TW202003328A - Pedaling bearing transmission in form of planet transmission for a bicycle or pedelec - Google Patents

Pedaling bearing transmission in form of planet transmission for a bicycle or pedelec Download PDF

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Publication number
TW202003328A
TW202003328A TW108118216A TW108118216A TW202003328A TW 202003328 A TW202003328 A TW 202003328A TW 108118216 A TW108118216 A TW 108118216A TW 108118216 A TW108118216 A TW 108118216A TW 202003328 A TW202003328 A TW 202003328A
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Taiwan
Prior art keywords
planetary gear
gear set
free wheel
gear
planetary
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TW108118216A
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Chinese (zh)
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TWI822784B (en
Inventor
彼得 齊瑪爾
克里斯多福 馬格雷夫
湯瑪斯 雷德瑟
歐利齊 朵爾
金 弗瑞爾
哈根 多普夫爾特
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德商查發傅利得利夏芬股份有限公司
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Publication of TWI822784B publication Critical patent/TWI822784B/en

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    • 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
    • B62M11/145—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears built in, or adjacent to, the bottom bracket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
    • 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
    • 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
    • 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
    • F16H2200/201—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
    • F16H2200/2046—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

Abstract

The invention relates to a planet-type bottom-bracket transmission for a bicycle or a pedelec, comprising a transmission input shaft (1) as the drive, a transmission output shaft (2) as the output, three planetary gear sets (RS1, RS2, RS3), three freewheel clutches (F1, F2, F3), and three brakes (B1, B2, B3) in order to implement eight gears (G1, G2, G3, G4, G5, G6, G7, G8). Each planetary gear set (RS1, RS2, RS3) is paired with a brake (B1, B2, B3) and a freewheel clutch (F1, F2, F3). A sun gear (4) of the first planetary gear set (RS1) can be fixed via the first brake (B1), a sun gear (7) of the second planetary gear set (RS2) can be fixed via the second brake (B2), and a ring gear (12) of the third planetary gear set (RS3) can be fixed via the third brake (B3). A planet carrier (5) of the first planetary gear set (RS1), a planet carrier (8) of the second planetary gear set (RS2), and a planet carrier (11) of the third planetary gear set (RS3) each forms the input of the respective planetary gear set (RS1, RS2, RS3), and a ring gear (6) of the first planetary gear set (RS1), a ring gear (9) of the second planetary gear set (RS2), and a sun gear (10) of the third planetary gear set (RS3) each forms the output of the respective planetary gear set (RS1, RS2, RS3). The invention additionally relates to a bicycle or a pedelec comprising the bottom-bracket transmission.

Description

用於自行車或電動自行車之行星齒輪結構的踩踏軸承齒輪箱Stepping bearing gear box for planetary gear structure of bicycle or electric bicycle

本發明係有關於一種用於自行車或電動自行車之行星結構的踩踏軸承齒輪箱。此外，本發明係有關於一種具有該踩踏軸承齒輪箱的自行車或電動自行車。The invention relates to a tread bearing gear box for planetary structure of bicycle or electric bicycle. In addition, the present invention relates to a bicycle or electric bicycle having the tread bearing gear box.

先前技術揭露大量一般配設有撥鏈器（Kettenschaltung，英：chain shifter）或齒輪輪轂（Nabenschaltung，英：hub gear-shifter）的自行車或電動自行車。電動自行車區別於自行車之處在於設有為騎行者提供助力的電機。在一些應用中，電動自行車的前輪或後輪中裝有輪轂馬達。前輪中的輪轂馬達由於重量大而不利於騎行行為。而設置在後輪中的輪轂馬達一直以來係與不易維護的齒輪輪轂配合使用，且同樣由於重量大而不利於騎行行為。因此，業界已開發出在踩踏軸承中設置副軸結構之齒輪箱以及電動馬達的電動自行車。習知的副軸結構之踩踏軸承齒輪箱的缺點在於功率密度低，且由於僅出現滾動功率（Wälzleistung）而效率低下。The prior art discloses a large number of bicycles or electric bicycles generally equipped with a derailleur (Kettenschaltung, English: chain shifter) or gear wheel hub (Nabenschaltung, English: hub gear-shifter). Electric bicycles differ from bicycles in that they are equipped with motors that provide assistance to cyclists. In some applications, hub motors are installed in the front or rear wheels of electric bicycles. The wheel hub motor in the front wheel is unfavorable for riding behavior due to its heavy weight. The hub motor provided in the rear wheel has been used in conjunction with a gear hub that is not easy to maintain, and it is also unfavorable for riding behavior due to its heavy weight. Therefore, the industry has developed an electric bicycle in which a stepped bearing is provided with a gearbox of an auxiliary shaft structure and an electric motor. The disadvantage of the conventional stepped bearing gearbox of the countershaft structure is that the power density is low, and the efficiency is low due to the occurrence of only rolling power (Wälzleistung).

本發明之目的在於提供一種踩踏軸承齒輪箱以及一種具有該踩踏軸承齒輪箱的自行車或電動自行車，二者擋位數多，功率密度大且效率高。The purpose of the present invention is to provide a tread bearing gear box and a bicycle or electric bicycle with the tread bearing gear box, both of which have a large number of gears, high power density and high efficiency.

根據本發明，此目的藉由請求項1及10之特徵而達成，其中，請求保護的有利改進方案可從附屬項以及說明書及圖式中獲得。According to the present invention, this object is achieved by the features of claims 1 and 10, wherein the advantageous improvements of the claims can be obtained from the appended items as well as the description and drawings.

因此，本發明提出一種用於自行車或電動自行車之行星結構的踩踏軸承齒輪箱，具有作為驅動裝置的齒輪箱輸入軸，例如踏板曲柄軸或類似之物，以及作為從動裝置之齒輪箱輸出軸。該踩踏軸承齒輪箱包括用於實現八個擋位的三個行星齒輪組、三個自由輪離合器及三個制動器，其中每個行星齒輪組分別對應於一個制動器及一個自由輪離合器。此外在該踩踏軸承齒輪箱中，該第一行星齒輪組的太陽輪可由第一制動器固定，該第二行星齒輪組的太陽輪可由第二制動器固定，以及該第三行星齒輪組的內齒圈可由第三制動器固定，其中該第一行星齒輪組的行星輪架及該第二行星齒輪組的行星輪架以及該第三行星齒輪組的行星輪架分別形成該等行星齒輪組上的輸入端，且其中該第一行星齒輪組的內齒圈及該第二行星齒輪組的內齒圈以及該第三行星齒輪組的太陽輪分別形成該等行星齒輪組上的輸出端。Therefore, the present invention proposes a planetary stepped bearing gearbox for bicycles or electric bicycles, having a gearbox input shaft as a driving device, such as a pedal crankshaft or the like, and a gearbox output shaft as a driven device . The tread bearing gearbox includes three planetary gear sets for realizing eight gears, three free wheel clutches and three brakes, wherein each planetary gear set corresponds to one brake and one free wheel clutch, respectively. In addition, in the tread bearing gearbox, the sun gear of the first planetary gear set can be fixed by a first brake, the sun gear of the second planetary gear set can be fixed by a second brake, and the ring gear of the third planetary gear set Can be fixed by a third brake, wherein the planetary gear carrier of the first planetary gear set and the planetary gear carrier of the second planetary gear set and the planetary gear carrier of the third planetary gear set form the input ends on the planetary gear sets, respectively , And wherein the ring gear of the first planetary gear set, the ring gear of the second planetary gear set, and the sun gear of the third planetary gear set form output ends on the planetary gear sets, respectively.

以此方式實現用於踩踏軸承齒輪箱的齒輪組配置，該齒輪組配置基於齒輪組之間的連接而在效率儘可能高的同時實現特別高的功率密度，從而實現高度的系統整合，而無論各齒輪組以何種軸向順序佈置。In this way, a gear set configuration for a stepped bearing gearbox is realized, which achieves a particularly high power density while being as efficient as possible based on the connection between gear sets, thereby achieving a high degree of system integration, regardless of In what axial order are the gear sets arranged?

此外，為了在各行星齒輪組上實現聯鎖，可藉由相對應的自由輪離合器將太陽輪與內齒圈或者將太陽輪與行星輪架或者將內齒圈與行星輪架連接在一起。In addition, in order to achieve interlocking on each planetary gear set, the sun gear and the ring gear or the sun gear and the planet gear carrier or the ring gear and the planet gear carrier can be connected together by a corresponding free wheel clutch.

因此，本發明所提出之踩踏軸承齒輪箱包括三個軸向依次佈置或耦合的行星齒輪組，其可視擋位而聯鎖或者轉換成高速擋（Schnelle，英：high gear），從而透過三個自由輪及三個易於自外部觸及的制動器來切換出至少八個擋位，其中就該踩踏軸承齒輪箱而言能夠實現極高的效率。Therefore, the stepped bearing gearbox proposed by the present invention includes three planetary gear sets arranged or coupled in sequence in the axial direction, which can be interlocked or converted into a high-speed gear (Schnelle, English: high gear) according to the gear position, thus through three The free wheel and three brakes that are easily accessible from the outside can switch out at least eight gears, of which extremely high efficiency can be achieved with regard to the stepped bearing gearbox.

在本發明所提出之踩踏軸承齒輪箱中，為將彼此耦合之行星齒輪組機械連接在一起，可透過中間軸或類似之物將一個行星齒輪組的輸出端與另一行星齒輪組的輸入端連接在一起。In the tread bearing gearbox proposed by the present invention, in order to mechanically connect the planetary gear sets coupled to each other, the output end of one planetary gear set and the input end of the other planetary gear set can be connected through an intermediate shaft or the like connected.

此外，使用軸體或軸體狀元件來連接所設行星齒輪組的各種齒輪組元件。術語“軸體”不僅指可轉動地安裝的、用於傳遞轉矩的圓柱形機器元件，而是亦可理解為將各齒輪組元件相互連接起來的一般性連接元件。In addition, shaft bodies or shaft body-like elements are used to connect the various gear set elements of the planetary gear set provided. The term "shaft body" refers not only to a rotatably mounted cylindrical machine element for transmitting torque, but can also be understood as a general connection element that connects the gear set elements to each other.

為了除騎行者的人力驅動外亦實現助力電功率，可在本發明之踩踏軸承齒輪箱中如下設置：設有至少一個電機或類似之物。In order to realize the assist electric power in addition to the human driving of the rider, the tread bearing gearbox of the present invention may be provided as follows: at least one motor or the like is provided.

該電機例如可直接地或者藉由一個或數個傳動級、鏈條、齒帶或類似之物而接合在齒輪箱輸入軸、齒輪箱輸出軸及/或中間軸上。為此，亦可視情況而使用諸如自由輪離合器等換擋元件。由此產生以下優點：在電機停止驅動之情況下騎行時，透過騎行而被驅動的電機不產生阻力矩。在例如藉由傳動級進行接合的情況下，必要時可換成慢擋。The motor can be coupled to the gearbox input shaft, gearbox output shaft and/or intermediate shaft directly or by one or several transmission stages, chains, toothed belts or the like, for example. For this, shifting elements such as free wheel clutches can also be used as appropriate. This results in the following advantages: when riding when the motor stops driving, the motor driven by the riding does not generate resistance torque. In the case of engagement by, for example, a gear stage, it can be shifted to a slower gear if necessary.

可選地，該踩踏軸承齒輪箱可在踩踏軸承曲柄軸與齒輪箱輸入端之間實現自由輪。由此產生以下優點：已接合的電機可進一步旋轉，而踩踏軸承曲柄軸的踏板不轉動。Optionally, the tread bearing gearbox can realize a free wheel between the crankshaft of the tread bearing and the input end of the gearbox. This has the advantage that the motor that has been engaged can be rotated further, while the pedal that treads on the crankshaft of the bearing does not rotate.

如前所述，所設置的制動器亦可實施為可切換自由輪或自由輪制動器，其優點在於：換擋時實現各擋位之間更快更簡單的切換。As mentioned above, the brakes provided can also be implemented as switchable freewheels or freewheel brakes, which has the advantage that a faster and simpler switch between the gears is achieved when shifting.

根據本發明之改進方案，該等行星齒輪組可特別是配設有絕對值更低或更高的固定傳動比，例如配設有階梯式行星齒輪。如此，本發明之踩踏軸承齒輪箱實現了更好的空間經濟性。According to the improvement of the present invention, the planetary gear sets may be equipped with a fixed transmission ratio with a lower or higher absolute value, for example, with a stepped planetary gear. In this way, the stepped bearing gearbox of the present invention achieves better space economy.

本發明之另一態樣係提供一種具有前述之踩踏軸承齒輪箱的自行車或電動自行車或類似之物，其中產生前述優點及進一步的優點。Another aspect of the present invention is to provide a bicycle or electric bicycle or the like having the aforementioned stepped bearing gearbox, wherein the aforementioned advantages and further advantages are produced.

圖1及2示出本發明之踩踏軸承齒輪箱的各種實施方案，該踩踏軸承齒輪箱具有各齒輪組的固定傳動比i0，其中圖3所示相關換擋圖提供可能的擋位G1至G8以及相對應的傳動比i及步進或主銷內傾角φ。在換擋圖中示出制動器B1、B2、B3及自由輪離合器F1、F2、F3的單一狀態，其中就制動器B1、B2、B3而言，點表示接合狀態，叉表示分離或移開狀態，而針對自由輪離合器F1、F2、F3，點表示鎖定方向狀態，短線表示超越驅動狀態。自由輪的超越運行或超越驅動狀態意味著自由輪不鎖定。例如當其中一個與自由輪連接的元件快速旋轉而使得自由輪無法鎖定時，自由輪可處於超越驅動。自由輪的鎖定方向狀態意味著自由輪鎖定。FIGS. 1 and 2 show various embodiments of the tread bearing gearbox of the present invention, which has a fixed transmission ratio i0 of each gear set, wherein the relevant shift map shown in FIG. 3 provides possible gears G1 to G8 And the corresponding transmission ratio i and stepping or kingpin inclination angle φ. The shift diagram shows a single state of brakes B1, B2, B3 and free wheel clutches F1, F2, F3, where for brakes B1, B2, B3, the point represents the engaged state, and the fork represents the disengaged or removed state, For the free wheel clutches F1, F2, and F3, the dots indicate the lock direction state, and the short line indicates the overdrive state. The freewheel overrun or overdrive state means that the freewheel is not locked. For example, when one of the elements connected to the free wheel rotates quickly and the free wheel cannot be locked, the free wheel may be in overdrive. The lock direction state of the free wheel means that the free wheel is locked.

無論踩踏軸承齒輪箱具體採用何種實施方案，皆如下設置：該行星結構的踩踏軸承齒輪箱可用於自行車、電動自行車或類似之物。踩踏軸承齒輪箱包括作為驅動裝置的齒輪箱輸入軸1，該驅動裝置在圖1及2中實施為踏板曲柄軸，以及作為從動裝置的齒輪箱輸出軸2，該從動裝置例如可實施為鏈輪或齒帶輪。該踩踏軸承齒輪箱包括三個行星齒輪組RS1、RS2、RS3，其中第一行星齒輪組RS1及第二行星齒輪組RS2以及第三行星齒輪組RS3例如實施為所謂之負行星齒輪組。此外，設有至少三個自由輪離合器F1、F2、F3及三個制動器或自由輪制動器B1、B2、B3，其大體上作為用於實現至少8個擋位G1、G2、G3、G4、G5、G6、G7、G8的換擋元件。該踩踏軸承齒輪箱的行星齒輪組RS1、RS2、RS3相對踏板曲柄軸而言較佳係同軸佈置，從而在結構空間方面具備優勢。Regardless of the specific implementation of the stepped bearing gearbox, it is set as follows: the planetary structured stepped bearing gearbox can be used for bicycles, electric bicycles, or the like. The stepped bearing gearbox includes a gearbox input shaft 1 as a driving device, which is implemented as a pedal crankshaft in FIGS. 1 and 2 and a gearbox output shaft 2 as a driven device, which can be implemented as, for example, Sprocket or toothed belt wheel. The tread bearing gearbox includes three planetary gear sets RS1, RS2, and RS3, wherein the first planetary gear set RS1, the second planetary gear set RS2, and the third planetary gear set RS3 are, for example, implemented as so-called negative planetary gear sets. In addition, there are at least three free wheel clutches F1, F2, F3 and three brakes or free wheel brakes B1, B2, B3, which are generally used to achieve at least 8 gears G1, G2, G3, G4, G5 , G6, G7, G8 shift elements. The planetary gear sets RS1, RS2, and RS3 of the stepped bearing gearbox are preferably arranged coaxially with respect to the pedal crankshaft, thereby having advantages in terms of structural space.

在該踩踏軸承齒輪箱的所有實施方案中，每個行星齒輪組RS1、RS2、RS3分別對應於一個制動器B1、B2、B3及一個自由輪離合器F1、F2、F3，其中第一行星齒輪組RS1的太陽輪4可由第一制動器B1固定在殼體3或殼體側上，第二行星齒輪組RS2的太陽輪7可由第二制動器B2固定，以及，第三行星齒輪組RS3的內齒圈12可由第三制動器B3固定。第一行星齒輪組RS1的行星輪架5及第二行星齒輪組RS2的行星輪架8以及第三行星齒輪組RS3的行星輪架11分別形成行星齒輪組RS1、RS2、RS3上的輸入端，其中第一行星齒輪組RS1的內齒圈6及第二行星齒輪組RS2的內齒圈9以及第三行星齒輪組RS3的太陽輪10分別形成行星齒輪組RS1、RS2、RS3上的輸出端。In all embodiments of the tread bearing gearbox, each planetary gear set RS1, RS2, RS3 corresponds to a brake B1, B2, B3 and a free wheel clutch F1, F2, F3, of which the first planetary gear set RS1 The sun gear 4 can be fixed on the housing 3 or the housing side by the first brake B1, the sun gear 7 of the second planetary gear set RS2 can be fixed by the second brake B2, and the ring gear 12 of the third planetary gear set RS3 It can be fixed by the third brake B3. The planetary gear carrier 5 of the first planetary gear set RS1, the planetary gear carrier 8 of the second planetary gear set RS2, and the planetary gear carrier 11 of the third planetary gear set RS3 respectively form input ends on the planetary gear sets RS1, RS2, and RS3, The ring gear 6 of the first planetary gear set RS1, the ring gear 9 of the second planetary gear set RS2, and the sun gear 10 of the third planetary gear set RS3 form the output ends of the planetary gear sets RS1, RS2, and RS3, respectively.

為透過第一自由輪離合器F1來聯鎖第一行星齒輪組RS1，該第一行星齒輪組RS1的太陽輪4可與內齒圈6連接，或者太陽輪4可與行星輪架5連接，或者內齒圈6可與行星輪架5連接。此外，為透過第二自由輪離合器F2來聯鎖第二行星齒輪組RS2，該第二行星齒輪組RS2的太陽輪7可與內齒圈9連接，或者太陽輪7可與行星輪架8連接，或者內齒圈9可與行星輪架8連接。最後，為透過第三自由輪離合器F3來聯鎖第三行星齒輪組RS3，該第三行星齒輪組RS3的太陽輪10可與內齒圈12連接，或者太陽輪10可與行星輪架11連接，或者內齒圈12可與行星輪架11連接。To interlock the first planetary gear set RS1 through the first free wheel clutch F1, the sun gear 4 of the first planetary gear set RS1 may be connected to the ring gear 6, or the sun gear 4 may be connected to the planetary gear carrier 5, or The ring gear 6 can be connected to the planetary gear carrier 5. In addition, in order to interlock the second planetary gear set RS2 through the second free wheel clutch F2, the sun gear 7 of the second planetary gear set RS2 may be connected to the ring gear 9 or the sun gear 7 may be connected to the planetary gear carrier 8 Or, the ring gear 9 may be connected to the planetary gear carrier 8. Finally, in order to interlock the third planetary gear set RS3 through the third free wheel clutch F3, the sun gear 10 of the third planetary gear set RS3 may be connected to the ring gear 12, or the sun gear 10 may be connected to the planetary gear carrier 11 Or, the ring gear 12 may be connected to the planetary gear carrier 11.

圖1示出踩踏軸承齒輪箱的第一實施方案，其中按軸向順序設有第三行星齒輪組RS3及第二行星齒輪組RS2以及第一行星齒輪組RS1。圖1中進一步提供第三行星齒輪組RS3的固定傳動比i03 -1.62、第二行星齒輪組RS2的固定傳動比i02 -1.62、及第一行星齒輪組RS1的固定傳動比i01 -3.66。FIG. 1 shows a first embodiment of a stepped bearing gearbox in which a third planetary gear set RS3 and a second planetary gear set RS2 and a first planetary gear set RS1 are provided in axial order. FIG 1 is further provided a third planetary gearset RS3 fixed gear ratio i 03 -1.62, stationary gear of the second planetary gearset RS2 fixed transmission ratio i 02 -1.62, and the first planetary gear set RS1 than i 01 -3.66 .

具體言之，齒輪箱輸入軸1與作為第三行星齒輪組RS3之輸入端的行星輪架11連接。太陽輪10作為第三行星齒輪組RS3之輸出端透過中間軸ZW與作為第一行星齒輪組RS1之輸入端的行星輪架5連接，其中內齒圈6作為第一行星齒輪組RS1之輸出端與作為第二行星齒輪組RS2之輸入端的行星輪架8連接。內齒圈9作為第二行星齒輪組RS2之輸出端與齒輪箱輸出軸2連接，其中第一行星齒輪組RS1的太陽輪4可透過第一自由輪離合器F1與第一行星齒輪組RS1的內齒圈6連接，其中第二行星齒輪組RS2的內齒圈9可透過第二自由輪離合器F2與第二行星齒輪組RS2的行星輪架8連接，且其中第三行星齒輪組RS3的行星輪架11可透過第三自由輪離合器F3與第三行星齒輪組RS3的內齒圈12連接。Specifically, the gearbox input shaft 1 is connected to the planetary carrier 11 that is the input end of the third planetary gear set RS3. The sun gear 10 as the output end of the third planetary gear set RS3 is connected to the planetary gear carrier 5 as the input end of the first planetary gear set RS1 through the intermediate shaft ZW, and the ring gear 6 serves as the output end of the first planetary gear set RS1 and The planetary gear carrier 8 as the input end of the second planetary gear set RS2 is connected. The ring gear 9 is connected to the gearbox output shaft 2 as the output end of the second planetary gear set RS2, wherein the sun gear 4 of the first planetary gear set RS1 can pass through the first free wheel clutch F1 and the inner of the first planetary gear set RS1 The ring gear 6 is connected, wherein the ring gear 9 of the second planetary gear set RS2 can be connected to the planetary carrier 8 of the second planetary gear set RS2 through the second free wheel clutch F2, and the planetary gear of the third planetary gear set RS3 The carrier 11 can be connected to the ring gear 12 of the third planetary gear set RS3 through the third free wheel clutch F3.

圖2示出踩踏軸承齒輪箱的第二實施方案，其中按軸向順序設有第二行星齒輪組RS2及第一行星齒輪組RS1以及第三行星齒輪組RS3。圖2中進一步提供第二行星齒輪組RS2的固定傳動比i02 -1.62、第一行星齒輪組RS1的固定傳動比i01 -3.66、及第三行星齒輪組RS3的固定傳動比i03 -1.62。FIG. 2 shows a second embodiment of a stepped bearing gearbox in which the second planetary gear set RS2 and the first planetary gear set RS1 and the third planetary gear set RS3 are provided in axial order. FIG. 2 further provides a fixed transmission ratio i 02 -1.62 of the second planetary gear set RS2, a fixed transmission ratio i 01 -3.66 of the first planetary gear set RS1, and a fixed transmission ratio i 03 -1.62 of the third planetary gear set RS3 .

具體言之，齒輪箱輸入軸1與作為第一行星齒輪組RS1之輸入端的行星輪架5連接，內齒圈6作為第一行星齒輪組RS1之輸出端與作為第二行星齒輪組RS2之輸入端的行星輪架8連接，內齒圈9作為第二行星齒輪組RS2之輸出端透過中間軸ZW與作為第三行星齒輪組RS3之輸入端的行星輪架11連接，太陽輪10作為第三行星齒輪組RS3之輸出端與齒輪箱輸出軸2連接，第一行星齒輪組RS1的太陽輪4可透過第一自由輪離合器F1與第一行星齒輪組RS1的內齒圈6連接，第二行星齒輪組RS2的太陽輪7可透過第二自由輪離合器F2與第二行星齒輪組RS2的內齒圈9連接，以及，第三行星齒輪組RS3的太陽輪10可透過第三自由輪離合器F3與第三行星齒輪組RS3的行星輪架11連接。此外，可作為馬達或發電機工作的電機EM與中間軸ZW連接，以便為騎行者提供助力功率。如此，該第二實施方案示例性地實現了一種混合式踩踏軸承齒輪箱，其中電機EM較佳例如可以與齒輪箱輸入軸1軸向平行的方式佈置在自行車或電動自行車之下管中或下管上。透過將電機EM接合至中間軸ZW，電機EM便能在傳動比為i=1的擋位G1至G4中工作，以及在傳動比為i=0.38的擋位G5至G8中工作。在電機EM接合至齒輪箱輸入軸1之情況下，電機EM可以相應的擋位傳動比工作，如此，電機EM便能總是在效率優化的範圍內工作。在電機EM接合至齒輪箱輸出軸2之情況下，電機EM以鏈傳動比工作，其中，若在換擋期間僅由電機EM施加負荷且齒輪箱處於無負荷狀態，則藉此可實現動力換擋。Specifically, the gearbox input shaft 1 is connected to the planetary gear carrier 5 as the input end of the first planetary gear set RS1, and the ring gear 6 serves as the output end of the first planetary gear set RS1 and serves as the input of the second planetary gear set RS2 The planetary gear carrier 8 at the end is connected, and the ring gear 9 as the output end of the second planetary gear set RS2 is connected to the planetary gear carrier 11 as the input end of the third planetary gear set RS3 through the intermediate shaft ZW, and the sun gear 10 as the third planetary gear The output end of the set RS3 is connected to the gearbox output shaft 2. The sun gear 4 of the first planetary gear set RS1 can be connected to the ring gear 6 of the first planetary gear set RS1 through the first free wheel clutch F1, and the second planetary gear set The sun gear 7 of RS2 can be connected to the ring gear 9 of the second planetary gear set RS2 through the second free wheel clutch F2, and the sun gear 10 of the third planetary gear set RS3 can be connected to the third through the third free wheel clutch F3 The planetary gear carrier 11 of the planetary gear set RS3 is connected. In addition, the motor EM, which can work as a motor or a generator, is connected to the intermediate shaft ZW in order to provide a booster power for the rider. In this way, the second embodiment exemplarily realizes a hybrid stepping bearing gearbox, wherein the motor EM is preferably arranged in the lower tube of the bicycle or electric bicycle, for example, in an axial parallel manner with the gearbox input shaft 1 On the tube. By engaging the motor EM to the intermediate shaft ZW, the motor EM can be operated in the gears G1 to G4 with the transmission ratio i=1, and in the gears G5 to G8 with the transmission ratio i=0.38. When the motor EM is coupled to the gearbox input shaft 1, the motor EM can work with the corresponding gear ratio, so that the motor EM can always work within the range of efficiency optimization. When the motor EM is coupled to the gearbox output shaft 2, the motor EM operates at a chain transmission ratio, wherein if only the motor EM applies a load during the gear shift and the gearbox is in an unloaded state, power shifting can be achieved thereby block.

圖3為圖1所示第一實施方案及圖2所示第二實施方案的換擋圖。由該換擋圖可知：為了切換出第一擋位G1，第一、第二及第三制動器B1、B2、B3分離或移開，其中第一、第二及第三自由輪離合器F1、F2、F3處於鎖定方向狀態。為了切換出第二擋位G2，第一制動器B1接合且第二及第三制動器B2、B3分離或移開，其中第一自由輪離合器F1處於超越驅動狀態且第二及第三自由輪離合器F2、F3處於鎖定方向狀態。為了切換出第三擋位G3，第二制動器B2接合且第一及第三制動器B1、B3分離或移開，其中第二自由輪離合器F2處於超越驅動狀態且第一及第三自由輪離合器F1、F3處於鎖定方向狀態。為了切換出第四擋位G4，第一及第二制動器B1、B2接合且第三制動器B3分離或移開，其中第一及第二自由輪離合器F1、F2處於超越驅動狀態且第三自由輪離合器F3處於鎖定方向狀態。為了切換出第五擋位G5，第三制動器B3接合且第一及第二制動器B1、B2分離或移開，其中第一及第二自由輪離合器F1、F2處於鎖定方向狀態且第三自由輪離合器F3處於超越驅動狀態。為了切換出第六擋位G6，第一及第三制動器B1、B3接合且第二制動器B2分離或移開，其中第一及第三自由輪離合器F1、F3處於超越驅動狀態且第二自由輪離合器F2處於鎖定方向狀態。為了切換出第七擋位G7，第一制動器B1分離或移開且第二及第三制動器B2、B3接合，其中第一自由輪離合器F1處於鎖定方向狀態且第二及第三自由輪離合器F2、F3處於超越驅動狀態。為了切換出第八擋位G8，第一、第二及第三制動器B1、B2、B3接合，其中第一、第二及第三自由輪離合器F1、F2、F3處於超越驅動狀態。FIG. 3 is a shift diagram of the first embodiment shown in FIG. 1 and the second embodiment shown in FIG. 2. It can be seen from the shift map: in order to switch out the first gear G1, the first, second and third brakes B1, B2, B3 are disengaged or removed, in which the first, second and third free wheel clutches F1, F2 , F3 is in the locked direction. In order to switch out of the second gear G2, the first brake B1 is engaged and the second and third brakes B2, B3 are disengaged or removed, wherein the first free wheel clutch F1 is in an overdrive state and the second and third free wheel clutch F2 , F3 is in the locked direction. To switch out of the third gear G3, the second brake B2 is engaged and the first and third brakes B1, B3 are disengaged or removed, wherein the second free wheel clutch F2 is in an overdrive state and the first and third free wheel clutch F1 , F3 is in the locked direction. In order to switch out of the fourth gear G4, the first and second brakes B1, B2 are engaged and the third brake B3 is disengaged or removed, wherein the first and second free wheel clutches F1, F2 are in overdrive state and the third free wheel The clutch F3 is in the locked direction. In order to switch out of the fifth gear G5, the third brake B3 is engaged and the first and second brakes B1, B2 are disengaged or removed, wherein the first and second free wheel clutches F1, F2 are in the locked direction and the third free wheel Clutch F3 is in overdrive state. In order to switch out of the sixth gear G6, the first and third brakes B1, B3 are engaged and the second brake B2 is disengaged or removed, wherein the first and third free wheel clutches F1, F3 are in overdrive state and the second free wheel The clutch F2 is in the locked direction. In order to switch out of the seventh gear G7, the first brake B1 is disengaged or removed and the second and third brakes B2, B3 are engaged, wherein the first free wheel clutch F1 is in the locked direction and the second and third free wheel clutch F2 , F3 is in overdrive state. In order to switch out of the eighth gear G8, the first, second and third brakes B1, B2 and B3 are engaged, wherein the first, second and third freewheel clutches F1, F2 and F3 are in the overdrive state.

1‧‧‧齒輪箱輸入軸或踏板曲柄軸 2‧‧‧齒輪箱輸出軸或者自行車或電動自行車的從動裝置 3‧‧‧殼體 4‧‧‧第一行星齒輪組的太陽輪 5‧‧‧第一行星齒輪組的行星輪架或支架 6‧‧‧第一行星齒輪組的內齒圈 7‧‧‧第二行星齒輪組的太陽輪 8‧‧‧第二行星齒輪組的行星輪架 9‧‧‧第二行星齒輪組的內齒圈 10‧‧‧第三行星齒輪組的太陽輪 11‧‧‧第三行星齒輪組的行星輪架 12‧‧‧第三行星齒輪組的內齒圈 B1‧‧‧第一制動器 B2‧‧‧第二制動器 B3‧‧‧第三制動器 EM‧‧‧電機 F1‧‧‧第一自由輪離合器 F2‧‧‧第二自由輪離合器 F3‧‧‧第三自由輪離合器 G1‧‧‧第一擋位 G2‧‧‧第二擋位 G3‧‧‧第三擋位 G4‧‧‧第四擋位 G5‧‧‧第五擋位 G6‧‧‧第六擋位 G7‧‧‧第七擋位 G8‧‧‧第八擋位 i‧‧‧傳動比 i01‧‧‧第一行星齒輪組的固定傳動比 i02‧‧‧第二行星齒輪組的固定傳動比 i03‧‧‧第三行星齒輪組的固定傳動比 RS1‧‧‧第一行星齒輪組 RS2‧‧‧第二行星齒輪組 RS3‧‧‧第三行星齒輪組 ZW‧‧‧中間軸 Φ‧‧‧步進 Φges‧‧‧總步進1‧‧‧ gearbox input shaft or pedal crankshaft 2‧‧‧ gearbox output shaft or bicycle or electric bicycle driven device 3‧‧‧case 4‧‧‧sun gear of the first planetary gear set 5‧‧ ‧Planetary carrier or bracket of the first planetary gear set 6‧‧‧Inner ring gear of the first planetary gear set 7‧‧‧Sun gear of the second planetary gear set 8‧‧‧Planetary carrier of the second planetary gear set 9‧‧‧Inner ring gear of the second planetary gear set 10‧‧‧Sun gear of the third planetary gear set 11‧‧‧Planet carrier of the third planetary gear set 12‧‧‧‧Internal teeth of the third planetary gear set Circle B1‧‧‧ First brake B2‧‧‧ Second brake B3‧‧‧ Third brake EM‧‧‧Motor F1‧‧‧ First free wheel clutch F2‧‧‧ Second free wheel clutch F3‧‧‧ Three free wheel clutch G1‧‧‧ first gear G2‧‧‧ second gear G3‧‧‧ third gear G4‧‧‧ fourth gear G5‧‧‧ fifth gear G6‧‧‧ sixth Gear G7‧‧‧ seventh gear G8‧‧‧ eighth gear i‧‧‧ transmission ratio i 01 ‧‧‧ fixed transmission ratio of the first planetary gear set i 02 ‧‧‧fixation of the second planetary gear set Transmission ratio i 03 ‧‧‧The fixed transmission ratio of the third planetary gear set RS1‧‧‧The first planetary gear set RS2‧‧‧The second planetary gear set RS3‧‧‧The third planetary gear set ZW‧‧‧Intermediate shaft Φ ‧‧‧Step Φ ges ‧‧‧Total step

下面結合附圖對本發明進一步進行說明。其中： 圖1為具有三個軸向依次佈置之行星齒輪組的本發明之踩踏軸承齒輪箱的第一實施方案的示意圖； 圖2為具有該等行星齒輪組之軸向有所變化之順序的本發明之踩踏軸承齒輪箱的第二實施方案的示意圖； 圖3為該踩踏軸承齒輪箱的第一及第二實施方案的換擋圖。The present invention will be further described below with reference to the drawings. among them: FIG. 1 is a schematic diagram of a first embodiment of a tread bearing gearbox of the present invention having three planetary gear sets arranged sequentially in the axial direction; 2 is a schematic diagram of a second embodiment of the tread bearing gearbox of the present invention having a sequence in which the axial directions of the planetary gear sets are changed; Fig. 3 is a shift diagram of the first and second embodiments of the stepped bearing gearbox.

1‧‧‧齒輪箱輸入軸或踏板曲柄軸 1‧‧‧ gearbox input shaft or pedal crank shaft

2‧‧‧齒輪箱輸出軸或者自行車或電動自行車的從動裝置 2‧‧‧ Gearbox output shaft or driven device of bicycle or electric bicycle

3‧‧‧殼體 3‧‧‧Housing

4‧‧‧第一行星齒輪組的太陽輪 4‧‧‧The sun gear of the first planetary gear set

5‧‧‧第一行星齒輪組的行星輪架或支架 5‧‧‧Planetary carrier or bracket of the first planetary gear set

6‧‧‧第一行星齒輪組的內齒圈 6‧‧‧Inner ring gear of the first planetary gear set

7‧‧‧第二行星齒輪組的太陽輪 7‧‧‧The sun gear of the second planetary gear set

8‧‧‧第二行星齒輪組的行星輪架 8‧‧‧Planetary carrier of the second planetary gear set

9‧‧‧第二行星齒輪組的內齒圈 9‧‧‧Inner ring gear of the second planetary gear set

10‧‧‧第三行星齒輪組的太陽輪 10‧‧‧The sun gear of the third planetary gear set

11‧‧‧第三行星齒輪組的行星輪架 11‧‧‧Planetary carrier of the third planetary gear set

12‧‧‧第三行星齒輪組的內齒圈 12‧‧‧Inner ring gear of the third planetary gear set

B1‧‧‧第一制動器 B1‧‧‧ First brake

B2‧‧‧第二制動器 B2‧‧‧Second brake

B3‧‧‧第三制動器 B3‧‧‧third brake

F1‧‧‧第一自由輪離合器 F1‧‧‧The first free wheel clutch

F2‧‧‧第二自由輪離合器 F2‧‧‧Second free wheel clutch

F3‧‧‧第三自由輪離合器 F3‧‧‧The third free wheel clutch

i01‧‧‧第一行星齒輪組的固定傳動比 i 01 ‧‧‧ Fixed transmission ratio of the first planetary gear set

i02‧‧‧第二行星齒輪組的固定傳動比 i 02 ‧‧‧ Fixed transmission ratio of the second planetary gear set

i03‧‧‧第三行星齒輪組的固定傳動比 i 03 ‧‧‧ Fixed transmission ratio of the third planetary gear set

RS1‧‧‧第一行星齒輪組 RS1‧‧‧The first planetary gear set

RS2‧‧‧第二行星齒輪組 RS2‧‧‧Second planetary gear set

RS3‧‧‧第三行星齒輪組 RS3‧‧‧third planetary gear set

ZW‧‧‧中間軸 ZW‧‧‧ intermediate shaft

Claims (10)

一種用於自行車或電動自行車之行星結構的踩踏軸承齒輪箱，具有作為驅動裝置的齒輪箱輸入軸（1）及作為從動裝置的齒輪箱輸出軸（2），具有用於實現八個擋位（G1，G2，G3，G4，G5，G6，G7，G8）的三個行星齒輪組（RS1，RS2，RS3）、三個自由輪離合器（F1，F2，F3）及三個制動器（B1，B2，B3），其中每個行星齒輪組（RS1，RS2，RS3）分別對應於一個制動器（B1，B2，B3）及一個自由輪離合器（F1，F2，F3），其中該第一行星齒輪組（RS1）的太陽輪（4）可由該第一制動器（B1）固定，該第二行星齒輪組（RS2）的太陽輪（7）可由該第二制動器（B2）固定，以及該第三行星齒輪組（RS3）的內齒圈（12）可由該第三制動器（B3）固定，其中該第一行星齒輪組（RS1）的行星輪架（5）及該第二行星齒輪組（RS2）的行星輪架（8）以及該第三行星齒輪組（RS3）的行星輪架（11）分別形成該等行星齒輪組（RS1，RS2，RS3）上的輸入端，且其中該第一行星齒輪組（RS1）的內齒圈（6）及該第二行星齒輪組（RS2）的內齒圈（9）以及該第三行星齒輪組（RS3）的太陽輪（10）分別形成該等行星齒輪組（RS1，RS2，RS3）上的輸出端。A planetary stepping bearing gearbox for bicycles or electric bicycles has a gearbox input shaft (1) as a driving device and a gearbox output shaft (2) as a driven device, and has eight gears for achieving (G1, G2, G3, G4, G5, G6, G7, G8) three planetary gear sets (RS1, RS2, RS3), three free wheel clutches (F1, F2, F3) and three brakes (B1, B2, B3), where each planetary gear set (RS1, RS2, RS3) corresponds to a brake (B1, B2, B3) and a free wheel clutch (F1, F2, F3), wherein the first planetary gear set The sun gear (4) of (RS1) can be fixed by the first brake (B1), the sun gear (7) of the second planetary gear set (RS2) can be fixed by the second brake (B2), and the third planetary gear The ring gear (12) of the set (RS3) can be fixed by the third brake (B3), wherein the planet carrier (5) of the first planetary gear set (RS1) and the planets of the second planetary gear set (RS2) The gear carrier (8) and the planet gear carrier (11) of the third planetary gear set (RS3) respectively form the input ends on the planetary gear sets (RS1, RS2, RS3), and wherein the first planetary gear set ( The ring gear (6) of RS1), the ring gear (9) of the second planetary gear set (RS2) and the sun gear (10) of the third planetary gear set (RS3) form the planetary gear sets ( RS1, RS2, RS3) on the output. 如請求項1所述之踩踏軸承齒輪箱，其中，為透過該第一自由輪離合器（F1）來聯鎖該第一行星齒輪組（RS1），該第一行星齒輪組（RS1）的該太陽輪（4）可與該內齒圈（6）連接，或者該太陽輪（4）可與該行星輪架（5）連接，或者該內齒圈（6）可與該行星輪架（5）連接。The stepped bearing gearbox according to claim 1, wherein in order to interlock the first planetary gear set (RS1) through the first free wheel clutch (F1), the sun of the first planetary gear set (RS1) The gear (4) can be connected to the inner ring gear (6), or the sun gear (4) can be connected to the planetary gear carrier (5), or the inner ring gear (6) can be connected to the planetary gear carrier (5) connection. 如請求項1或2所述之踩踏軸承齒輪箱，其中，為透過該第二自由輪離合器（F2）來聯鎖該第二行星齒輪組（RS2），該第二行星齒輪組（RS2）的該太陽輪（7）可與該內齒圈（9）連接，或者該太陽輪（7）可與該行星輪架（8）連接，或者該內齒圈（9）可與該行星輪架（8）連接。The stepped bearing gearbox according to claim 1 or 2, wherein, for interlocking the second planetary gear set (RS2) through the second free wheel clutch (F2), the second planetary gear set (RS2) The sun gear (7) may be connected to the inner ring gear (9), or the sun gear (7) may be connected to the planetary gear carrier (8), or the inner ring gear (9) may be connected to the planetary gear carrier ( 8) Connect. 如請求項1或2項所述之踩踏軸承齒輪箱，其中，為透過該第三自由輪離合器（F3）來聯鎖該第三行星齒輪組（RS3），該第三行星齒輪組（RS3）的該太陽輪（10）可與該內齒圈（12）連接，或者該太陽輪（10）可與該行星輪架（11）連接，或者該內齒圈（12）可與該行星輪架（11）連接。The stepped bearing gearbox according to claim 1 or 2, wherein, to interlock the third planetary gear set (RS3) through the third free wheel clutch (F3), the third planetary gear set (RS3) The sun gear (10) can be connected to the inner ring gear (12), or the sun gear (10) can be connected to the planetary gear carrier (11), or the inner ring gear (12) can be connected to the planetary gear carrier (11) Connect. 如請求項1或2項所述之踩踏軸承齒輪箱，其中，設置自由輪制動器作為制動器（B1、B2、B3、B4）。The stepped bearing gearbox according to claim 1 or 2, wherein a free wheel brake is provided as a brake (B1, B2, B3, B4). 如請求項1或2項所述之踩踏軸承齒輪箱，其中，該齒輪箱輸入軸（1）與作為該第三行星齒輪組（RS3）之輸入端的行星輪架（11）連接，該太陽輪（10）作為該第三行星齒輪組（RS3）之輸出端與作為該第一行星齒輪組（RS1）之輸入端的行星輪架（5）連接，該內齒圈（6）作為該第一行星齒輪組（RS1）之輸出端與作為該第二行星齒輪組（RS2）之輸入端的行星輪架（8）連接，該內齒圈（9）作為該第二行星齒輪組（RS2）之輸出端與該齒輪箱輸出軸（2）連接，該第一行星齒輪組（RS1）的太陽輪（4）可透過該第一自由輪離合器（F1）與該第一行星齒輪組（RS1）的內齒圈（6）連接，該第二行星齒輪組（RS2）的內齒圈（9）可透過該第二自由輪離合器（F2）與該第二行星齒輪組（RS2）的行星輪架（8）連接，以及，該第三行星齒輪組（RS3）的行星輪架（11）可透過該第三自由輪離合器（F3）與該第三行星齒輪組（RS3）的內齒圈（12）連接。圖1The tread bearing gearbox according to claim 1 or 2, wherein the gearbox input shaft (1) is connected to the planetary gear carrier (11) which is the input end of the third planetary gear set (RS3), the sun gear (10) The output end of the third planetary gear set (RS3) is connected to the planetary gear carrier (5) as the input end of the first planetary gear set (RS1), and the ring gear (6) serves as the first planet The output end of the gear set (RS1) is connected to the planetary gear carrier (8) as the input end of the second planetary gear set (RS2), and the ring gear (9) serves as the output end of the second planetary gear set (RS2) Connected to the gearbox output shaft (2), the sun gear (4) of the first planetary gear set (RS1) can pass through the first free wheel clutch (F1) and the internal teeth of the first planetary gear set (RS1) The ring gear (6) is connected, and the ring gear (9) of the second planetary gear set (RS2) can pass through the second free wheel clutch (F2) and the planetary gear carrier (8) of the second planetary gear set (RS2) And the planetary carrier (11) of the third planetary gear set (RS3) can be connected to the ring gear (12) of the third planetary gear set (RS3) through the third free wheel clutch (F3). figure 1 如請求項1或2項所述之踩踏軸承齒輪箱，其中，該齒輪箱輸入軸（1）與作為該第一行星齒輪組（RS1）之輸入端的行星輪架（5）連接，該內齒圈（6）作為該第一行星齒輪組（RS1）之輸出端與作為該第二行星齒輪組（RS2）之輸入端的行星輪架（8）連接，該內齒圈（9）作為該第二行星齒輪組（RS2）之輸出端與作為該第三行星齒輪組（RS3）之輸入端的行星輪架（11）連接，該太陽輪（10）作為該第三行星齒輪組（RS3）之輸出端與該齒輪箱輸出軸（2）連接，該第一行星齒輪組（RS1）的太陽輪（4）可透過該第一自由輪離合器（F1）與該第一行星齒輪組（RS1）的內齒圈（6）連接，該第二行星齒輪組（RS2）的太陽輪（7）可透過該第二自由輪離合器（F2）與該第二行星齒輪組（RS2）的內齒圈（9）連接，以及，該第三行星齒輪組（RS3）的太陽輪（10）可透過該第三自由輪離合器（F3）與該第三行星齒輪組（RS3）的行星輪架（11）連接。圖2The stepped bearing gearbox according to claim 1 or 2, wherein the gearbox input shaft (1) is connected to the planetary gear carrier (5) as the input end of the first planetary gear set (RS1), and the internal teeth The ring (6) as the output end of the first planetary gear set (RS1) is connected to the planetary carrier (8) as the input end of the second planetary gear set (RS2), and the ring gear (9) as the second The output end of the planetary gear set (RS2) is connected to the planetary gear carrier (11) as the input end of the third planetary gear set (RS3), and the sun gear (10) serves as the output end of the third planetary gear set (RS3) Connected to the gearbox output shaft (2), the sun gear (4) of the first planetary gear set (RS1) can pass through the first free wheel clutch (F1) and the internal teeth of the first planetary gear set (RS1) The ring gear (6) is connected, and the sun gear (7) of the second planetary gear set (RS2) can be connected to the ring gear (9) of the second planetary gear set (RS2) through the second free wheel clutch (F2) And, the sun gear (10) of the third planetary gear set (RS3) can be connected to the planetary gear carrier (11) of the third planetary gear set (RS3) through the third free wheel clutch (F3). figure 2 如前述請求項第1或2項所述之踩踏軸承齒輪箱，其中，為了切換出第一擋位（G1），該第一、第二及第三制動器（B1，B2，B3）分離，其中該第一、第二及第三自由輪離合器（F1，F2，F3）處於鎖定方向狀態，或者，為了切換出第二擋位（G2），該第一制動器（B1）接合且該第二及第三制動器（B2，B3）分離，其中該第一自由輪離合器（F1）處於超越驅動狀態且該第二及第三自由輪離合器（F2，F3）處於鎖定方向狀態，或者，為了切換出第三擋位（G3），該第二制動器（B2）接合且該第一及第三制動器（B1，B3）分離，其中該第二自由輪離合器（F2）處於超越驅動狀態且該第一及第三自由輪離合器（F1，F3）處於鎖定方向狀態，或者，為了切換出第四擋位（G4），該第一及第二制動器（B1，B2）接合且該第三制動器（B3）分離，其中該第一及第二自由輪離合器（F1，F2）處於超越驅動狀態且該第三自由輪離合器（F3）處於鎖定方向狀態，或者，為了切換出第五擋位（G5），該第三制動器（B3）接合且該第一及第二制動器（B1，B2）分離，其中該第一及第二自由輪離合器（F1，F2）處於鎖定方向狀態且該第三自由輪離合器（F3）處於超越驅動狀態，或者，為了切換出第六擋位（G6），該第一及第三制動器（B1，B3）接合且該第二制動器（B2）分離，其中該第一及第三自由輪離合器（F1，F3）處於超越驅動狀態且該第二自由輪離合器（F2）處於鎖定方向狀態，或者，為了切換出第七擋位（G7），該第一制動器（B1）分離且該第二及第三制動器（B2，B3）接合，其中該第一自由輪離合器（F1）處於鎖定方向狀態且該第二及第三自由輪離合器（F2，F3）處於超越驅動狀態，或者，為了切換出第八擋位（G8），該第一、第二及第三制動器（B1，B2，B3）接合，其中該第一、第二及第三自由輪離合器（F1，F2，F3）處於超越驅動狀態。The stepped bearing gearbox as described in item 1 or 2 of the preceding claim, wherein in order to switch out the first gear (G1), the first, second and third brakes (B1, B2, B3) are disengaged, wherein The first, second and third free wheel clutches (F1, F2, F3) are in the locked direction, or, in order to switch out of the second gear (G2), the first brake (B1) is engaged and the second and The third brake (B2, B3) is disengaged, wherein the first free wheel clutch (F1) is in the overdrive state and the second and third free wheel clutches (F2, F3) are in the locking direction, or, in order to switch out In the third gear (G3), the second brake (B2) is engaged and the first and third brakes (B1, B3) are disengaged, wherein the second free wheel clutch (F2) is in an overdrive state and the first and second brakes The three free wheel clutches (F1, F3) are in the locked direction, or to switch out of the fourth gear (G4), the first and second brakes (B1, B2) are engaged and the third brake (B3) is released, Wherein the first and second free wheel clutches (F1, F2) are in the overdrive state and the third free wheel clutch (F3) is in the locked direction state, or, in order to switch out the fifth gear (G5), the third The brake (B3) is engaged and the first and second brakes (B1, B2) are disengaged, wherein the first and second free wheel clutches (F1, F2) are in the locked direction state and the third free wheel clutch (F3) is in Overdrive state, or, to switch out of the sixth gear (G6), the first and third brakes (B1, B3) are engaged and the second brake (B2) is disengaged, wherein the first and third free wheel clutches (F1, F3) is in the overdrive state and the second free wheel clutch (F2) is in the locked direction, or, in order to switch out the seventh gear (G7), the first brake (B1) is released and the second and The third brake (B2, B3) is engaged, wherein the first free wheel clutch (F1) is in the locked direction and the second and third free wheel clutches (F2, F3) are in the overdrive state, or, in order to switch out Eighth gear (G8), the first, second and third brakes (B1, B2, B3) are engaged, wherein the first, second and third free wheel clutches (F1, F2, F3) are in overdrive state . 如請求項1或2項所述之踩踏軸承齒輪箱，其中，設有至少一個電機（EM）。The tread bearing gearbox according to claim 1 or 2, wherein at least one electric motor (EM) is provided. 一種具有如前述請求項1至9項中任一項所述之踩踏軸承齒輪箱的自行車或電動自行車。A bicycle or electric bicycle having a tread bearing gearbox as described in any one of the foregoing claims 1 to 9.
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