ギア１００の一方が規制状態であれば、第３太陽ギア９２および第４太陽ギア１００の他方が回転状態であるように第３設定部材１１６と第４設定部材１１８とを制御する。設定機構５４は、スリーブ１２２の各アーム部各アーム部１２２Ａ〜１２２Ｄの傾斜面を周方向において異なる位置に設けることによって、各太陽ギア７２，８０，９２，１００の回転状態と規制状態とが切り替えられる制御部材１２０の回転位相を異ならせる。   When one of the first sun gear 72 and the second sun gear 80 is in a restricted state, the setting mechanism 54 shown in FIG. 4 is configured so that the other of the first sun gear 72 and the second sun gear 80 is in a rotating state. The first setting member 112 and the second setting member 114 are controlled. If one of the third sun gear 92 and the fourth sun gear 100 is in the restricted state, the setting mechanism 54 is configured so that the other of the third sun gear 92 and the fourth sun gear 100 is in the rotating state. And the fourth setting member 118 are controlled. The setting mechanism 54 switches the rotation state and the regulation state of the sun gears 72, 80, 92, 100 by providing the inclined surfaces of the arm portions 122 </ b> A to 122 </ b> D of the sleeve 122 at different positions in the circumferential direction. The rotation phase of the control member 120 to be controlled is varied.

第１切替部１２４および第２切替部１２６は、入力体５８の回転が第２変速機構６２Ｂによる変速を経由して出力体６０に出力される第１状態と、入力体５８の回転が第２変速機構６２Ｂによる変速を経由せずに出力体６０に出力される第２状態とを形成する。   The first switching unit 124 and the second switching unit 126 include a first state in which the rotation of the input body 58 is output to the output body 60 via a shift by the second transmission mechanism 62B, and the rotation of the input body 58 is the second. A second state is formed in which the gear is output to the output body 60 without passing through the speed change by the speed change mechanism 62B.

第１切替部１２４は、第１ワンウェイクラッチ１２４Ａを含む。第１ワンウェイクラッチ１２４Ａは、例えばローラクラッチである。第１ワンウェイクラッチ１２４Ａは、第２リングギア部材１０８と出力体６０との間に配置される。具体的には、第２リングギア部材１０８が第１ワンウェイクラッチ１２４Ａのインナレースと一体化され、出力体６０の内周部が第１ワンウェイクラッチ１２４Ａのアウタレースと一体化される。第１ワンウェイクラッチ１２４Ａは、第２リングギア部材１０８の回転速度が出力体６０の回転速度よりも遅い場合、第２リングギア部材１０８と出力体６０との相対回転を許容する。第１ワンウェイクラッチ１２４Ａは、第２リングギア部材１０８の回転速度が出力体６０の回転速度以上の場合、第１リングギア部材８８と出力体６０とを一体に回転させる。   First switching unit 124 includes a first one-way clutch 124A. The first one-way clutch 124A is, for example, a roller clutch. The first one-way clutch 124A is disposed between the second ring gear member 108 and the output body 60. Specifically, the second ring gear member 108 is integrated with the inner race of the first one-way clutch 124A, and the inner peripheral portion of the output body 60 is integrated with the outer race of the first one-way clutch 124A. The first one-way clutch 124 </ b> A allows relative rotation between the second ring gear member 108 and the output body 60 when the rotational speed of the second ring gear member 108 is slower than the rotational speed of the output body 60. The first one-way clutch 124 </ b> A rotates the first ring gear member 88 and the output body 60 together when the rotational speed of the second ring gear member 108 is equal to or higher than the rotational speed of the output body 60.

第２切替部１２６は、第２ワンウェイクラッチ１２６Ａを含む。第２ワンウェイクラッチ１２６Ａは、例えば爪を有するワンウェイクラッチである。第２ワンウェイクラッチ１２６Ａは、第３キャリア９８および第４キャリア１０６と、出力体６０との間に配置される。第２ワンウェイクラッチ１２６Ａは、第３キャリア９８および第４キャリア１０６の回転を出力体６０に伝達し、出力体６０の回転を第３キャリア９８および第４キャリア１０６に伝達しない。   Second switching unit 126 includes a second one-way clutch 126A. The second one-way clutch 126A is a one-way clutch having a pawl, for example. The second one-way clutch 126 </ b> A is disposed between the third carrier 98 and the fourth carrier 106 and the output body 60. The second one-way clutch 126 </ b> A transmits the rotation of the third carrier 98 and the fourth carrier 106 to the output body 60 and does not transmit the rotation of the output body 60 to the third carrier 98 and the fourth carrier 106.

第１太陽ギア７２および第２太陽ギア８０の両方が回転状態にあり、第３太陽ギア９２および第４太陽ギア１００の両方が回転状態にある場合、第１遊星機構６４、第２遊星機構６６、第３遊星機構６８、および、第４遊星機構７０に入力された回転は増速されない。このため、入力体５８の回転は、第１遊星機構６４、第２遊星機構６６、第３遊星機構６８、および、第４遊星機構７０による変速を経由せずに第１切替部１２４を介して出力体６０に出力される。第３キャリア９８および第４キャリア１０６と出力体６０との相対回転は、第２切替部１２６によって許容される。   When both the first sun gear 72 and the second sun gear 80 are in a rotating state and both the third sun gear 92 and the fourth sun gear 100 are in a rotating state, the first planetary mechanism 64 and the second planetary mechanism 66 The rotations input to the third planetary mechanism 68 and the fourth planetary mechanism 70 are not accelerated. For this reason, the rotation of the input body 58 does not pass through the first planetary mechanism 64, the second planetary mechanism 66, the third planetary mechanism 68, and the fourth planetary mechanism 70, and does not pass through the first switching unit 124. It is output to the output body 60. Relative rotation between the third carrier 98 and the fourth carrier 106 and the output body 60 is allowed by the second switching unit 126.

第１太陽ギア７２および第２太陽ギア８０の一方が規制状態にあり、第３太陽ギア９２および第４太陽ギア１００の両方が回転状態にある場合、第３遊星機構６８および第４遊星機構７０に入力された回転は増速されない。このため、入力体５８の回転は、第３遊星機構６８および第４遊星機構７０による変速を経由せずに第１切替部１２４を介して出力体６０に出力される。第３キャリア９８および第４キャリア１０６と出力体６０との相対回転は、第２切替部１２６によって許容される。   When one of the first sun gear 72 and the second sun gear 80 is in a restricted state and both the third sun gear 92 and the fourth sun gear 100 are in a rotating state, the third planetary mechanism 68 and the fourth planetary mechanism 70 The rotation input to is not accelerated. For this reason, the rotation of the input body 58 is output to the output body 60 via the first switching unit 124 without passing through the speed change by the third planetary mechanism 68 and the fourth planetary mechanism 70. Relative rotation between the third carrier 98 and the fourth carrier 106 and the output body 60 is allowed by the second switching unit 126.

第１太陽ギア７２および第２太陽ギア８０の一方が規制状態にあり、第３太陽ギア９２および第４太陽ギア１００の一方が規制状態にある場合、第３遊星機構６８または第４遊星機構７０に入力された回転は増速される。このため、入力体５８の回転は、第３遊星機構６８または第４遊星機構７０による変速を経由して第２切替部１２６を介して出力体６０に出力される。   When one of the first sun gear 72 and the second sun gear 80 is in a restricted state and one of the third sun gear 92 and the fourth sun gear 100 is in a restricted state, the third planetary mechanism 68 or the fourth planetary mechanism 70 The rotation input to is increased. Therefore, the rotation of the input body 58 is output to the output body 60 via the second switching unit 126 via the speed change by the third planetary mechanism 68 or the fourth planetary mechanism 70.

伝達機構５２は、第１変速経路Ｓ１０および第２変速経路Ｓ２０を少なくとも形成する。第１変速経路Ｓ１０は、少なくとも第１変速機構６２Ａでの変速を経由して、入力体５８からの回転を３段階以上の変速比のうちの第１変速比および第２変速比の一方で出力体６０に伝達する。第２変速経路Ｓ２０は、第１変速経路Ｓ１０において経由される変速機構６２とは異なる第２変速機構６２Ｂでの変速を経由して、入力体５８からの回転を第１変速比および第２変速比よりも大きい変速比で出力体６０に伝達する。   The transmission mechanism 52 forms at least a first shift path S10 and a second shift path S20. The first speed change path S10 outputs at least one of the first speed ratio and the second speed ratio among the speed ratios of three or more stages through the rotation from the input body 58 via the speed change in the first speed change mechanism 62A. Transmitted to the body 60. The second speed change path S20 changes the rotation from the input body 58 through the speed change in the second speed change mechanism 62B different from the speed change mechanism 62 passed in the first speed change path S10. It is transmitted to the output body 60 at a gear ratio larger than the ratio.

第１変速経路Ｓ１０は、第１遊星変速経路Ｓ１１および第２遊星変速経路Ｓ１２を含む。第１遊星変速経路Ｓ１１は、第１遊星機構６４での変速を経由し第２遊星機構６６での変速を経由せず入力体５８からの回転を第１変速比で出力体６０に伝達する。第２遊星変速経路Ｓ１２は、第１遊星機構６４での変速を経由せず第２遊星機構６６での変速を経由して入力体５８からの回転を第２変速比で出力体６０に伝達する。   The first speed change path S10 includes a first planetary speed change path S11 and a second planetary speed change path S12. The first planetary speed change path S11 transmits the rotation from the input body 58 to the output body 60 at the first speed ratio without going through the speed change at the second planetary mechanism 66 via the speed change at the first planetary mechanism 64. The second planetary speed change path S12 transmits the rotation from the input body 58 to the output body 60 at the second speed ratio through the speed change at the second planetary mechanism 66 without going through the speed change at the first planetary mechanism 64. .

設定機構５４は、第２変速経路Ｓ２０において第１遊星機構６４での変速を経由しないように伝達機構５２を設定する。第２変速経路Ｓ２０は、第３遊星変速経路Ｓ２１および第４遊星変速経路Ｓ２２を含む。第３遊星変速経路Ｓ２１は、第３遊星機構６８での変速を経由し第４遊星機構７０での変速を経由せず入力体５８からの回転を第２変速比よりも大きい第３変速比で出力体６０に伝達する。第４遊星変速経路Ｓ２２は、第３遊星機構６８での変速を経由せず第４遊星機構７０での変速を経由して入力体５８からの回転を第３変速比よりも大きい第４変速比で出力体６０に伝達する。   The setting mechanism 54 sets the transmission mechanism 52 so as not to pass through the shift in the first planetary mechanism 64 in the second shift path S20. The second speed change path S20 includes a third planetary speed change path S21 and a fourth planetary speed change path S22. The third planetary speed change path S21 passes through the speed change in the third planetary mechanism 68 and does not pass the speed change in the fourth planetary mechanism 70, and rotates from the input body 58 at a third speed ratio larger than the second speed ratio. This is transmitted to the output body 60. The fourth planetary speed change path S22 is a fourth speed change ratio in which the rotation from the input body 58 is larger than the third speed change ratio through the speed change in the fourth planetary mechanism 70 without passing through the speed change in the third planetary mechanism 68. To the output body 60.

図６〜図１１および表１を参照して、各変速段と伝達機構５２の構成要素との関係を説明する。
図６および表１に示されるとおり、第１変速段では、第１太陽ギア７２が回転状態にあり、第２太陽ギア８０が回転状態にあり、第３太陽ギア９２が回転状態にあり、かつ、第４太陽ギア１００が回転状態にある。図７に示されるとおり、第１変速段では、変速経路Ｓは無変速経路Ｓ０を形成する。この場合、変速比は、最小変速比Ｒ０である。最小変速比Ｒ０は、「１」である。 With reference to FIGS. 6 to 11 and Table 1, the relationship between each shift stage and the components of the transmission mechanism 52 will be described.
As shown in FIG. 6 and Table 1, at the first speed, the first sun gear 72 is in the rotating state, the second sun gear 80 is in the rotating state, the third sun gear 92 is in the rotating state, and The fourth sun gear 100 is in a rotating state. As shown in FIG. 7, at the first speed, the speed change path S forms a non-speed change path S0. In this case, the speed ratio is the minimum speed ratio R0. The minimum speed ratio R0 is “1”.

図６および表１に示されるとおり、第２変速段では、第１太陽ギア７２が規制状態にあり、第２太陽ギア８０が回転状態にあり、第３太陽ギア９２が回転状態にあり、かつ、第４太陽ギア１００が回転状態にある。図８に示されるとおり、第２変速段では、変速経路Ｓは、第１増速経路Ｓ１を形成する。第１増速経路Ｓ１は、第１変速経路Ｓ１０を経由し、第２変速経路Ｓ２０を経由しない。変速経路Ｓは、第１変速経路Ｓ１０のうちの第１遊星変速経路Ｓ１１のみを経由する第１増速経路を形成する。この場合、変速比は最小変速比Ｒ０よりも大きい第１増速比Ｒ１になる。   As shown in FIG. 6 and Table 1, at the second speed, the first sun gear 72 is in a restricted state, the second sun gear 80 is in a rotating state, the third sun gear 92 is in a rotating state, and The fourth sun gear 100 is in a rotating state. As shown in FIG. 8, at the second speed, the speed change path S forms a first speed increase path S1. The first speed increase path S1 passes through the first speed change path S10 and does not pass through the second speed change path S20. The speed change path S forms a first speed increasing path that passes only through the first planetary speed change path S11 of the first speed change path S10. In this case, the gear ratio becomes the first speed increase ratio R1 that is larger than the minimum speed ratio R0.

図６および表１に示されるとおり、第３変速段では、第１太陽ギア７２が規制状態にあり、第２太陽ギア８０が回転状態にあり、第３太陽ギア９２が規制状態にあり、かつ、第４太陽ギア１００が回転状態にある。図９に示されるとおり、第３変速段では、変速経路Ｓは、第２増速経路Ｓ２を形成する。第２増速経路Ｓ２は、第１変速経路Ｓ１０および第２変速経路Ｓ２０を経由する。変速経路Ｓは、第１変速経路Ｓ１０のうちの第１遊星変速経路Ｓ１１、および、第２変速経路Ｓ２０のうちの第３遊星変速経路Ｓ２１を経由する第２増速経路を形成する。この場合、変速比は第１増速比Ｒ１よりも大きい第２増速比Ｒ２になる。   As shown in FIG. 6 and Table 1, at the third speed, the first sun gear 72 is in a restricted state, the second sun gear 80 is in a rotating state, the third sun gear 92 is in a restricted state, and The fourth sun gear 100 is in a rotating state. As shown in FIG. 9, at the third speed, the speed change path S forms a second speed increase path S2. The second speed increase path S2 passes through the first speed change path S10 and the second speed change path S20. The speed change path S forms a second speed increase path that passes through the first planetary speed change path S11 in the first speed change path S10 and the third planetary speed change path S21 in the second speed change path S20. In this case, the gear ratio becomes a second speed increase ratio R2 that is larger than the first speed increase ratio R1.

図６および表１に示されるとおり、第４変速段では、第１太陽ギア７２が規制状態にあり、第２太陽ギア８０が回転状態にあり、第３太陽ギア９２が回転状態にあり、かつ、第４太陽ギア１００が規制状態にある。図１０に示されるとおり、第３変速段では、変速経路Ｓは、第３増速経路Ｓ３を形成する。第３増速経路Ｓ３は、第１変速経路Ｓ１０および第２変速経路Ｓ２０を経由する。変速経路Ｓは、第１変速経路Ｓ１０のうちの第１遊星変速経路Ｓ１１、および、第２変速経路Ｓ２０のうちの第４遊星変速経路Ｓ２２を経由する第３増速経路を形成する。この場合、変速比は第２増速比Ｒ２よりも大きい第３増速比Ｒ３になる。   As shown in FIG. 6 and Table 1, at the fourth speed, the first sun gear 72 is in a restricted state, the second sun gear 80 is in a rotating state, the third sun gear 92 is in a rotating state, and The fourth sun gear 100 is in a restricted state. As shown in FIG. 10, at the third speed, the speed change path S forms a third speed increase path S3. The third speed increase path S3 passes through the first speed change path S10 and the second speed change path S20. The speed change path S forms a third speed increase path via the first planetary speed change path S11 in the first speed change path S10 and the fourth planetary speed change path S22 in the second speed change path S20. In this case, the transmission gear ratio becomes a third speed increase ratio R3 that is larger than the second speed increase ratio R2.

図６および表１に示されるとおり、第５変速段では、第１太陽ギア７２が回転状態にあり、第２太陽ギア８０が規制状態にあり、第３太陽ギア９２が回転状態にあり、かつ、第４太陽ギア１００が規制状態にある。図１１に示されるとおり、第５変速段では、変速経路Ｓは、第４増速経路Ｓ４を形成する。第４増速経路Ｓ４は、第１変速経路Ｓ１０および第２変速経路Ｓ２０を経由する。変速経路Ｓは、第１変速経路Ｓ１０のうちの第２遊星変速経路Ｓ１２、および、第２変速経路Ｓ２０のうちの第４遊星変速経路Ｓ２２を経由する第４増速経路を形成する。この場合、変速比は第３増速比Ｒ３よりも大きい第４増速比Ｒ４になる。   As shown in FIG. 6 and Table 1, at the fifth speed, the first sun gear 72 is in the rotating state, the second sun gear 80 is in the restricted state, the third sun gear 92 is in the rotating state, and The fourth sun gear 100 is in a restricted state. As shown in FIG. 11, at the fifth shift speed, the speed change path S forms a fourth speed increase path S4. The fourth speed increase path S4 passes through the first speed change path S10 and the second speed change path S20. The speed change path S forms a fourth speed increasing path via the second planetary speed change path S12 in the first speed change path S10 and the fourth planetary speed change path S22 in the second speed change path S20. In this case, the transmission gear ratio becomes the fourth speed increase ratio R4 that is larger than the third speed increase ratio R3.

表２は、本実施形態の各遊星機構６４，６６，６８，７０のギアの歯数の一例を示す。   Table 2 shows an example of the number of gear teeth of each planetary mechanism 64, 66, 68, 70 of the present embodiment.

表３を参照して、各変速段における変速比について説明する。「差ｄＡ」は、５つ以上の変速段のうち連続する３つの変速段において、最小変速段の変速比に対する中間変速段の変速比の比率Ｐから、中間変速段の変速比に対する最大変速段の変速比の比率Ｐを減算した差（変速ステップ）を示す。表３に示す自転車用変速機５０の変速段は５つである。   With reference to Table 3, the gear ratio in each gear stage will be described. “Difference dA” is the maximum shift speed with respect to the gear ratio of the intermediate gear, from the ratio P of the gear ratio of the intermediate gear to the gear ratio of the minimum gear in three consecutive gears among the five or more gears. The difference (shift step) obtained by subtracting the ratio P of the gear ratio is shown. The bicycle transmission 50 shown in Table 3 has five shift stages.

変速機構６２では、差（変速ステップ）ｄＡは、いずれの連続する３つの変速段においても正である。５つの変速段は、変速機構６２において最小である変速段を含む。差ｄＡの絶対値は、０．０３以上０．１５以下である。好ましくは、差ｄＡの絶対値は、０．０４以上０．１以下である。   In the speed change mechanism 62, the difference (speed change step) dA is positive in any three consecutive gear positions. The five shift speeds include the speed that is the smallest in the speed change mechanism 62. The absolute value of the difference dA is not less than 0.03 and not more than 0.15. Preferably, the absolute value of the difference dA is 0.04 or more and 0.1 or less.

差ｄＡは、いずれの連続する３つの変速段においても正である。具体的には、差ｄＡは、第１〜３変速段、第２〜４変速段、および、第３〜５変速段のいずれにおいても正である。差ｄＡのうちの１つから差ｄＡのうちの他の１つを減算した値ｄＸの絶対値は、０．００５以上０．０２以下である。   The difference dA is positive at any three consecutive gear positions. Specifically, the difference dA is positive in any of the first to third shift speeds, the second to fourth shift speeds, and the third to fifth shift speeds. The absolute value of the value dX obtained by subtracting the other one of the differences dA from one of the differences dA is not less than 0.005 and not more than 0.02.

図１２を参照して、自転車用変速機５０の作用について説明する。
図１２の実線Ｌ１１は、自転車用変速機５０の第１変速段を用いた場合のケイデンスと車速との関係を示す。実線Ｌ１２は、自転車用変速機５０の第２変速段を用いた場合のケイデンスと車速との関係を示す。実線Ｌ１３は、自転車用変速機５０の第３変速段を用いた場合のケイデンスと車速との関係を示す。実線Ｌ１４は、自転車用変速機５０の第４変速段を用いた場合のケイデンスと車速との関係を示す。実線Ｌ１５は、自転車用変速機５０の第５変速段を用いた場合のケイデンスと車速との関係を示す。 The operation of the bicycle transmission 50 will be described with reference to FIG.
A solid line L11 in FIG. 12 shows the relationship between the cadence and the vehicle speed when the first shift stage of the bicycle transmission 50 is used. A solid line L12 indicates the relationship between the cadence and the vehicle speed when the second shift stage of the bicycle transmission 50 is used. A solid line L13 indicates the relationship between the cadence and the vehicle speed when the third shift stage of the bicycle transmission 50 is used. A solid line L14 indicates the relationship between the cadence and the vehicle speed when the fourth shift stage of the bicycle transmission 50 is used. A solid line L15 indicates the relationship between cadence and vehicle speed when the fifth shift stage of the bicycle transmission 50 is used.

図１２の二点鎖線Ｌ２１は、比率Ｐが常に「０」である仮想の自転車用変速機の第１変速段を用いた場合のケイデンスと車速との関係を示す。二点鎖線Ｌ２２は、仮想の自転車用変速機５０の第２変速段を用いた場合のケイデンスと車速との関係を示す。二点鎖線Ｌ２３は、仮想の自転車用変速機の第３変速段を用いた場合のケイデンスと車速との関係を示す。二点鎖線Ｌ２４は、仮想の自転車用変速機の第４変速段を用いた場合のケイデンスと車速との関係を示す。二点鎖線Ｌ２５は、仮想の自転車用変速機の第５変速段を用いた場合のケイデンスと車速との関係を示す。   A two-dot chain line L21 in FIG. 12 shows the relationship between the cadence and the vehicle speed when the first shift stage of the virtual bicycle transmission in which the ratio P is always “0” is used. A two-dot chain line L22 indicates the relationship between the cadence and the vehicle speed when the second shift stage of the virtual bicycle transmission 50 is used. An alternate long and two short dashes line L23 indicates the relationship between the cadence and the vehicle speed when the third shift stage of the virtual bicycle transmission is used. A two-dot chain line L24 indicates a relationship between cadence and vehicle speed when the fourth shift stage of the virtual bicycle transmission is used. A two-dot chain line L25 indicates a relationship between cadence and vehicle speed when the fifth shift stage of the virtual bicycle transmission is used.

例えばケイデンスが７０ｒｐｍまで上昇したときに変速段を１段階上昇させて自転車１０の車速を上昇させるような走行を行う場合、仮想の自転車用変速機では、変速段が小さいほど変速段を上昇させる操作を操作部４４に行うまでの期間が短い。具体的には、第１変速段でケイデンスが７０ｒｐｍまで上昇して第２変速段に変更するまでの車速の変化量が、第２変速段でケイデンスが７０ｒｐｍまで上昇して第３変速段に変更するまでの車速の変化量よりも小さい。このため、変速段が小さいほど変速段を上昇させる操作が頻繁に行われる。   For example, when traveling to increase the vehicle speed of the bicycle 10 by increasing the gear position by one step when the cadence increases to 70 rpm, in a virtual bicycle transmission, the operation to increase the gear step as the gear step decreases. The period until the operation unit 44 is performed is short. Specifically, the amount of change in the vehicle speed until the cadence increases to 70 rpm at the first gear and changes to the second gear, the cadence increases to 70 rpm at the second gear and changes to the third gear. Less than the amount of change in vehicle speed until For this reason, the operation of raising the gear position is performed more frequently as the gear position is smaller.

他方、自転車用変速機５０では、変速段の大きさに関わらず、変速段を上昇させる操作を操作部４４に行うまでの期間が所定の範囲内に維持される。このため、運転者は変速段の変更のための操作を車速の変化に対して安定したタイミングで行うことができる。   On the other hand, in the bicycle transmission 50, the period until the operation unit 44 is operated to raise the shift speed is maintained within a predetermined range regardless of the size of the shift speed. For this reason, the driver can perform an operation for changing the gear position at a stable timing with respect to a change in the vehicle speed.

（変形例）
上記実施形態に関する説明は、本発明に従う自転車用変速機およびこれを備える自転車用アシストシステムが取り得る形態の例示であり、その形態を制限することを意図していない。本発明に従う自転車用変速機およびこれを備える自転車用アシストシステムは、例えば以下に示される上記実施形態の変形例、および、相互に矛盾しない少なくとも２つの変形例が組み合わせられた形態を取り得る。以下の変形例において、実施形態の形態と共通する部分については、実施形態と同一の符号を付してその説明を省略する。 (Modification)
The above description of the embodiment is an example of a form that the bicycle transmission according to the present invention and the bicycle assist system including the same can take, and is not intended to limit the form. The bicycle transmission according to the present invention and the bicycle assist system including the same can take a form in which, for example, the modifications of the above-described embodiment described below and at least two modifications not contradicting each other are combined. In the following modified examples, the same reference numerals as those in the embodiment are given to portions common to the embodiment, and the description thereof is omitted.

・変速機構６２の段階的に変速比が大きくなるように構成される５つの変速段において、差ｄＡの絶対値を０．０３未満、または、０．１５よりも大きく設定することもできる。
・５つ以上の変速段のうちの４つの変速段の連続する３つの変速段において、差ｄＡをいずれの連続する３つの変速段においても正および負の一方とし、かつ、その差ｄＡの絶対値は、いずれも０．０３以上０．１５以下とすることもできる。この場合、４つの変速段に含まれない変速段を含む連続する３つの変速段における差ｄＡを「０」に設定することもできる。４つの変速段に含まれない変速段は、上記実施形態では第１変速段または第５変速段である。
・５つ以上の変速段のうち連続する３つの変速段において差ｄＡを負に設定することもできる。 The absolute value of the difference dA can be set to be less than 0.03 or greater than 0.15 in five shift stages configured so that the speed ratio of the speed change mechanism 62 increases stepwise.
The difference dA is set to one of positive and negative in any three consecutive shift speeds in four consecutive shift speeds among five or more shift speeds, and the absolute difference dA Any of the values may be 0.03 or more and 0.15 or less. In this case, the difference dA in three consecutive shift stages including a shift stage not included in the four shift stages can be set to “0”. The shift speeds not included in the four shift speeds are the first shift speed or the fifth shift speed in the embodiment.
The difference dA can be set to be negative in three consecutive gears among five or more gears.

・自転車用変速機５０が６つ以上の変速段を含むようにすることもできる。この場合も、６つの変速段のうち連続する３つの変速段においても、差ｄＡは、いずれの連続する３つの変速段においても正および負の一方である。自転車用変速機５０が６段階以上の変速段を含む場合、連続する５つの変速段のうちの連続する３つの変速段における差ｄＡを正および負の一方とし、この連続する５つの変速段以外の変速段を含む３つの変速段における差ｄＡを正および負の他方にしてもよい。また、この連続する５つの変速段以外の変速段を含む３つの変速段における差ｄＡを正および負の他方ではなく、「０」にしてもよい。   The bicycle transmission 50 can include six or more shift stages. Also in this case, the difference dA is one of positive and negative in any three consecutive gears even in three consecutive gears out of the six gears. When the bicycle transmission 50 includes six or more speeds, the difference dA in three consecutive speeds out of the five consecutive speeds is set to one of positive and negative, and other than the five consecutive speeds The difference dA in the three shift speeds including these shift speeds may be the other of positive and negative. Further, the difference dA in the three shift stages including the shift stages other than the five consecutive shift stages may be set to “0” instead of the other of positive and negative.

・差ｄＡのうちの１つから差ｄＡのうちの他の１つを減算した値ｄＸの絶対値が、０．００５未満、または、０．０２より大きくなるように設定することもできる。   The absolute value of the value dX obtained by subtracting the other one of the differences dA from one of the differences dA may be set to be less than 0.005 or greater than 0.02.

・モータ４２を含まない自転車１０に自転車用変速機５０を搭載することもできる。この場合も、自転車の車速に対する変速段の変更を一定に行うという要求を実現できるため、ユーザビリティに貢献できる。   The bicycle transmission 50 can be mounted on the bicycle 10 that does not include the motor 42. In this case as well, it is possible to realize a requirement to change the gear position with respect to the bicycle vehicle speed, which can contribute to usability.

・自転車用変速機５０をクランク軸２０Ａまわりに設けることもできる。この場合、自転車用変速機５０は、クランク軸２０Ａに入力された回転を変速してフロント回転体２４に出力する。   The bicycle transmission 50 can be provided around the crankshaft 20A. In this case, the bicycle transmission 50 shifts the rotation input to the crankshaft 20 </ b> A and outputs it to the front rotating body 24.

・第１〜４遊星機構６４，６６，６８，７０の少なくとも１つを遊星ローラ機構にすることもできる。
・第１〜４遊星機構６４，６６，６８，７０の第１遊星ギア７６、第２遊星ギア８４、第３遊星ギア９６、および、第４遊星ギア１０４を１つの部材に設け、４段階の段付き遊星ギアとすることもできる。
・第１〜４遊星機構６４，６６，６８，７０の少なくとも１つを入力された回転を減速して出力する機構にすることもできる。 -At least one of the first to fourth planetary mechanisms 64, 66, 68, 70 may be a planetary roller mechanism.
The first planetary gear 76, the second planetary gear 84, the third planetary gear 96, and the fourth planetary gear 104 of the first to fourth planetary mechanisms 64, 66, 68, and 70 are provided in one member, and are in four stages. It can also be a planetary gear with steps.
-At least one of the first to fourth planetary mechanisms 64, 66, 68, 70 may be a mechanism that decelerates and outputs the input rotation.

・自転車１０に、自転車用変速機５０を制御する制御部を設けることもできる。例えば、制御部はケイデンスが所定の範囲になるように自転車用変速機５０を制御して変速段を変更する。この場合も、制御部が自転車用変速機５０を制御するタイミングが車速に対して一定になるため、運転者が違和感を覚えにくい。   The bicycle 10 may be provided with a control unit that controls the bicycle transmission 50. For example, the control unit changes the gear position by controlling the bicycle transmission 50 so that the cadence falls within a predetermined range. Also in this case, since the timing at which the control unit controls the bicycle transmission 50 is constant with respect to the vehicle speed, it is difficult for the driver to feel uncomfortable.

１０…自転車、１８Ｃ…ハブ、４０…自転車用アシストシステム、４２…モータ、４４…操作部、５０…自転車用変速機、６２…変速機構。   DESCRIPTION OF SYMBOLS 10 ... Bicycle, 18C ... Hub, 40 ... Bicycle assist system, 42 ... Motor, 44 ... Operation part, 50 ... Bicycle transmission, 62 ... Transmission mechanism.

Claims (13)

段階的に変速比が大きくなるように構成される５つ以上の変速段を含む変速機構を備え、
前記５つ以上の変速段のうち連続する３つの変速段において、最小変速段の変速比に対する中間変速段の変速比の比率から、前記中間変速段の変速比に対する最大変速段の変速比の比率を減算すると、その差は、いずれの前記連続する３つの変速段においても正および負の一方である、自転車用変速機。 A speed change mechanism including five or more speed stages configured so that the speed ratio increases stepwise;
The ratio of the gear ratio of the maximum gear ratio to the gear ratio of the intermediate gear speed from the ratio of the gear ratio of the intermediate gear speed to the gear ratio of the minimum gear speed in three consecutive gear speeds among the five or more gear speeds. Is a bicycle transmission in which the difference is one of positive and negative at any of the three consecutive gears. 前記５つ以上の変速段は、前記変速機構において最小である変速段を含む、請求項１に記載の自転車用変速機。   The bicycle transmission according to claim 1, wherein the five or more shift stages include a shift stage that is the smallest in the transmission mechanism. 前記差の絶対値は、０．０３以上０．１５以下である、請求項１または２に記載の自転車用変速機。   The bicycle transmission according to claim 1 or 2, wherein an absolute value of the difference is 0.03 or more and 0.15 or less. 段階的に変速比が大きくなるように構成される４つ以上の変速段を含む変速機構を備え、
前記４つ以上の変速段のうち連続する３つの変速段において、最小変速段の変速比に対する中間変速段の変速比の比率から、前記中間変速段の変速比に対する最大変速段の変速比の比率を減算すると、その差は、いずれの前記連続する３つの変速段においても正および負の一方であり、かつ、その差の絶対値は、いずれも０．０３以上０．１５以下である、自転車用変速機。 A transmission mechanism including four or more shift stages configured so that a gear ratio increases stepwise;
The ratio of the gear ratio of the maximum gear ratio to the gear ratio of the intermediate gear speed from the ratio of the gear ratio of the intermediate gear speed to the gear ratio of the minimum gear speed in three consecutive gear speeds among the four or more gear speeds. The difference is one of positive and negative at any of the three consecutive shift speeds, and the absolute value of the difference is 0.03 or more and 0.15 or less. Transmission. 前記４つ以上の変速段は、前記変速機構において最小である変速段を含む、請求項４に記載の自転車用変速機。   The bicycle transmission according to claim 4, wherein the four or more shift stages include a shift stage that is the smallest in the transmission mechanism. 前記変速機構は、段階的に変速比が大きくなるように構成される５つ以上の変速段を含み、
前記連続する３つの変速段は、前記５つ以上の変速段に含まれる、請求項４または５に記載の自転車用変速機。 The speed change mechanism includes five or more speed stages that are configured so that the speed ratio increases stepwise.
The bicycle transmission according to claim 4 or 5, wherein the three consecutive shift speeds are included in the five or more shift speeds. 前記差の絶対値は、０．０４以上０．１以下である、請求項３〜６のいずれか一項に記載の自転車用変速機。   The bicycle transmission according to any one of claims 3 to 6, wherein an absolute value of the difference is 0.04 or more and 0.1 or less. 前記差は、いずれの前記連続する３つの変速段においても正である、請求項１〜７のいずれか一項に記載の自転車用変速機。   The bicycle transmission according to any one of claims 1 to 7, wherein the difference is positive in any of the three consecutive gear positions. 前記差のうちの１つから前記差のうちの他の１つを減算した値の絶対値は、０．００５以上０．０２以下である、請求項１〜８のいずれか一項に記載の自転車用変速機。   The absolute value of a value obtained by subtracting the other one of the differences from one of the differences is 0.005 or more and 0.02 or less, according to any one of claims 1 to 8. Bicycle transmission. 前記変速機構は、内装変速機構である、請求項１〜９のいずれか一項に記載の自転車用変速機。   The bicycle transmission according to any one of claims 1 to 9, wherein the transmission mechanism is an internal transmission mechanism. 前記内装変速機構を収容するハブをさらに備える、請求項１０に記載の自転車用変速機。   The bicycle transmission according to claim 10, further comprising a hub that houses the internal speed change mechanism. 請求項１〜１１のいずれか一項に記載の自転車用変速機と、
人力駆動力をアシストするモータと、を備える、自転車用アシストシステム。 The bicycle transmission according to any one of claims 1 to 11,
A bicycle assist system comprising: a motor for assisting human driving force. 前記自転車用変速機を操作するために人の手によって操作される操作部をさらに備え、
前記自転車用変速機は、前記操作部への操作に応じて自転車の変速比を変更する、請求項１２に記載の自転車用アシストシステム。 An operation unit operated by a human hand to operate the bicycle transmission;
The bicycle assist system according to claim 12, wherein the bicycle transmission changes a bicycle gear ratio in accordance with an operation on the operation unit.
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WO2024014431A1 (en) * 2022-07-11 2024-01-18 本田技研工業株式会社 Gear stage estimation method, gear stage estimation device, gear stage estimation program, and storage medium

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CN108466671B (en) 2022-05-10
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TW201831370A (en) 2018-09-01
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CN108466671A (en) 2018-08-31
TWI742237B (en) 2021-10-11

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