[發明欲解決的課題] [0004] 本發明的目的要提供一種自行車用變速器及具備該變速器的自行車用輔助系統，能適當地變更變速比。 [用以解決課題的手段] [0005] 本發明的第1型態的自行車用變速器，是用來將輸入體的旋轉變速而傳遞到輸出體；上述自行車用變速器具備有：包含將來自上述輸入體的旋轉變速而輸出到上述輸出體的複數的變速機構且將來自上述輸入體的旋轉以3階段以上的變速比傳遞到上述輸出體的傳遞機構、及用來設定上述傳遞機構的變速路線的設定機構；上述複數的變速機構，至少包含第1變速機構，上述第1變速機構包含第1行星機構及第2行星機構；上述傳遞機構，至少形成：至少經由上述第1變速機構的變速而以上述3階段以上的變速比之中的第1變速比及第2變速比的其中一方將來自上述輸入體的旋轉傳遞到上述輸出體的第1變速路線、及經由與在上述第1變速路線所經由的上述變速機構不同的上述變速機構的變速，以較上述第1變速比及上述第2變速比更大的變速比將來自上述輸入體的旋轉傳遞到上述輸出體的第2變速路線；上述第1變速路線包含：經由上述第1行星機構的變速而未經由上述第2行星機構的變速而將來自上述輸入體的旋轉以上述第1變速比傳遞到上述輸出體的第1行星變速路線、及未經由上述第1行星機構的變速而經由上述第2行星機構的變速而將來自上述輸入體的旋轉以上述第2變速比傳遞到上述輸出體的第2行星變速路線；上述設定機構，將上述傳遞機構設定成在上述第2變速路線未經由上述第1行星機構的變速。 在習知的自行車用變速器，在使變速比階段性變大的情況，包含：從齒數較少的太陽齒輪變更到齒數較多的太陽齒輪的階段、及從齒數較多的太陽齒輪變更到齒數較少的太陽齒輪的階段兩種。因此變速路線的組成很複雜。 藉由上述構造，在以較第2變速比更大的變速比傳遞到輸出體的第2變速路線，未經由第1行星機構的變速。因此，與在形成較第2變速比更大的變速比的路線再經由第1行星機構的變速的情況相比，變速路線的組成較簡單。因此能適當地變更變速比。 [0006] 在根據上述第1型態的第2型態的自行車用變速器其中，上述第1行星機構及上述第2行星機構，都將來自上述輸入體的旋轉增速而輸出。 藉由上述構造，能藉由第1行星機構及第2行星機構的其中一方將來自輸入體的旋轉增速而輸出。 [0007] 在根據上述第1或2型態的第3型態的自行車用變速器其中，上述複數的變速機構，進一步包含：至少經由上述第2變速路線的第2變速機構；上述第2變速機構，包含第3行星機構及第4行星機構；上述第2變速路線包含：經由上述第3行星機構的變速而未經由上述第4行星機構的變速而將來自上述輸入體的旋轉以較上述第2變速比更大的第3變速比傳遞到上述輸出體的第3行星變速路線、及未經由上述第3行星機構的變速而經由上述第4行星機構的變速而將來自上述輸入體的旋轉以較上述第3變速比更大的第4變速比傳遞到上述輸出體的第4行星變速路線；上述設定機構，將上述變速路線設定成在與較上述第4變速比更大的變速比對應的上述變速路線未經由上述第3行星機構的變速。 藉由上述構造，在以較第4變速比更大的變速比傳遞到輸出體的變速路線，未經由第3行星機構的變速。因此，與在形成較第4變速比更大的變速比的路線再經由第3行星機構的變速的情況相比，變速路線的組成較簡單。 [0008] 在根據上述第3型態的第4型態的自行車用變速器其中，上述第3行星機構，將來自上述輸入體的旋轉增速而輸出。 藉由上述構造，能藉由第3行星機構將來自輸入體的旋轉增速而輸出。 [0009] 在根據上述第3或4型態的第5型態的自行車用變速器，上述第4行星機構，將來自上述輸入體的旋轉增速而輸出。 藉由上述構造，能藉由第4行星機構將來自輸入體的旋轉增速而輸出。 [0010] 本發明的第6型態的自行車用變速器，是用來將輸入體的旋轉變速而傳遞到輸出體；上述自行車用變速器具備有：包含將來自上述輸入體的旋轉變速而輸出到上述輸出體的複數的變速機構且將來自上述輸入體的旋轉以3階段以上的變速比傳遞到上述輸出體的傳遞機構、及用來設定上述輸入體的旋轉的上述傳遞機構的變速路線的設定機構；上述複數的變速機構，分別包含至少一個行星機構；上述傳遞機構，至少形成：至少經由一個上述變速機構的變速而以上述3階段以上的變速比之中的第1預定變速比將來自上述輸入體的旋轉傳遞到上述輸出體的第1變速路線、及經由與在上述第1變速路線所經由的上述變速機構不同的上述變速機構的變速，以較上述第1預定變速比更大的第2預定變速比將來自上述輸入體的旋轉傳遞到上述輸出體的第2變速路線；上述設定機構，將上述傳遞機構設定成：在上述第2變速路線經由在上述第1變速路線所經由的上述變速機構的變速的情況，在與較上述第2預定變速比更大的變速比對應的上述變速路線，經由在上述第1變速路線所經由的上述變速機構的變速。 藉由上述構造，在以較第2預定變速比更大的變速比傳遞到輸出體的變速路線，經由在第1變速路線所經由的變速機構的變速。因此，在形成較第2預定變速比更大的變速比的路線，不會變更成未經由在第1變速路線所經由的變速機構的變速的變速路線。因此能簡化變速路線的組成。因此能適當地變更變速比。 [0011] 在根據上述第6型態的第7型態的自行車用變速器其中，在上述第1變速路線所經由的上述變速機構，包含第1行星機構及第2行星機構。 藉由上述構造，由於在第1變速路線包含兩個行星機構，所以能使在第1變速路線所能達成的變速比的數量增加。 [0012] 在根據上述第7型態的第8型態的自行車用變速器其中，上述第1行星機構及上述第2行星機構，都將來自上述輸入體的旋轉增速而輸出。 藉由上述構造，能藉由第1行星機構及第2行星機構的其中一方將來自輸入體的旋轉增速而輸出。 [0013] 在根據上述第1至5、7及8型態的任一型態的第9型態的自行車用變速器其中，進一步具備有支承構件，上述第1行星機構包含：以上述支承構件可旋轉地支承的第1太陽齒輪、配置在上述第1太陽齒輪周圍的第1環狀齒輪、及與上述第1太陽齒輪卡合而可相對於上述第1太陽齒輪及上述第1環狀齒輪公轉的第1行星齒輪；上述第2行星機構包含：以上述支承構件可旋轉地支承的第2太陽齒輪、配置在上述第2太陽齒輪周圍的第2環狀齒輪、及與上述第2太陽齒輪卡合而可相對於上述第2太陽齒輪及上述第2環狀齒輪公轉的第2行星齒輪；上述設定機構包含：將上述第1太陽齒輪設定成相對於上述支承構件可旋轉的旋轉狀態與不能旋轉的限制狀態的任一方的第1設定構件、及將上述第2太陽齒輪設定成相對於上述支承構件可旋轉的旋轉狀態與不能旋轉的限制狀態的任一方的第2設定構件；將上述第1設定構件與上述第2設定構件控制成：如果上述第1太陽齒輪及上述第2太陽齒輪的其中一方為限制狀態的話，則上述第1太陽齒輪及上述第2太陽齒輪的另一方為旋轉狀態。 藉由上述構造，藉由第1設定構件與第2設定構件，則只有第1行星機構及第2行星機構的其中一方成為限制狀態，所以形成只經由第1行星機構及第2行星機構的其中一方的變速路線。 [0014] 在根據上述第9型態的第10型態的自行車用變速器其中，上述第1行星齒輪及上述第2行星齒輪，形成於第1行星齒輪構件；上述第1環狀齒輪及上述第2環狀齒輪，形成於第1環狀齒輪構件。 藉由上述構造，將第1行星齒輪及第2行星齒輪形成於一個第1行星齒輪構件，將第1環狀齒輪及第2環狀齒輪形成於一個第1環狀齒輪構件，所以能有助於減少零件數量。 [0015] 在根據上述第10型態的第11型態的自行車用變速器其中，上述第1環狀齒輪構件包含第1齒輪部；上述第1齒輪部，共用為上述第1環狀齒輪及上述第2環狀齒輪。 藉由上述構造，由於將第1齒輪部共用為第1環狀齒輪及第2環狀齒輪，所以能簡化第1環狀齒輪的構造。 [0016] 在根據上述第9至11型態的任一型態的第12型態的自行車用變速器其中，上述設定機構，在藉由上述第1設定構件將上述第1太陽齒輪從上述限制狀態設定為上述旋轉狀態，且藉由上述第2設定構件將上述第2太陽齒輪從上述旋轉狀態設定為上述限制狀態的動作，是藉由上述第2設定構件將上述第2太陽齒輪從上述旋轉狀態設定為上述限制狀態之後，再藉由上述第1設定構件將上述第1太陽齒輪從上述限制狀態設定為上述旋轉狀態。 在習知的自行車用變速器，在將變速比階段性變大的情況，當從使用齒數較少的太陽齒輪進行變速的狀態變更為使用齒數較多的太陽齒輪進行變速的狀態時，往往會有因為傳遞到齒數較少的太陽齒輪的轉矩而難以變更太陽齒輪的狀態的情況。 藉由上述構造，當藉由第1設定構件將第1太陽齒輪從限制狀態設定為旋轉狀態時，藉由第2設定構件將第2太陽齒輪設定為限制狀態，所以可在作用於第1設定構件與第1太陽齒輪之間的力較小的狀態變更變速比。因此能適當地變更變速比。 [0017] 在根據上述第3至5型態的任一型態的第13型態的自行車用變速器其中，進一步具備有支承構件，上述第3行星機構包含：以上述支承構件可旋轉地支承的第3太陽齒輪、配置在上述第3太陽齒輪周圍的第3環狀齒輪、及與上述第3太陽齒輪卡合而可相對於上述第3太陽齒輪及上述第3環狀齒輪公轉的第3行星齒輪；上述第4行星機構包含：以上述支承構件可旋轉地支承的第4太陽齒輪、配置在上述第4太陽齒輪周圍的第4環狀齒輪、及與上述第4太陽齒輪卡合而可相對於上述第4太陽齒輪及上述第4環狀齒輪公轉的第4行星齒輪；上述設定機構包含：將上述第3太陽齒輪設定成相對於上述支承構件可旋轉的旋轉狀態與不能旋轉的限制狀態的任一方的第3設定構件、及將上述第4太陽齒輪設定成相對於上述支承構件可旋轉的旋轉狀態與不能旋轉的限制狀態的任一方的第4設定構件；將上述第3設定構件與上述第4設定構件控制成：如果上述第3太陽齒輪及上述第4太陽齒輪的其中一方為限制狀態的話，則上述第3太陽齒輪及上述第4太陽齒輪的另一方為旋轉狀態。 藉由上述構造，藉由第3設定構件與第4設定構件，則只有第3行星機構及第4行星機構的其中一方成為限制狀態，所以形成只經由第3行星機構及第4行星機構的其中一方的變速路線。 [0018] 在根據上述第13型態的第14型態的自行車用變速器其中，上述第3行星齒輪及上述第4行星齒輪，形成於第2行星齒輪構件；上述第3環狀齒輪及上述第4環狀齒輪，形成於第2環狀齒輪構件。 藉由上述構造，將第3行星齒輪及第4行星齒輪形成於一個第2行星齒輪構件，將第3環狀齒輪及第4環狀齒輪形成於一個第2環狀齒輪構件，所以能有助於減少零件數量。 [0019] 在根據上述第14型態的第15型態的自行車用變速器其中，上述第2環狀齒輪構件包含第2齒輪部；上述第2齒輪部，共用為上述第3環狀齒輪及上述第4環狀齒輪。 藉由上述構造，由於將第2齒輪部共用為第3環狀齒輪及第4環狀齒輪，所以能簡化第2環狀齒輪的構造。 [0020] 在根據上述第13至15型態的任一型態的第16型態的自行車用變速器其中，在藉由上述第3設定構件將上述第3太陽齒輪從上述限制狀態設定為上述旋轉狀態，且藉由上述第4設定構件將上述第4太陽齒輪從上述旋轉狀態設定為上述限制狀態的動作，是藉由上述第4設定構件將上述第4太陽齒輪從上述旋轉狀態設定為上述限制狀態之後，再藉由上述第3設定構件將上述第3太陽齒輪從上述限制狀態設定為上述旋轉狀態。 藉由上述構造，當藉由第3設定構件將第3太陽齒輪從限制狀態設定為旋轉狀態時，藉由第4設定構件將第4太陽齒輪設定為限制狀態，所以可在作用於第3設定構件與第3太陽齒輪之間的力較小的狀態變更變速比。因此能適當地變更變速比。 [0021] 本發明的第17型態的自行車用變速器，是將輸入體的旋轉變速而傳遞到輸出體；上述自行車用變速器具備有：包含將來自上述輸入體的旋轉變速而輸出到上述輸出體的變速機構且將來自上述輸入體的旋轉以2階段以上的變速比傳遞到上述輸出體的傳遞機構、用來設定上述傳遞機構的變速路線的設定機構、及支承構件；上述變速機構，具備有：可設定為可旋轉的旋轉狀態與限制旋轉的限制狀態的其中任一方且被上述支承構件所支承的複數的傳遞體；上述複數的傳遞體，包含第1傳遞體及第2傳遞體，上述傳遞機構的上述變速路線，包含：將來自上述輸入體的旋轉經由上述第1傳遞體變速而傳遞到上述輸出體的第1路線、及將來自上述輸入體的旋轉經由上述第2傳遞體以較上述第1路線更大1階段的上述變速比變速而傳遞到上述輸出體的第2路線；上述設定機構，在將上述變速路線從上述第1路線設定為上述第2路線的動作，在將上述第2傳遞體從上述旋轉狀態限制為上述限制狀態之後，將上述第1傳遞體從上述限制狀態設定為上述旋轉狀態。 藉由上述構造，當將第1傳遞體從限制狀態設定為旋轉狀態時，將第2傳遞體設定為限制狀態，所以能在作用於第2傳遞體的力量較小的狀態變更變速比。因此能適當地變更變速比。 [0022] 在根據上述第17型態的第18型態的自行車用變速器其中，上述變速機構，包含第1變速機構，上述第1變速機構，包含第1行星機構及第2行星機構；上述第1行星機構，包含上述第1傳遞體也就是第1太陽齒輪；上述第2行星機構，包含上述第2傳遞體也就是第2太陽齒輪；上述設定機構，包含：將上述第1太陽齒輪設定為上述旋轉狀態與上述限制狀態的任一方的第1設定構件、及將上述第2太陽齒輪設定為上述旋轉狀態與上述限制狀態的任一方的第2設定構件；將上述第1設定構件與上述第2設定構件控制為：如果上述第1太陽齒輪及上述第2太陽齒輪的其中一方為上述限制狀態的話，則上述第1太陽齒輪及上述第2太陽齒輪的另一方為上述旋轉狀態。 藉由上述構造，藉由第1設定構件與第2設定構件，則只有第1行星機構及第2行星機構的其中一方成為限制狀態，所以形成只經由第1行星機構及第2行星機構的其中一方的變速路線。當藉由第1設定構件將第1太陽齒輪從限制狀態設定為旋轉狀態時，能藉由第2設定構件將第2太陽齒輪設定為限制狀態，所以將作用於第1設定構件與第1太陽齒輪之間的力適當地變小。 [0023] 在根據上述第17或18型態的第19型態的自行車用變速器其中，上述變速機構，包含第2變速機構，上述第2變速機構，包含第3行星機構及第4行星機構；上述第3行星機構，包含上述第1傳遞體也就是第3太陽齒輪；上述第4行星機構，包含上述第2傳遞體也就是第4太陽齒輪；上述設定機構，包含：將上述第3太陽齒輪設定為上述旋轉狀態與上述限制狀態的任一方的第3設定構件、及將上述第4太陽齒輪設定為上述旋轉狀態與上述限制狀態的任一方的第4設定構件；將上述第3設定構件與上述第4設定構件控制為：如果上述第3太陽齒輪及上述第4太陽齒輪的其中一方為上述限制狀態的話，則上述第3太陽齒輪及上述第4太陽齒輪的另一方為上述旋轉狀態。 藉由上述構造，藉由第3設定構件與第4設定構件，則只有第3行星機構及第4行星機構的其中一方成為限制狀態，所以形成只經由第3行星機構及第4行星機構的其中一方的變速路線。當藉由第3設定構件將第3太陽齒輪從限制狀態設定為旋轉狀態時，能藉由第4設定構件將第4太陽齒輪設定為限制狀態，所以將作用於第3設定構件與第3太陽齒輪之間的力適當地變小。 [0024] 在根據上述第17至19型態的任一型態的第20型態的自行車用變速器其中，上述設定機構，包含：可與上述第1傳遞體的內周部卡合且配置在上述支承構件周圍的爪構件。 藉由上述構造，藉由第1傳遞體與爪構件的卡合，則能適當地形成第1傳遞體的限制狀態。 [0025] 在根據上述第20型態的第21型態的自行車用變速器其中，在上述第1傳遞體的上述內周部，形成有可讓上述爪構件嵌入的溝部。 藉由上述構造，藉由第1傳遞體的溝部與爪構件的卡合，則能適當地形成第1傳遞體的限制狀態。 [0026] 在根據上述第17或21型態的第22型態的自行車用變速器其中，上述設定機構，在作用於上述爪構件與上述第1傳遞體之間的轉矩為預定值以下的狀態，將上述第1傳遞體從上述限制狀態設定為上述旋轉狀態。 藉由上述構造，在將第1傳遞體從限制狀態設定為旋轉狀態的情況，可讓作用於爪構件與第1傳遞體之間的轉矩成為預定值以下，所以能將第1傳遞體從限制狀態適當地變更為旋轉狀態。 [0027] 在根據上述第22型態的第23型態的自行車用變速器其中，上述預定值為15Nm。 藉由上述構造，在將第1傳遞體從限制狀態設定為旋轉狀態的情況，可讓作用於爪構件與第1傳遞體之間的轉矩成為15Nm以下，所以能將第1傳遞體從限制狀態適當地變更為旋轉狀態。 [0028] 在根據上述第1至23型態中任一型態的第24型態的自行車用變速器其中，上述傳遞機構，進一步形成有未將上述輸入體的旋轉變速而輸出到上述輸出體的無變速路線。 藉由上述構造，藉由形成無變速路線，則能使自行車用變速器能達成的變速比增加。 [0029] 在根據上述第1至24型態中任一型態的第25型態的自行車用變速器其中，上述自行車用變速器，進一步具備有：用來將上述傳遞機構及上述設定機構收容的輪轂。 藉由上述構造，在具備輪轂的自行車用變速器，也就是在內裝變速輪轂能將變速路線的組成簡化。 [0030] 本發明的第26型態的自行車用輔助系統，具備有：上述第1至25型態的任一型態的自行車用變速器、及輔助人力驅動力的馬達。 藉由上述構造，在藉由馬達輔助人力驅動力的自行車所搭載的自行車用變速器，也能使變速路線的組成簡化。 [0031] 根據上述第26型態的第27型態的自行車用變速器，進一步具備有：為了操作上述自行車用變速器而藉由人手操作的操作部，上述自行車用變速器，因應對上述操作部的操作來變更自行車的變速比。 藉由上述構造，在因應對操作部的操作來變更自行車的變速比的自行車所搭載的自行車用變速器，也能使變速路線的組成簡化。 [發明效果] [0032] 本自行車用變速器及具備該變速器的自行車用輔助系統能適當地將變速比變更。[Problem to be Solved by the Invention] [0004] The object of the present invention is to provide a bicycle transmission and a bicycle auxiliary system equipped with the transmission, which can appropriately change the gear ratio. [Means to Solve the Problem] [0005] The bicycle transmission of the first aspect of the present invention is used to transmit the rotational speed of the input body to the output body; the bicycle transmission includes: A plurality of speed change mechanisms that output the rotation of the body to the output body and transmit the rotation from the input body to the output body at a speed ratio of three or more stages, and a transmission mechanism for setting the speed change path of the transmission mechanism Setting mechanism; the plurality of speed change mechanisms, including at least a first speed change mechanism, the first speed change mechanism includes a first planetary mechanism and a second planetary mechanism; One of the first gear ratio and the second gear ratio among the above-mentioned three-step or more gear ratios transmits the rotation from the input body to the first gear shift path of the output body, and via the first gear ratio between the first gear ratio and the second gear ratio. The speed change of the said speed change mechanism through the said speed change mechanism is a second speed change path which transmits the rotation from the said input body to the said output body at a speed ratio greater than the said first speed ratio and the said second speed ratio; The first speed change path includes: a first planetary speed change path that transmits the rotation from the input body to the output body at the first speed ratio without speed change by the second planetary mechanism through the speed change of the first planetary mechanism, And a second planetary transmission path that transmits the rotation from the input body to the output body at the second gear ratio through the transmission of the second planetary mechanism without shifting by the first planetary mechanism; the setting mechanism will The transmission mechanism is set so as not to be shifted by the first planetary mechanism in the second shift path. In the conventional bicycle transmission, the stepwise increase in the gear ratio includes: changing from a sun gear with a small number of teeth to a sun gear with a large number of teeth, and changing from a sun gear with a large number of teeth to the number of teeth There are two stages with fewer sun gears. Therefore, the composition of the shifting route is complicated. With the above-mentioned structure, the second speed change path that is transmitted to the output body with a larger speed ratio than the second speed ratio is not shifted by the first planetary mechanism. Therefore, the composition of the speed change path is simpler compared to the case where the speed change is performed via the first planetary mechanism in a route where a speed ratio greater than the second speed ratio is formed. Therefore, the gear ratio can be changed appropriately. [0006] In the bicycle transmission of the second type according to the first type, the first planetary mechanism and the second planetary mechanism both increase the speed of rotation from the input body and output it. With the above structure, one of the first planetary mechanism and the second planetary mechanism can increase the speed of the rotation from the input body and output it. [0007] In the bicycle transmission of the third type according to the first or second type, the plurality of speed change mechanisms further include: a second speed change mechanism via at least the second speed change path; the second speed change mechanism , Including a third planetary mechanism and a fourth planetary mechanism; the second speed change path includes: the speed of the third planetary mechanism without the speed of the fourth planetary mechanism and the rotation from the input body to compare the second The third gear ratio, which has a larger gear ratio, is transmitted to the third planetary gear shift path of the output body, and the rotation from the input body is compared by the gear shift of the fourth planetary mechanism without the gear shift of the third planetary mechanism. The fourth gear ratio with the larger third gear ratio is transmitted to the fourth planetary gear shift path of the output body; the setting mechanism sets the gear shift path to the gear ratio that corresponds to the gear ratio larger than the fourth gear ratio. The shift path is not shifted by the above-mentioned third planetary mechanism. With the above-mentioned structure, the third planetary mechanism does not use the third planetary mechanism in the transmission route to the output body with a larger gear ratio than the fourth gear ratio. Therefore, the composition of the speed change path is simpler than when the third planetary mechanism is used for speed change in a route that has a higher speed ratio than the fourth speed ratio. [0008] In the bicycle transmission of the fourth type according to the third type, the third planetary mechanism increases the speed of the rotation from the input body and outputs it. With the above structure, the rotation from the input body can be increased and output by the third planetary mechanism. [0009] In the fifth type bicycle transmission according to the third or fourth type, the fourth planetary mechanism increases the speed of the rotation from the input body and outputs it. With the above structure, the rotation from the input body can be increased and output by the fourth planetary mechanism. [0010] The bicycle transmission of the sixth aspect of the present invention is used to transmit the rotational speed of the input body to the output body; the bicycle transmission includes: A plurality of speed change mechanisms for the output body and a transmission mechanism for transmitting the rotation from the input body to the output body at a speed ratio of three or more stages, and a setting mechanism for setting the speed change path of the transmission mechanism for the rotation of the input body The plurality of speed change mechanisms each include at least one planetary mechanism; the transmission mechanism at least forms: at least through the speed change of the speed change mechanism, the first predetermined speed ratio among the three or more speed ratios will come from the input The rotation of the body is transmitted to the first speed change path of the output body, and the speed change via the speed change mechanism that is different from the speed change mechanism through which the first speed change path passes, to a second predetermined speed ratio that is greater than the first predetermined speed ratio. The predetermined gear ratio transmits the rotation from the input body to the second gear shift path of the output body; In the case of the gear shifting of the mechanism, the gear shift path corresponding to the gear ratio larger than the second predetermined gear ratio is shifted via the gear shift mechanism through the first gear ratio. With the above-mentioned structure, in the transmission path transmitted to the output body with a larger transmission ratio than the second predetermined transmission ratio, the transmission is performed via the transmission mechanism through the first transmission path. Therefore, in a route that forms a gear ratio larger than the second predetermined gear ratio, it is not changed to a gear shift route that is not shifted by the transmission mechanism through the first gear shift route. Therefore, the composition of the shifting route can be simplified. Therefore, the gear ratio can be changed appropriately. [0011] In the bicycle transmission of the seventh form according to the sixth form, the speed change mechanism through which the first speed change route passes includes a first planetary mechanism and a second planetary mechanism. With the above-mentioned structure, since two planetary mechanisms are included in the first shifting route, the number of gear ratios that can be achieved in the first shifting route can be increased. [0012] In the bicycle transmission of the eighth form according to the seventh form, the first planetary mechanism and the second planetary mechanism both increase the speed of rotation from the input body and output it. With the above structure, one of the first planetary mechanism and the second planetary mechanism can increase the speed of the rotation from the input body and output it. [0013] In a ninth type bicycle transmission according to any one of the above-mentioned first to 5th, 7th, and 8th forms, further comprising a support member, and the first planetary mechanism includes: the support member may be A first sun gear that is rotatably supported, a first ring gear disposed around the first sun gear, and the first sun gear are engaged with the first sun gear so as to revolve relative to the first sun gear and the first ring gear The first planetary gear; the second planetary mechanism includes: a second sun gear rotatably supported by the support member, a second ring gear arranged around the second sun gear, and the second sun gear card Together, a second planetary gear that can revolve relative to the second sun gear and the second ring gear; the setting mechanism includes: setting the first sun gear to a rotatable and non-rotatable state with respect to the support member The first setting member in any one of the restricted states, and the second setting member that sets the second sun gear to either a rotatable state or a non-rotatable restricted state with respect to the support member; the first The setting member and the second setting member are controlled so that if one of the first sun gear and the second sun gear is in a restricted state, the other of the first sun gear and the second sun gear is in a rotating state. With the above structure, with the first setting member and the second setting member, only one of the first planetary mechanism and the second planetary mechanism becomes a restricted state, so it is formed only through the first planetary mechanism and the second planetary mechanism. One side's variable speed route. [0014] In the bicycle transmission of the tenth form according to the ninth form, the first planetary gear and the second planetary gear are formed in a first planetary gear member; the first ring gear and the first 2 ring gears are formed in the first ring gear member. With the above structure, the first planetary gear and the second planetary gear are formed in a first planetary gear member, and the first ring gear and the second ring gear are formed in a first ring gear member, so it can help To reduce the number of parts. [0015] In the bicycle transmission of the eleventh aspect according to the tenth aspect, the first ring gear member includes a first gear portion; and the first gear portion is shared as the first ring gear and the The second ring gear. "With the above structure, since the first gear part is shared as the first ring gear and the second ring gear, the structure of the first ring gear can be simplified. [0016] In a bicycle transmission of a twelfth aspect according to any one of the ninth to eleventh aspects, the setting mechanism is configured to remove the first sun gear from the restricted state by the first setting member The operation of setting to the above-mentioned rotating state and setting the second sun gear from the above-mentioned rotating state to the above-mentioned restricted state by the above-mentioned second setting member is to set the second sun gear from the above-mentioned rotating state by the above-mentioned second setting member After setting to the restricted state, the first sun gear is set from the restricted state to the rotating state by the first setting member. In the conventional bicycle transmission, when the gear ratio is increased stepwise, when changing from a state where the sun gear with a small number of teeth is used for shifting to a state where the sun gear with a large number of teeth is used for shifting, there is often It is difficult to change the state of the sun gear due to the torque transmitted to the sun gear with a small number of teeth. With the above structure, when the first sun gear is set from the restricted state to the rotating state by the first setting member, the second sun gear is set to the restricted state by the second setting member, so it can be used in the first setting. When the force between the member and the first sun gear is small, the gear ratio is changed. Therefore, the gear ratio can be changed appropriately. [0017] In a bicycle transmission of a thirteenth aspect according to any one of the third to fifth aspects described above, further comprising a support member, and the third planetary mechanism includes: rotatably supported by the support member A third sun gear, a third ring gear arranged around the third sun gear, and a third planet that is engaged with the third sun gear and can revolve relative to the third sun gear and the third ring gear Gear; The fourth planetary mechanism includes: a fourth sun gear rotatably supported by the support member, a fourth ring gear disposed around the fourth sun gear, and the fourth sun gear engaged with the fourth sun gear to be opposed A fourth planetary gear that revolves in the fourth sun gear and the fourth ring gear; the setting mechanism includes: setting the third sun gear to a rotational state and a non-rotatable restricted state with respect to the support member Any one of the third setting member, and the fourth setting member that sets the fourth sun gear to either a rotatable state or a non-rotatable restricted state with respect to the support member; the third setting member is combined with the above The fourth setting member is controlled so that if one of the third sun gear and the fourth sun gear is in a restricted state, the other of the third sun gear and the fourth sun gear is in a rotating state. With the above structure, with the third setting member and the fourth setting member, only one of the third planetary mechanism and the fourth planetary mechanism becomes a restricted state, so it is formed only through the third planetary mechanism and the fourth planetary mechanism. One side's variable speed route. [0018] In the bicycle transmission according to the thirteenth aspect and the fourteenth aspect, the third planetary gear and the fourth planetary gear are formed in a second planetary gear member; the third ring gear and the first Four ring gears are formed in the second ring gear member. With the above structure, the third planetary gear and the fourth planetary gear are formed in one second planetary gear member, and the third ring gear and the fourth ring gear are formed in one second ring gear member, so it can help To reduce the number of parts. [0019] In the bicycle transmission of the fifteenth aspect according to the fourteenth aspect, the second ring gear member includes a second gear portion; and the second gear portion is commonly used as the third ring gear and the The 4th ring gear. "With the above structure, since the second gear part is shared as the third ring gear and the fourth ring gear, the structure of the second ring gear can be simplified. [0020] In the bicycle transmission of the 16th mode according to any of the 13th to 15th modes, the third sun gear is set from the restricted state to the rotation by the third setting member. The operation of setting the fourth sun gear from the rotation state to the restricted state by the fourth setting member is to set the fourth sun gear from the rotation state to the restriction by the fourth setting member After the state, the third sun gear is set from the restricted state to the rotating state by the third setting member. With the above structure, when the third sun gear is set from the restricted state to the rotating state by the third setting member, the fourth sun gear is set to the restricted state by the fourth setting member, so it can be used in the third setting. When the force between the member and the third sun gear is small, the gear ratio is changed. Therefore, the gear ratio can be changed appropriately. [0021] The bicycle transmission of the 17th aspect of the present invention transmits the rotation speed of the input body to the output body; the bicycle transmission includes: The transmission mechanism that transmits the rotation from the input body to the output body at a speed ratio of two or more stages, a setting mechanism for setting the transmission path of the transmission mechanism, and a support member; the transmission mechanism includes: : A plurality of transmission bodies that can be set in either a rotatable rotation state or a restricted rotation state and supported by the support member; the plurality of transmission bodies includes a first transmission body and a second transmission body, the above The speed change path of the transmission mechanism includes: a first path for transmitting the rotation from the input body to the output body via the first transmission body, and comparing the rotation from the input body via the second transmission body. The first route is one step larger than the transmission of the gear ratio to the second route of the output body; the setting mechanism, in the operation of setting the speed change route from the first route to the second route, sets the After the second transmission body is restricted from the rotation state to the restriction state, the first transmission body is set from the restriction state to the rotation state. With the above structure, when the first transmitting body is set from the restricted state to the rotating state, the second transmitting body is set to the restricted state, so that the gear ratio can be changed in a state where the force acting on the second transmitting body is small. Therefore, the gear ratio can be changed appropriately. [0022] In the bicycle transmission according to the seventeenth aspect and the eighteenth aspect, the speed change mechanism includes a first speed change mechanism, the first speed change mechanism includes a first planetary mechanism and a second planetary mechanism; 1 planetary mechanism, including the first transmitting body, which is the first sun gear; the second planetary mechanism, including the second transmitting body, which is the second sun gear; the setting mechanism, including: setting the first sun gear to A first setting member in either of the rotation state and the restriction state, and a second setting member that sets the second sun gear to either of the rotation state and the restriction state; and the first setting member and the first setting member 2 The setting means is controlled such that if one of the first sun gear and the second sun gear is in the restricted state, the other of the first sun gear and the second sun gear is in the rotating state. With the above structure, with the first setting member and the second setting member, only one of the first planetary mechanism and the second planetary mechanism becomes a restricted state, so it is formed only through the first planetary mechanism and the second planetary mechanism. One side's variable speed route. When the first sun gear is set from the restricted state to the rotating state by the first setting member, the second sun gear can be set to the restricted state by the second setting member, so it will act on the first setting member and the first sun The force between the gears is appropriately reduced. [0023] In the bicycle transmission of the 19th type according to the above-mentioned 17th or 18th type, the speed change mechanism includes a second speed change mechanism, and the second speed change mechanism includes a third planetary mechanism and a fourth planetary mechanism; The third planetary mechanism includes the first transmission body, which is the third sun gear; the fourth planetary mechanism includes the second transmission body, which is the fourth sun gear; and the setting mechanism includes: the third sun gear A third setting member that is set to one of the rotation state and the restriction state, and a fourth setting member that sets the fourth sun gear to either the rotation state and the restriction state; and the third setting member is combined with The fourth setting member is controlled such that if one of the third sun gear and the fourth sun gear is in the restricted state, the other of the third sun gear and the fourth sun gear is in the rotating state. With the above structure, with the third setting member and the fourth setting member, only one of the third planetary mechanism and the fourth planetary mechanism becomes a restricted state, so it is formed only through the third planetary mechanism and the fourth planetary mechanism. One side's variable speed route. When the third sun gear is set from the restricted state to the rotating state by the third setting member, the fourth sun gear can be set to the restricted state by the fourth setting member, so it will act on the third setting member and the third sun The force between the gears is appropriately reduced. [0024] In a bicycle transmission of a twentieth type according to any of the 17th to 19th types, the setting mechanism includes: engageable with the inner peripheral portion of the first transmitting body and is arranged at The claw member around the support member. With the above structure, the first transmission body and the claw member are engaged with each other to appropriately form the restricted state of the first transmission body. [0025] In the bicycle transmission of the 21st aspect according to the 20th aspect, the inner peripheral part of the first transmitting body is formed with a groove into which the claw member can be fitted. With the above-mentioned structure, by the engagement of the groove portion of the first transmission body and the claw member, the restricted state of the first transmission body can be appropriately formed. [0026] In the bicycle transmission of the 22nd aspect according to the 17th or 21st aspect, the setting mechanism is in a state where the torque acting between the pawl member and the first transmitting body is less than or equal to a predetermined value , Setting the first transmitting body from the restricted state to the rotating state. With the above structure, when the first transmitting body is set from the restricted state to the rotating state, the torque acting between the pawl member and the first transmitting body can be lower than the predetermined value, so the first transmitting body can be removed from The restricted state is appropriately changed to the rotating state. [0027] In the bicycle transmission of the 23rd type according to the 22nd type, the predetermined value is 15 Nm. With the above structure, when the first transmitting body is set from the restricted state to the rotating state, the torque acting between the pawl member and the first transmitting body can be 15Nm or less, so the first transmitting body can be removed from the restricted state. The state is appropriately changed to the rotating state. [0028] In the bicycle transmission of the 24th form according to any one of the above-mentioned 1st to 23rd forms, the transmission mechanism is further formed with a device for outputting the rotation of the input body to the output body without changing the speed of the rotation of the input body. No variable-speed routes. With the above structure, the gear ratio that can be achieved by the bicycle transmission can be increased by forming a non-shifting route. [0029] In a bicycle transmission according to any one of the first to 24 forms, the bicycle transmission further includes: a hub for housing the transmission mechanism and the setting mechanism . With the above structure, the structure of the transmission line can be simplified in a bicycle transmission equipped with a hub, that is, a built-in transmission hub. [0030] The bicycle assist system of the 26th aspect of the present invention is provided with a bicycle transmission of any one of the above-mentioned 1st to 25th forms, and a motor that assists human driving force. With the above-mentioned structure, the structure of the shifting route can be simplified even in the bicycle transmission mounted on the bicycle that uses the motor to assist the human driving force. [0031] The bicycle transmission according to the twenty-sixth aspect and the twenty-seventh aspect is further provided with an operation part that is manually operated in order to operate the bicycle transmission, and the bicycle transmission is responsive to the operation of the operation part. To change the gear ratio of the bicycle. With the above-mentioned structure, it is also possible to simplify the composition of the shifting route for the bicycle transmission mounted on the bicycle that changes the gear ratio of the bicycle in response to the operation of the operation part. [Effects of the Invention] [0032] The bicycle transmission and the bicycle auxiliary system provided with the transmission can appropriately change the gear ratio.
[0034] (第1實施方式) 參考第1至19圖，針對搭載第1實施方式的自行車用輔助系統40的自行車10來說明。 [0035] 如第1圖所示，自行車10具備有：車體12、驅動機構14、前輪16、後輪18、及自行車用輔助系統40。車體12具備有：框架12A及安裝於框架12A的車把桿12B。 [0036] 驅動機構14具備有：曲柄20、踏板22、前旋轉體24、傳遞構件26、後旋轉體28。曲柄20包含曲柄軸20A及曲柄臂20B。驅動機構14，將施加於踏板22的人力驅動力傳遞至後輪18。前旋轉體24包含：鏈輪、滑輪、或斜齒輪。後旋轉體28包含：鏈輪、滑輪、或斜齒輪。傳遞構件26，例如經由鏈條、皮帶、或軸部，將曲柄20的旋轉傳遞至後輪18。前旋轉體24，經由單向離合器(省略圖示)而結合於曲柄軸20A。單向離合器，當曲柄20前轉時，使前旋轉體24前轉，當曲柄20後轉時，不使前旋轉體24後轉。前旋轉體24，也可未經由單向離合器而結合於曲柄軸20A。 [0037] 自行車用輔助系統40具備有：自行車用變速器50、馬達42。自行車用輔助系統40進一步具備有：操作部44及電池單元46。自行車用輔助系統40搭載於自行車10。 [0038] 馬達42用來輔助人力驅動力。馬達42被框架12A支承。在一個例子，馬達42設置於曲柄軸20A周圍，將馬達42的轉矩傳遞到曲柄軸20A。在其他例子，馬達42，設置在前輪16的車軸16A或後輪18的車軸18A周圍，將馬達42的轉矩傳遞到前輪16或後輪18。 [0039] 操作部44，為了操作自行車用變速器50藉由人手所操作。在一個例子，操作部44設置於車把桿12B。操作部44，安裝有波登型纜線(省略圖示)的一端。藉由使用者操作操作部44，讓波登型纜線的內纜線C1(參考第2圖)移動。波登型纜線的另一端安裝於自行車用變速器50。 [0040] 電池單元46將電力供給到馬達42。電池單元46具備有：電池元件46A、及將電池單元46安裝於框架12A的保持件46B。 [0041] 自行車用變速器50，因應對操作部44的操作來變更自行車10的變速比。自行車用變速器50具備有變速機構62。變速機構62是內裝變速器。自行車用變速器50具備有輪轂18C。也就是說，如第2圖所示，自行車用變速器50，是與輪轂18C設置為一體的內裝輪轂。 [0042] 如第3圖所示，內裝變速輪轂也就是自行車用變速器50，具備有傳遞機構52及設定機構54。輪轂18C用來收容傳遞機構52及設定機構54。自行車用變速器50進一步具備有：支承構件56、輸入體58、及輸出體60。支承構件56與後輪18的車軸18A一體化。輸入體58，與後旋轉體28可一體旋轉地設置在支承構件56周圍。輸出體60為輪轂殼罩。輸出體60具備有：用來安裝後輪18的輻絲18B的凸緣部60A。自行車用變速器50，將輸入體58的旋轉變速而傳遞到輸出體60。 [0043] 傳遞機構52包含複數的變速機構62。複數的變速機構62，至少包含第1變速機構62A。複數的變速機構62，進一步包含第2變速機構62B。傳遞機構52，以三階段以上的變速比將來自輸入體58的旋轉傳遞到輸出體60。變速機構62，可將來自輸入體58的旋轉變速而輸出到輸出體60。變速機構62，包含讓變速比階段性變大的4個以上的變速檔位。變速機構62，包含讓變速比階段性變大的5個以上的變速檔位。第3圖所示的變速機構62包含5個變速檔位。 [0044] 複數的變速機構62，分別包含至少一個行星機構64、66、68、70。複數的變速機構62包含：第1行星機構64及第2行星機構66。複數的變速機構62進一步包含：第3行星機構68及第4行星機構70。具體來說，第1變速機構62A包含：第1行星機構64及第2行星機構66。第2變速機構62B包含：第3行星機構68及第4行星機構70。第1行星機構64，在自行車用變速器50的軸方向配置在輸入體58旁邊。第2行星機構66，在自行車用變速器50的軸方向配置在第1行星機構64旁邊及在輸入體58的相反側。第4行星機構70，在自行車用變速器50的軸方向配置在第2行星機構66旁邊及在第1行星機構64的相反側。第3行星機構68，在自行車用變速器50的軸方向配置在第4行星機構70旁邊及在第2行星機構66的相反側。 [0045] 第1行星機構64包含：第1太陽齒輪72、第1環狀齒輪74、第1行星齒輪76、及第1載體78。第1太陽齒輪72，在支承構件56的軸周圍可旋轉地被支承構件56所支承。第1環狀齒輪74配置在第1太陽齒輪72周圍。第1行星齒輪76，與第1太陽齒輪72卡合而可相對第1太陽齒輪72及第1環狀齒輪74公轉。第1行星機構64包含複數的第1行星齒輪76。第1載體78分別可旋轉地支承著複數的第1行星齒輪76。第1載體78，設置成可繞支承構件56的軸周圍旋轉。複數的第1行星齒輪76，分別伴隨第1載體78的旋轉而在第1太陽齒輪72周圍公轉。第1載體78，連接於輸入體58，傳遞來自輸入體58的旋轉。第1行星機構64，將來自輸入體58的旋轉增速而輸出。 [0046] 第2行星機構66包含：第2太陽齒輪80、第2環狀齒輪82、第2行星齒輪84、及第2載體86。第2太陽齒輪80，在支承構件56的軸周圍可旋轉地被支承構件56所支承。第2環狀齒輪82配置在第2太陽齒輪80周圍。第2行星齒輪84，與第2太陽齒輪80卡合而可相對第2太陽齒輪80及第2環狀齒輪82公轉。第2行星機構66包含複數的第2行星齒輪84。第2載體86分別可旋轉地支承著複數的第2行星齒輪84。第2載體86，設置成可繞支承構件56的軸周圍旋轉。複數的第2行星齒輪84，分別伴隨第2載體86的旋轉而在第2太陽齒輪80周圍公轉。第2行星機構66，將來自輸入體58的旋轉增速而輸出。第2載體86，連接於輸入體58，傳遞來自輸入體58的旋轉。 [0047] 第1行星機構64及第2行星機構66，都將來自輸入體58的旋轉增速而輸出。第1太陽齒輪72的齒數少於第2太陽齒輪80的齒數。第1行星齒輪76的齒數多於第2行星齒輪84的齒數。第1環狀齒輪74的齒數及第2環狀齒輪82的齒數相等。第1環狀齒輪74及第2環狀齒輪82形成於第1環狀齒輪構件88。第1環狀齒輪構件88包含第1齒輪部88A。第1齒輪部88A共用為第1環狀齒輪74及第2環狀齒輪82。第1行星齒輪76及第2行星齒輪84形成於第1行星齒輪構件90。第1行星齒輪構件90構成所謂具階段的行星齒輪。第1載體78及第2載體86形成為一體。 [0048] 第3行星機構68包含：第3太陽齒輪92、第3環狀齒輪94、第3行星齒輪96、及第3載體98。第3太陽齒輪92，在支承構件56的軸周圍可旋轉地被支承構件56所支承。第3環狀齒輪94配置在第3太陽齒輪92周圍。第3行星齒輪96，與第3太陽齒輪92卡合而可相對第3太陽齒輪92及第3環狀齒輪94公轉。第3行星機構68包含複數的第3行星齒輪96。第3載體98分別可旋轉地支承著複數的第3行星齒輪96。第3載體98，設置成可繞支承構件56的軸周圍旋轉。複數的第3行星齒輪96，分別伴隨第3載體98的旋轉而在第3太陽齒輪92周圍公轉。第3載體98，連接於第1環狀齒輪構件88，傳遞來自第1環狀齒輪構件88的旋轉。 [0049] 第4行星機構70包含：第4太陽齒輪100、第4環狀齒輪102、第4行星齒輪104、及第4載體106。第4太陽齒輪100，在支承構件56的軸周圍可旋轉地被支承構件56所支承。第4環狀齒輪102配置在第4太陽齒輪100周圍。第4行星齒輪104，與第4太陽齒輪100卡合而可相對第4太陽齒輪100及第4環狀齒輪102公轉。第4行星機構70包含複數的第4行星齒輪104。第4載體106分別可旋轉地支承著複數的第4行星齒輪104。第4載體106，設置成可繞支承構件56的軸周圍旋轉。複數的第4行星齒輪104，分別伴隨第4載體106的旋轉而在第4太陽齒輪100周圍公轉。第4載體106，連接於第1環狀齒輪構件88，傳遞來自第1環狀齒輪構件88的旋轉。 [0050] 第3行星機構68，將來自輸入體58的旋轉增速而輸出。第4行星機構70，將來自輸入體58的旋轉增速而輸出。第3太陽齒輪92的齒數少於第4太陽齒輪100的齒數。第3行星齒輪96的齒數多於第4行星齒輪104的齒數。第3環狀齒輪94的齒數及第4環狀齒輪102的齒數相等。第3環狀齒輪94及第4環狀齒輪102形成於第2環狀齒輪構件108。第2環狀齒輪構件108包含第2齒輪部108A。第2齒輪部108A共用為第3環狀齒輪94及第4環狀齒輪102。第3行星齒輪96及第4行星齒輪104形成於第2行星齒輪構件110。第2行星齒輪構件110構成所謂具階段的行星齒輪。第3載體98及第4載體106形成為一體。 [0051] 變速機構62，具備有：以支承構件56所支承的複數的傳遞體(這裡是太陽齒輪)。傳遞體，可設定為可旋轉的旋轉狀態與限制旋轉的限制狀態的任一方。複數的傳遞體包含第1傳遞體及第2傳遞體。第1變速機構62A的第1傳遞體為第1太陽齒輪72，第2傳遞體為第2太陽齒輪80。第2變速機構62B的第1傳遞體為第3太陽齒輪92，第2傳遞體為第4太陽齒輪100。 [0052] 設定機構54，用來設定輸入體58的旋轉的傳遞機構52上的變速路線S。設定機構54用來設定複數的變速路線S的其中一個。複數的變速路線S包含第1變速路線S10(第11圖)。複數的變速路線S進一步包含第2變速路線S20(第12圖)。傳遞機構52，進一步形成有：不使輸入體58的旋轉變速而輸出到輸出體60的無變速路線S0(第10圖)。 [0053] 如第3圖所示，設定機構54包含：第1設定構件112、第2設定構件114、第3設定構件116、第4設定構件118、控制構件120、套筒122、第1切換部124、及第2切換部126。在該實施方式，第1設定構件112、第2設定構件114、第3設定構件116、及第4設定構件118，分別為爪構件，配置在支承構件56周圍且可卡合於傳遞體也就是太陽齒輪的內周部。也就是設定機構54，包含爪構件，該爪構件配置在支承構件56周圍且可卡合於傳遞體的內周部。 [0054] 第1設定構件112，將第1太陽齒輪72設定成：相對於支承構件56可旋轉的旋轉狀態、與不能旋轉的限制狀態的其中之一。第2設定構件114，將第2太陽齒輪80設定成：相對於支承構件56可旋轉的旋轉狀態、與不能旋轉的限制狀態的其中之一。第3設定構件116，將第3太陽齒輪92設定成：相對於支承構件56可旋轉的旋轉狀態、與不能旋轉的限制狀態的其中之一。第4設定構件118，將第4太陽齒輪100設定成：相對於支承構件56可旋轉的旋轉狀態、與不能旋轉的限制狀態的其中之一。 [0055] 控制構件120，設置成可繞支承構件56相對其旋轉。控制構件120，連接於旋轉體C2(參考第2圖)，旋轉體C2連接著內纜線C1的端部，而可與旋轉體C2一體地旋轉。旋轉體C2，藉由操作部44(參考第1圖)的操作而當內纜線C1移動時旋轉。因此，控制構件120也伴隨著旋轉體C2的旋轉而繞支承構件56旋轉。 [0056] 如第4圖所示，套筒122具備有：第1臂部122A、第2臂部122B、第3臂部122C、第4臂部122D、及基座部122E。各臂部122A~122D，彎曲成沿著支承構件56的周方向。基座部122E，朝支承構件56的軸方向延伸而將各臂部122A~122D連接。臂部122A~122D的數量，與設定構件112、114、116、118的數量相等。在各臂部122A~122D，在其延伸方向的端部或中間部形成傾斜面。套筒122，嵌入於控制構件120，在支承構件56周圍與控制構件120一體旋轉。 [0057] 如第5圖~第8圖所示，第1設定構件112，配置在第1傳遞體也就是第1太陽齒輪72與支承構件56之間。在第1傳遞體也就是第1太陽齒輪72的內周部，形成有可讓爪構件也就是第1設定構件112嵌入的溝部72S。爪構件也就是第1設定構件112，配置在支承構件56周圍且可卡合於第1太陽齒輪72的內周部。爪構件也就是第1設定構件112，具備有：爪部112A、及與第1臂部122A的內周面卡合的卡合部112B。當第1臂部122A繞支承構件56旋轉時，卡合部112B沿著第1臂部122A的傾斜面移動，讓第1設定構件112旋轉。爪部112A朝向第1太陽齒輪72的溝部72S(內周部的凹部)突出的狀態(第5圖的實線)，形成了第1太陽齒輪72相對於支承構件56不能旋轉的限制狀態。以下將爪部112A朝向溝部72S突出的狀態作為第1設定構件112的第1狀態。爪部112A從第1太陽齒輪72的溝部72S(內周部的凹部)脫離的狀態(第5圖的兩點鏈線)，形成了第1太陽齒輪72相對於支承構件56可旋轉的旋轉狀態。以下將爪部112A從溝部72S的內部脫離的狀態作為第1設定構件112的第2狀態。以下將第1設定構件112可形成第1狀態的第1臂部122A的位置作為可突出位置。以下將第1設定構件112可維持第2狀態的第2臂部122B的位置作為不能突出位置。在第1臂部122A在可突出位置時，第1設定構件112可採取第1狀態及第2狀態雙方。在第1臂部122A在不能突出位置時，第1設定構件112僅可採取第2狀態。如第6圖所示，在第1設定構件112為第1狀態且爪部112A與溝部72S卡合的狀態，爪構件也就是第1設定構件112，限制第1傳遞體也就是第1太陽齒輪72的第1方向A的移動。在第5圖~第8圖，雖然針對第1設定構件112與第1太陽齒輪72與第1臂部122A的關係來說明，而針對其他構件也藉由同樣構造形成太陽齒輪80、92、100的旋轉狀態與限制狀態。第2太陽齒輪80，藉由第2設定構件114及第2臂部122B形成旋轉狀態及限制狀態。第3太陽齒輪92，藉由第3設定構件116及第3臂部122C形成旋轉狀態及限制狀態。第4太陽齒輪100，藉由第4設定構件118及第4臂部122D形成旋轉狀態及限制狀態。第2臂部122B，移動於：爪構件也就是第2設定構件114可形成第1狀態的可突出位置、與爪構件也就是第2設定構件114維持第2狀態的不能突出位置之間。第3臂部122C，移動於：爪構件也就是第3設定構件116可形成第1狀態的可突出位置、與爪構件也就是第3設定構件116維持第2狀態的不能突出位置之間。第4臂部122D，移動於：爪構件也就是第4設定構件118可形成第1狀態的可突出位置、與爪構件也就是第4設定構件118維持第2狀態的不能突出位置之間。在第5圖、第6圖、及第8圖，第1設定構件112以外的設定構件的符號、及第1太陽齒輪72以外的太陽齒輪的符號顯示在括弧內，而實際其他設定構件及太陽齒輪的大小、形狀等，也可與第1設定構件112、及第1太陽齒輪72不同。 [0058] 如第7圖所示，設定機構54進一步包含彈壓構件119。彈壓構件119，分別設置在第1設定構件112、第2設定構件114、第3設定構件116、及第4設定構件118，以用來彈壓第1設定構件112、第2設定構件114、第3設定構件116、及第4設定構件118。各彈壓構件119，將朝向傳遞體也就是各太陽齒輪72、80、92、100突出的方向的力量施加於各設定構件112、114、116、118。彈壓構件119在一個例子是線圈彈簧。如第8圖所示，彈壓構件119，嵌入於朝第1設定構件112的周方向延伸的凹部112C，且繞掛於支承構件56。針對其他設定構件也同樣地設置有彈壓構件119。 [0059] 第4圖所示的設定機構54，如果第1太陽齒輪72及第2太陽齒輪80的其中一方為限制狀態的話，則控制第1設定構件112與第2設定構件114讓第1太陽齒輪72及第2太陽齒輪80的另一方為旋轉狀態。設定機構54，如果第3太陽齒輪92及第4太陽齒輪100的其中一方為限制狀態的話，則控制第3設定構件116與第4設定構件118讓第3太陽齒輪92及第4太陽齒輪100的另一方為旋轉狀態。設定機構54，藉由將套筒122的各臂部122A~122D的傾斜面設置在周方向不同位置，則使用來將各太陽齒輪72、80、92、100的旋轉狀態與限制狀態切換的控制構件120的旋轉相位不同。 [0060] 第1切換部124及第2切換部126，形成：讓輸入體58的旋轉經由第2變速機構62B的變速而輸出到輸出體60的第1狀態、與讓輸入體58的旋轉未經由第2變速機構62B的變速而輸出到輸出體60的第2狀態。 [0061] 第1切換部124包含第1單向離合器124A。第1單向離合器124A例如是滾子離合器。第1單向離合器124A，配置在第2環狀齒輪構件108與輸出體60之間。具體來說，使第2環狀齒輪構件108與第1單向離合器124A的內座圈一體化，讓輸出體60的內周部與第1單向離合器124A的外座圈一體化。第1單向離合器124A，當第2環狀齒輪構件108的旋轉速度小於輸出體60的旋轉速度時，則允許第2環狀齒輪構件108與輸出體60的相對旋轉。第1單向離合器124A，當第2環狀齒輪構件108的旋轉速度為輸出體60的旋轉速度以上時，則使第1環狀齒輪構件88與輸出體60一體旋轉。 [0062] 第2切換部126包含第2單向離合器126A。第2單向離合器126A例如是具有爪部的單向離合器。第2單向離合器126A，配置在第3載體98及第4載體106、與輸出體60之間。第2單向離合器126A，將第3載體98及第4載體106的旋轉傳遞到輸出體60，不將輸出體60的旋轉傳遞到第3載體98及第4載體106。 [0063] 在第1太陽齒輪72及第2太陽齒輪80雙方為旋轉狀態，且第3太陽齒輪92及第4太陽齒輪100雙方為旋轉狀態時，未將輸入到第1行星機構64、第2行星機構66、第3行星機構68、及第4行星機構70的旋轉增速。因此，輸入體58的旋轉，並未經由第1行星機構64、第2行星機構66、第3行星機構68、及第4行星機構70的變速，而是經由第1切換部124而輸出到輸出體60。藉由第2切換部126而允許第3載體98及第4載體106與輸出體60的相對旋轉。 [0064] 在第1太陽齒輪72及第2太陽齒輪80其中一方為旋轉狀態，且第3太陽齒輪92及第4太陽齒輪100雙方為旋轉狀態時，未將輸入到第3行星機構68、及第4行星機構70的旋轉增速。因此，輸入體58的旋轉，並未經由第3行星機構68、及第4行星機構70的變速，而是經由第1切換部124而輸出到輸出體60。藉由第2切換部126而允許第3載體98及第4載體106與輸出體60的相對旋轉。 [0065] 在第1太陽齒輪72及第2太陽齒輪80其中一方為限制狀態，且第3太陽齒輪92及第4太陽齒輪100的其中一方為限制狀態時，將輸入到第3行星機構68或第4行星機構70的旋轉增速。因此，輸入體58的旋轉，經由第3行星機構68或第4行星機構70的變速然後經由第2切換部126而輸出到輸出體60。 [0066] 傳遞機構52，至少形成有第1變速路線S10及第2變速路線S20。第1變速路線S10，至少經由第1變速機構62A的變速，將來自輸入體58的旋轉以3階段以上的變速比之中的第1變速比及第2變速比的其中一方傳遞到輸出體60。第2變速路線S20，與在第1變速路線S10所經由的變速機構62不同經由第2變速機構62B的變速，將來自輸入體58的旋轉以相較第1變速比及第2變速比更大的變速比傳遞到輸出體60。 [0067] 第1變速路線S10，包含第1行星變速路線S11及第2行星變速路線S12。第1行星變速路線S11，經由第1行星機構64的變速而未經由第2行星機構66的變速，而將來自輸入體58的旋轉以第1變速比傳遞到輸出體60。第2行星變速路線S12，未經由第1行星機構64的變速而經由第2行星機構66的變速，而將來自輸入體58的旋轉以第2變速比傳遞到輸出體60。 [0068] 設定機構54，將傳遞機構52設定成在第2變速路線S20未經由第1行星機構64的變速。第2變速路線S20，包含第3行星變速路線S21及第4行星變速路線S22。第3行星變速路線S21，經由第3行星機構68的變速而未經由第4行星機構70的變速，而將來自輸入體58的旋轉以較第2變速比更大的第3變速比傳遞到輸出體60。第4行星變速路線S22，未經由第3行星機構68的變速而經由第4行星機構70的變速，而將來自輸入體58的旋轉以較第3變速比更大的第4變速比傳遞到輸出體60。 [0069] 第1變速路線S10，至少經由第1變速機構62的變速，將來自輸入體58的旋轉以3階段以上的變速比之中的第1預定變速比傳遞到輸出體60。第2變速路線S20，經由與在第1變速路線S10所經由的變速機構62不同的變速機構62的變速，將來自輸入體58的旋轉以相較第1預定變速比更大的第2預定變速比傳遞到輸出體60。設定機構54，將傳遞機構52設定成：在第2變速路線S20經由在第1變速路線S10所經由的變速機構62的變速的情況，在與較第2預定變速比更大的變速比對應的變速路線S，經由在第1變速路線S10所經由的變速機構62的變速。 [0070] 傳遞機構52的變速路線S，包含第1路線SA及第2路線SB。第1路線SA，將來自輸入體58的旋轉經由第1傳遞體(在第1變速機構62A為第1太陽齒輪72，在第2變速機構62B為第3太陽齒輪92)變速而傳遞到輸出體60。第2路線SB，將來自輸入體58的旋轉經由第2傳遞體(在第1變速機構62A為第2太陽齒輪80，在第2變速機構62B為第4太陽齒輪100)以較第1路線SA更大一階段的變速比變速而傳遞到輸出體60。相對於第1變速機構62A，第1路線SA相當於第1行星變速路線S11，第2路線SB相當於第2行星變速路線S12。相對於第2變速機構62B，第1路線SA相當於第3行星變速路線S21，第2路線SB相當於第4行星變速路線S22。 [0071] 設定機構54，進行將變速路線S從第1路線SA設定到第2路線SB的設定動作。在設定動作，設定機構54，將第1傳遞體從限制狀態設定為旋轉狀態，且將第2傳遞體從旋轉狀態設定到限制狀態。在設定動作，設定機構54，將第2傳遞體從旋轉狀態設定為限制狀態，且將第1傳遞體從限制狀態設定到旋轉狀態。設定動作包含：對於第1變速機構62A進行的第1設定動作、及對於第2變速機構62B進行的第2設定動作。 [0072] 在第1設定動作，設定機構54，藉由第1設定構件112將第1傳遞體也就是第1太陽齒輪72從限制狀態設定為旋轉狀態，且藉由第2設定構件114將第2傳遞體也就是第2太陽齒輪80從旋轉狀態設定為限制狀態。在第1設定動作，設定機構54，藉由第2設定構件114將第2傳遞體也就是第2太陽齒輪80從旋轉狀態設定為限制狀態，且藉由第1設定構件112將第1傳遞體也就是第1太陽齒輪72從限制狀態設定為旋轉狀態。具體來說，設定機構54，藉由使第2臂部122B從可旋轉位置移動到不能旋轉位置，而以第2設定構件114將第2太陽齒輪80從旋轉狀態設定為限制狀態。具體來說，設定機構54，藉由使第1臂部122A從不能旋轉位置移動到可旋轉位置，而以第1設定構件112將第1太陽齒輪72從限制狀態設定為旋轉狀態。 [0073] 在第2設定動作，設定機構54，藉由第3設定構件116將第1傳遞體也就是第3太陽齒輪92從限制狀態設定為旋轉狀態，且藉由第4設定構件118將第2傳遞體也就是第4太陽齒輪100從旋轉狀態設定為限制狀態。在第2設定動作，設定機構54，藉由第4設定構件118將第2傳遞體也就是第4太陽齒輪100從旋轉狀態設定為限制狀態，且藉由第3設定構件116將第1傳遞體也就是第3太陽齒輪92從限制狀態設定為旋轉狀態。具體來說，設定機構54，藉由使第4臂部122D從可旋轉位置移動到不能旋轉位置，而以第4設定構件118將第4太陽齒輪100從旋轉狀態設定為限制狀態。具體來說，設定機構54，藉由使第3臂部122C從不能旋轉位置移動到可旋轉位置，而以第3設定構件116將第3太陽齒輪92從限制狀態設定為旋轉狀態。 [0074] 設定機構54，在作用於爪構件也就是第1設定構件112與第1傳遞體也就是第1太陽齒輪72之間的轉矩為預定值M以下的狀態，將第1傳遞體從限制狀態設定為旋轉狀態。預定值M較佳為15Nm。預定值M，是根據第1設定構件112的爪部112A的形狀、第1太陽齒輪72的溝部72S的形狀、及彈壓構件119的彈壓力所設定。設定機構54，在作用於爪構件也就是第3設定構件116與第1傳遞體也就是第3太陽齒輪92之間的轉矩為預定值M以下的狀態，將第1傳遞體從限制狀態設定為旋轉狀態。預定值M，是根據第3設定構件116的爪部116A的形狀、第3太陽齒輪92的溝部92S的形狀、及彈壓構件119的彈壓力所設定。 [0075] 參考第9至14圖及表1，來說明各變速檔位與傳遞機構52的構成元件的關係。 如第9圖及表1所示，在第1變速檔位，第1太陽齒輪72為旋轉狀態，第2太陽齒輪80為旋轉狀態，第3太陽齒輪92為旋轉狀態，第4太陽齒輪100為旋轉狀態。如第10圖所示，在第1變速檔位，變速路線S形成無變速路線S0。在該情況，變速比為最小變速比T0。最小變速比T0為「1」。 [0076] 如第9圖及表1所示，在第2變速檔位，第1太陽齒輪72為限制狀態，第2太陽齒輪80為旋轉狀態，第3太陽齒輪92為旋轉狀態，第4太陽齒輪100為旋轉狀態。如第11圖所示，在第2變速檔位，變速路線S形成第1增速路線S1。第1增速路線S1，經由第1變速路線S10，未經由第2變速路線S20。變速路線S，形成有只經由第1變速路線S10之中的第1行星變速路線S11的第1增速路線S1。在該情況，變速比成為較最小變速比T0更大的第1增速比T1。第1增速比T1相當於「第1預定變速比」。 [0077] 如第9圖及表1所示，在第3變速檔位，第1太陽齒輪72為限制狀態，第2太陽齒輪80為旋轉狀態，第3太陽齒輪92為限制狀態，第4太陽齒輪100為旋轉狀態。如第12圖所示，在第3變速檔位，變速路線S形成第2增速路線S2。第2增速路線S2，經由第1變速路線S10及第2變速路線S20。變速路線S，形成第2增速路線S2，該第2增速路線S2經由：第1變速路線S10之中的第1行星變速路線S11、及第2變速路線S20之中的第3行星變速路線S21。在該情況，變速比成為較第1增速比T1更大的第2增速比T2。第2增速比T2相當於「第1變速比」及「第2預定變速比」。 [0078] 如第9圖及表1所示，在第4變速檔位，第1太陽齒輪72為限制狀態，第2太陽齒輪80為旋轉狀態，第3太陽齒輪92為旋轉狀態，第4太陽齒輪100為限制狀態。如第13圖所示，在第4變速檔位，變速路線S形成第3增速路線S3。第3增速路線S3，經由第1變速路線S10及第2變速路線S20。變速路線S，形成第3增速路線S3，該第3增速路線S3經由：第1變速路線S10之中的第1行星變速路線S11、及第2變速路線S20之中的第4行星變速路線S22。在該情況，變速比成為較第2增速比T2更大的第3增速比T3。第3增速比T3相當於「第2變速比」及「較第2預定變速比更大的變速比」。 [0079] 如第9圖及表1所示，在第5變速檔位，第1太陽齒輪72為旋轉狀態，第2太陽齒輪80為限制狀態，第3太陽齒輪92為旋轉狀態，第4太陽齒輪100為限制狀態。如第14圖所示，在第5變速檔位，變速路線S形成第4增速路線S4。第4增速路線S4，經由第1變速路線S10及第2變速路線S20。變速路線S，形成第4增速路線S4，該第4增速路線S4經由：第1變速路線S10之中的第2行星變速路線S12、及第2變速路線S20之中的第4行星變速路線S22。在該情況，變速比成為較第3增速比T3更大的第4增速比T4。第4增速比T4相當於「第3變速比」及「較第2預定變速比更大的變速比」。 [0080] [表1]
[0081] 表2，顯示本實施方式的各行星機構64、66、68、70的齒輪齒數的一個例子。 [0082] [表2]
[0083] 參考第9圖、第15圖及表1針對第1實施方式的自行車用變速器50的第1作用加以說明。 第15圖的實線箭頭，是表示當使傳遞機構52的變速檔位上升時，變速路線S所經由的第1變速路線S10及第2變速路線S20的變化。傳遞機構52，當從第4變速檔位變更成第5變速檔位時，從第1行星變速路線S11變更為第2行星變速路線S12。傳遞機構52，在從第1行星變速路線S11變更成第2行星變速路線S12之後，在更大的變速檔位就不會再使用第1行星變速路線S11。傳遞機構52，當從第3變速檔位變更成第4變速檔位時，從第3行星變速路線S21變更為第4行星變速路線S22。傳遞機構52，在從第3行星變速路線S21變更成第4行星變速路線S22之後，在更大的變速檔位就不會再使用第3行星變速路線S21。 [0084] 在習知的自行車用變速器，具備有切換部，該切換部，隨著內纜線C1的移動將第1變速機構與第2變速機構連結而切換成將旋轉從第2變速機構傳遞到輸出體的狀態。在習知的自行車用變速器，在使變速比從例如第3變速比上升到第4變速比的情況，從使用第2行星齒輪機構的太陽齒輪進行變速的狀態轉往使用第1行星齒輪機構的太陽齒輪進行變速的狀態。在習知的自行車用變速器，與其同時將第1變速機構與第2變速機構連結而從將旋轉從第2變速機構傳遞到輸出體的狀態切換成將旋轉從第1變速機構傳遞到輸出體的狀態。也就是說，在使變速比從第3變速比上升到第4變速比的情況，進行：第1行星齒輪機構與第2行星齒輪機構的切換、與第1變速機構與第2變速機構的連接狀態的切換雙方。例如在第15圖，在實線箭頭所示的第2變速檔位之後，以兩點鏈線的箭頭所示的順序形成假設的第3變速檔位及假設的第4變速檔位。假設的第3變速檔位，經由第2行星變速路線S12，未經由第2變速路線S20。假設的第4變速檔位，經由第1行星變速路線S11，經由第3行星變速路線S21。因此，當從假設的第3變速檔位切換到假設的第4變速檔位時，進行從第2行星變速路線S12朝第1行星變速路線S11的切換。因此變速路線的組成複雜化。 [0085] 自行車用變速器50，從第1變速機構62A將旋轉傳遞到輸出體60的狀態、與從第1變速機構62A經由第2變速機構62B將旋轉從第2變速機構62B傳遞到輸出體60的狀態的切換，是藉由第1單向離合器124A所進行。也就是說，可並不使用內纜線C1等的來自外部的力而進行該切換。因此，與習知的自行車用變速器相比，即使在輸入到自行車用變速器50的轉矩較大的情況，變速性能也不易降低。 [0086] 如表1所示，在自行車用變速器50，將變速檔位變更時，僅將第1太陽齒輪72、第2太陽齒輪80、第3太陽齒輪92、及第4太陽齒輪100的任一個從旋轉狀態變更成限制狀態。因此，與將複數的太陽齒輪72、80、92、100從旋轉狀態變更成限制狀態的構造相比，能抑制當變更成限制狀態時的變速性能的降低。 [0087] 在自行車用變速器50，即使藉由用來輔助人力驅動力的馬達42的驅動而讓輸入到自行車用變速器50的轉矩變大的情況，能適當地抑制變速性能降低。 [0088] 參考第16圖至第19圖及表1針對第1實施方式的自行車用變速器50的第2作用加以說明。 [0089] 第16圖顯示進行從第3增速比T3(第4變速檔位)變更到第4增速比T4(第5變速檔位)的設定動作時的各構件的狀態的變化的一個例子。 時刻t11，是表示當形成第3增速比T3時，控制構件120往變速比變大的方向移動的時刻。在達到時刻t11的期間，第1臂部122A位於可突出的位置，第2臂部122B位於不能突出的位置。因此將第1設定構件112維持為第1狀態，將第1太陽齒輪72維持為限制狀態，將第2設定構件114維持為第2狀態，且將第2太陽齒輪80維持為旋轉狀態。在時刻t11，第2臂部122B從不能突出位置移動到可突出位置。因此讓第2設定構件114成為從第2狀態朝向第1狀態變化的過渡狀態。第2設定構件114，當爪部114A嵌入於旋轉的第2太陽齒輪80的溝部80S時，則從過渡狀態變化成第1狀態。 [0090] 時刻t12是表示：第2設定構件114的爪部114A嵌入於第2太陽齒輪80的溝部80S而讓第2設定構件114變化為第1狀態，且爪部114A卡合於第2太陽齒輪80的溝部80S的時刻。此時，讓第2太陽齒輪80從旋轉狀態變化為限制狀態。藉由讓第2太陽齒輪80從旋轉狀態變化為限制狀態，則變速比從第3增速比T3變化為第4增速比T4。此時，第1設定構件112雖然成為第1狀態，而在第1設定構件112的爪部112A與第1太陽齒輪72之間是沒有轉矩(驅動轉矩)作用的無負荷的狀態。 [0091] 時刻t13，表示第1臂部122A從可突出位置移動到不能突出位置的時刻。在時刻t13，第1設定構件112變化為第2狀態。此時，在第1設定構件112的爪部112A與第1太陽齒輪72之間，沒有轉矩作用，所以第1臂部122A，能使第1設定構件112順暢地變化成第2狀態。 [0092] 第17圖顯示進行從第2增速比T2(第3變速檔位)變更到第3增速比T3(第4變速檔位)的設定動作時的各構件的狀態的變化的一個例子。 時刻t21，是表示當形成第2增速比T2時，控制構件120往變速比變大的方向移動的時刻。在達到時刻t21的期間，第3臂部122C位於可突出的位置，第4臂部122D位於不能突出的位置。因此將第3設定構件116維持為第1狀態，將第3太陽齒輪92維持為限制狀態，將第4設定構件118維持為第2狀態，且將第4太陽齒輪100維持為旋轉狀態。在時刻t21，第4臂部122D從不能突出位置移動到可突出位置。因此讓第4設定構件118成為從第2狀態朝向第1狀態變化的過渡狀態。第4設定構件118，當爪部118A嵌入於旋轉的第4太陽齒輪100的溝部100S時，則從過渡狀態變化成第1狀態。 [0093] 時刻t22是表示：第4設定構件118的爪部118A嵌入於第4太陽齒輪100的溝部100S而讓第4設定構件118變化為第1狀態，且爪部118A卡合於第4太陽齒輪100的溝部100S的時刻。此時，讓第4太陽齒輪100從旋轉狀態變化為限制狀態。藉由讓第4太陽齒輪100從旋轉狀態變化為限制狀態，則變速比從第2增速比T2變化為第3增速比T3。此時，第3設定構件116雖然成為第1狀態，而在第3設定構件116的爪部116A與第3太陽齒輪92之間是沒有轉矩(驅動轉矩)作用的無負荷的狀態。 [0094] 時刻t23，表示第3臂部122C從可突出位置移動到不能突出位置的時刻。在時刻t23，第3設定構件116變化為第2狀態。此時，在第3設定構件116的爪部116A與第3太陽齒輪92之間，沒有轉矩作用，所以第3臂部122C，能使第3設定構件116順暢地變化成第2狀態。 [0095] 第18圖是顯示從形成第2設定構件114的可突出狀態起至第2設定構件114成為第1狀態的期間較第16圖更長的情況，進行從第3增速比T3變更到第4增速比T4的設定動作時的各構件的狀態的變化的一個例子。 [0096] 時刻t31顯示與第16圖的時刻t11相同的狀態。 時刻t32，是顯示在第1設定構件112為第1狀態，且第2設定構件114為過渡狀態，第1臂部122A從可突出位置移動到不能突出位置的時刻。作用於第1設定構件112的爪部112A與第1太陽齒輪72之間的轉矩，為預定值M以下，所以相較於作用於第1設定構件112的爪部112A與第1太陽齒輪72之間的轉矩大於預定值M的情況相比，能更順暢地讓第1設定構件112移動成第2狀態。在時刻t32，當第2設定構件114的爪部114A嵌入於第2太陽齒輪80的溝部80S而讓第2設定構件114變化成第1狀態時，藉由讓第2太陽齒輪80從旋轉狀態變化成限制狀態，則讓變速比從第3增速比T3變化成第4增速比T4。由於第1臂部122A從可突出位置移動至不能突出位置，所以第1太陽齒輪72從限制狀態變化成旋轉狀態。 [0097] 第19圖是顯示從形成第2設定構件114的可突出狀態起至第2設定構件114成為第1狀態的期間較第18圖更長的情況，進行從第3增速比T3變更到第4增速比T4的設定動作時的各構件的狀態的變化的一個例子。 [0098] 時刻t41顯示與第16圖的時刻t11相同的狀態。 時刻t42，是顯示在第1設定構件112為第1狀態，且第2設定構件114為過渡狀態，第1臂部122A移動到可突出位置之中的不能突出位置之前的位置的時刻。在從第1臂部122A施加於第1設定構件112的力量超過作用於第1設定構件112的爪部112A與第1太陽齒輪72之間的轉矩之前，第1臂部122A不會移動到不能突出位置。 [0099] 時刻t43是表示：第2設定構件114的爪部114A嵌入於第2太陽齒輪80的溝部80S而讓第2設定構件114變化為第1狀態的時刻。此時，讓第2太陽齒輪80從旋轉狀態變化為限制狀態。藉由讓第2太陽齒輪80變化為限制狀態，則變速比從第3增速比T3變化為第4增速比T4。此時，第1設定構件112雖然成為第1狀態，而在第1設定構件112的爪部112A與第1太陽齒輪72之間是沒有轉矩(驅動轉矩)作用的無負荷的狀態。 [0100] 時刻t44是顯示，在從第1臂部122A施加於第1設定構件112的力量超過作用於第1設定構件112的爪部112A與第1太陽齒輪72之間的轉矩，而第1臂部122A移動到不能突出位置的時刻。在時刻t43，由於形成在第1設定構件112的爪部112A與第1太陽齒輪72之間沒有轉矩作用的狀態，所以第1臂部122A能順暢地移動到不能突出位置。 [0101] 在進行從第2增速比T2變更成第3增速比T3的設定動作的情況，在時刻t21之後，即使在第4設定構件118成為第1狀態之前的期間較第17圖更長的情況，也能與第18圖及第19圖同樣適當地變更變速比。 [0102] (第2實施方式) 參考第20圖~第29圖針對第2實施方式的自行車用變速器50的傳遞機構52A加以說明。第2實施方式的傳遞機構52A，除了與第1實施方式的傳遞機構52的齒輪的齒數與套筒128的形狀不同之外，都與第1實施方式的傳遞機構52相同，所以針對與第1實施方式共通的構造，加上與第1實施方式相同的符號，省略重複的說明。 [0103] 如第20圖所示，傳遞機構52A包含有複數的變速機構162。複數的變速機構162，至少包含第1變速機構162A。複數的變速機構162，進一步包含第2變速機構162B。傳遞機構52A，以三階段以上的變速比將來自輸入體58的旋轉傳遞到輸出體60。 [0104] 複數的變速機構162，分別包含至少一個行星機構64A、66A、68A、70A。複數的變速機構162包含：第1行星機構64A及第2行星機構66A。複數的變速機構162進一步包含：第3行星機構68A及第4行星機構70A。具體來說，第1變速機構162A包含：第1行星機構64A及第2行星機構66A。第2變速機構162B包含：第3行星機構68A及第4行星機構70A。第1行星機構64A，在自行車用變速器50的軸方向配置在與輸入體58相鄰的位置。第2行星機構66A，在自行車用變速器50的軸方向配置在第1行星機構64旁邊及在輸入體58的相反側。第4行星機構70A，在自行車用變速器50的軸方向配置在第2行星機構66A旁邊及在第1行星機構64A的相反側。第3行星機構68A，在自行車用變速器50的軸方向配置在第4行星機構70旁邊及在第2行星機構66A的相反側。 [0105] 第1行星機構64A包含：第1太陽齒輪72、第1環狀齒輪74、第1行星齒輪76、及第1載體78。第2行星機構66A包含：第2太陽齒輪80、第2環狀齒輪82、第2行星齒輪84、及第2載體86。第1行星機構64A及第2行星機構66A，都將來自輸入體58的旋轉增速而輸出。 [0106] 第3行星機構68A包含：第3太陽齒輪92、第3環狀齒輪94、第3行星齒輪96、及第3載體98。第4行星機構70A包含：第4太陽齒輪100、第4環狀齒輪102、第4行星齒輪104、及第4載體106。第3行星機構68A，將來自輸入體58的旋轉增速而輸出。第4行星機構70A，將來自輸入體58的旋轉增速而輸出。 [0107] 設定機構54包含：第1設定構件112、第2設定構件114、第3設定構件116、第4設定構件118、控制構件120、套筒128、第1切換部124、及第2切換部126。 [0108] 如第21圖所示，套筒128具備有：第1臂部128A、第2臂部128B、第3臂部128C、第4臂部128D、及基座部128E。各臂部128A~128D，彎曲成沿著支承構件56的周方向。基座部128E，朝支承構件56的軸方向延伸而將各臂部128A~128D連接。臂部128A~128D的數量，與設定構件112、114、116、118的數量相等。在各臂部128A~128D，在其延伸方向的端部或中間部形成傾斜面。套筒128，嵌入於控制構件120，在支承構件56周圍與控制構件120一體旋轉。 [0109] 第1設定構件112(參考第5圖)，配置在第1太陽齒輪72與支承構件56之間。第1設定構件112，具備有：爪部112A、及與第1臂部128A的內周面卡合的卡合部112B。當第1臂部128A繞支承構件56旋轉時，卡合部112B沿著第1臂部128A的傾斜面移動，讓第1設定構件112旋轉。第2太陽齒輪80，藉由第2設定構件114及第2臂部128B形成旋轉狀態及限制狀態。第3太陽齒輪92，藉由第3設定構件116及第3臂部128C形成旋轉狀態及限制狀態。第4太陽齒輪100，藉由第4設定構件118及第4臂部128D形成旋轉狀態及限制狀態。設定機構54，藉由將套筒128的各臂部128A~128D的傾斜面設置在周方向不同位置，則使用來將各太陽齒輪72、80、92、100的旋轉狀態與限制狀態切換的控制構件120的旋轉相位不同。 [0110] 傳遞機構52A，至少形成有第1變速路線S10及第2變速路線S20。第1變速路線S10，至少經由第1變速機構162A的變速，將來自輸入體58的旋轉以3階段以上的變速比之中的第1變速比及第2變速比的其中一方傳遞到輸出體60。第2變速路線S20，與在第1變速路線S10所經由的變速機構162不同經由第2變速機構162B的變速，將來自輸入體58的旋轉以相較第1變速比及第2變速比更大的變速比傳遞到輸出體60。第4行星變速路線S22，未經由第3行星機構68A的變速而經由第4行星機構70A的變速，而將來自輸入體58的旋轉以較第3變速比更大的第4變速比傳遞到輸出體60。設定機構54，將變速路線S設定成：在與較第4變速比更大的變速比對應的變速路線S未經由第3行星機構68A的變速。 [0111] 第1變速路線S10，包含第1行星變速路線S11及第2行星變速路線S12。第1行星變速路線S11，經由第1行星機構64A的變速而未經由第2行星機構66A的變速，而將來自輸入體58的旋轉以第1變速比傳遞到輸出體60。第2行星變速路線S12，未經由第1行星機構64A的變速而經由第2行星機構66A的變速，而將來自輸入體58的旋轉以第2變速比傳遞到輸出體60。 [0112] 設定機構54，將傳遞機構52A設定成在第2變速路線S20未經由第1行星機構64A的變速。第2變速路線S20，包含第3行星變速路線S21及第4行星變速路線S22。第3行星變速路線S21，經由第3行星機構68A的變速而未經由第4行星機構70的變速，而將來自輸入體58的旋轉以較第2變速比更大的第3變速比傳遞到輸出體60。第4行星變速路線S22，未經由第3行星機構68A的變速而經由第4行星機構70A的變速，而將來自輸入體58的旋轉以較第3變速比更大的第4變速比傳遞到輸出體60。 [0113] 第1變速路線S10，至少經由一個變速機構162的變速，將來自輸入體58的旋轉以3階段以上的變速比之中的第1預定變速比傳遞到輸出體60。第2變速路線S20，經由與在第1變速路線S10所經由的變速機構162不同的變速機構162的變速，將來自輸入體58的旋轉以相較第1預定變速比更大的第2預定變速比傳遞到輸出體60。設定機構54，將傳遞機構52A設定成：在第2變速路線S20經由在第1變速路線S10所經由的變速機構162的變速的情況，在與較第2預定變速比更大的變速比對應的變速路線S，經由在第1變速路線S10所經由的變速機構162的變速。 [0114] 參考第20圖、第22至26圖及表3，來說明各變速檔位與傳遞機構52A的構成元件的關係。 如第20圖及表3所示，在第1變速檔位，第1太陽齒輪72為旋轉狀態，第2太陽齒輪80為旋轉狀態，第3太陽齒輪92為旋轉狀態，第4太陽齒輪100為旋轉狀態。如第22圖所示，在第1變速檔位，變速路線S形成無變速路線SX0。在該情況，變速比為最小變速比R0。最小變速比R0為「1」。 [0115] 如第20圖及表3所示，在第2變速檔位，第1太陽齒輪72為限制狀態，第2太陽齒輪80為旋轉狀態，第3太陽齒輪92為旋轉狀態，第4太陽齒輪100為旋轉狀態。如第23圖所示，在第2變速檔位，變速路線S形成第1增速路線SX1。第1增速路線SX1，經由第1變速路線S10，未經由第2變速路線S20。變速路線S，形成有只經由第1變速路線S10之中的第1行星變速路線S11的第1增速路線SX1。在該情況，變速比成為較「1」更大的第1增速比R1。第1增速比R1相當於「第1變速比」。 [0116] 如第20圖及表3所示，在第3變速檔位，第1太陽齒輪72為旋轉狀態，第2太陽齒輪80為限制狀態，第3太陽齒輪92為旋轉狀態，第4太陽齒輪100為旋轉狀態。如第24圖所示，在第3變速檔位，變速路線S形成第2增速路線SX2。第2增速路線SX2，經由第1變速路線S10，未經由第2變速路線S20。變速路線S，形成有經由第1變速路線S10之中的第2行星變速路線S12的第2增速路線SX2。在該情況，變速比成為較第1增速比R1更大的第2增速比R2。第2增速比R2相當於「第2變速比」及「第1預定變速比」。 [0117] 如第20圖及表3所示，在第4變速檔位，第1太陽齒輪72為旋轉狀態，第2太陽齒輪80為限制狀態，第3太陽齒輪92為限制狀態，第4太陽齒輪100為旋轉狀態。如第25圖所示，在第4變速檔位，變速路線S形成第3增速路線SX3。第3增速路線SX3，經由第1變速路線S10及第2變速路線S20。變速路線S，形成第3增速路線SX3，該第3增速路線SX3經由：第1變速路線S10之中的第2行星變速路線S12、及第2變速路線S20之中的第3行星變速路線S21。在該情況，變速比成為較第2增速比R2更大的第3增速比R3。第3增速比R3相當於「第3變速比」及「第2預定變速比」。 [0118] 如第20圖及表3所示，在第5變速檔位，第1太陽齒輪72為旋轉狀態，第2太陽齒輪80為限制狀態，第3太陽齒輪92為旋轉狀態，第4太陽齒輪100為限制狀態。如第26圖所示，在第5變速檔位，變速路線S形成第4增速路線SX4。第4增速路線SX4，經由第1變速路線S10及第2變速路線S20。變速路線S，形成第4增速路線SX4，該第4增速路線SX4經由：第1變速路線S10之中的第2行星變速路線S12、及第2變速路線S20之中的第4行星變速路線S22。在該情況，變速比成為較第3增速比R3更大的第4增速比R4。第4增速比R4相當於「第4變速比」及「較第2預定變速比更大的變速比」。 [0119] [表3]
[0120] 表4，顯示本實施方式的各行星機構64A、66A、68A、70A的齒輪齒數的一個例子。 [0121] [表4]
[0122] 參考第27圖針對第2實施方式的自行車用變速器50的第1作用加以說明。 第27圖的實線箭頭，是表示當使傳遞機構52A的變速檔位上升時，變速路線S所經由的第1變速路線S10及第2變速路線S20的變化。傳遞機構52A，當從第2變速檔位變更成第3變速檔位時，從第1行星變速路線S11變更為第2行星變速路線S12。傳遞機構52A，在從第1行星變速路線S11變更成第2行星變速路線S12之後，在更大的變速檔位就不會再使用第1行星變速路線S11。傳遞機構52A，當從第4變速檔位變更成第5變速檔位時，從第3行星變速路線S21變更為第4行星變速路線S22。傳遞機構52A，在從第3行星變速路線S21變更成第4行星變速路線S22之後，在更大的變速檔位就不會再使用第3行星變速路線S21。藉由第2實施方式的自行車用變速器50，可得到與第1實施方式同樣的效果。 [0123] 參考第28圖、第29圖及表3針對第2實施方式的自行車用變速器50的第2作用加以說明。 [0124] 第28圖顯示進行從第1增速比R1(第2變速檔位)變更到第2增速比R2(第3變速檔位)的設定動作時的各構件的狀態的變化的一個例子。 時刻t51，是表示當形成第1增速比R1時，控制構件120往變速比變大的方向移動的時刻。在達到時刻t51的期間，第1臂部122A位於可突出的位置，第2臂部122B位於不能突出的位置。因此將第1設定構件112維持為第1狀態，將第1太陽齒輪72維持為限制狀態，將第2設定構件114維持為第2狀態，且將第2太陽齒輪80維持為旋轉狀態。在時刻t51，第2臂部122B從不能突出位置移動到可突出位置。因此讓第2設定構件114成為從第2狀態朝向第1狀態變化的過渡狀態。第2設定構件114，當爪部114A嵌入於旋轉的第2太陽齒輪80的溝部80S時，則從過渡狀態變化成第1狀態。 [0125] 時刻t52是表示：第2設定構件114的爪部114A嵌入於第2太陽齒輪80的溝部80S而讓第2設定構件114變化為第1狀態，且爪部114A卡合於第2太陽齒輪80的溝部80S的時刻。此時，讓第2太陽齒輪80從旋轉狀態變化為限制狀態。藉由讓第2太陽齒輪80從旋轉狀態變化為限制狀態，則變速比從第1增速比R1變化為第2增速比R2。此時，第1設定構件112雖然成為第1狀態，而在第1設定構件112的爪部112A與第1太陽齒輪72之間是沒有轉矩(驅動轉矩)作用的無負荷的狀態。 [0126] 時刻t53，表示第1臂部122A從可突出位置移動到不能突出位置的時刻。在時刻t53，第1設定構件112變化為第2狀態。此時，在第1設定構件112的爪部112A與第1太陽齒輪72之間，沒有轉矩作用，所以第1臂部122A，能使第1設定構件112順暢地變化成第2狀態。 [0127] 第29圖顯示進行從第3增速比R3(第4變速檔位)變更到第4增速比R4(第5變速檔位)的設定動作時的各構件的狀態的變化的一個例子。 時刻t61，是表示當形成第3增速比R3時，控制構件120往變速比變大的方向移動的時刻。在達到時刻t61的期間，第3臂部122C位於可突出的位置，第4臂部122D位於不能突出的位置。因此將第3設定構件116維持為第1狀態，將第3太陽齒輪92維持為限制狀態，將第4設定構件118維持為第2狀態，且將第4太陽齒輪100維持為旋轉狀態。在時刻t61，第4臂部122D從不能突出位置移動到可突出位置。因此讓第4設定構件118成為從第2狀態朝向第1狀態變化的過渡狀態。第4設定構件118，當爪部118A嵌入於旋轉的第4太陽齒輪100的溝部100S時，則從過渡狀態變化成第1狀態。 [0128] 時刻t62是表示：第4設定構件118的爪部118A嵌入於第4太陽齒輪100的溝部100S而讓第4設定構件118變化為第1狀態，且爪部118A卡合於第4太陽齒輪100的溝部100S的時刻。此時，讓第4太陽齒輪100從旋轉狀態變化為限制狀態。藉由讓第4太陽齒輪100從旋轉狀態變化為限制狀態，則變速比從第3增速比R3變化為第4增速比R4。此時，第3設定構件116雖然成為第1狀態，而在第3設定構件116的爪部116A與第3太陽齒輪92之間是沒有轉矩(驅動轉矩)作用的無負荷的狀態。 [0129] 時刻t63，表示第3臂部122C從可突出位置移動到不能突出位置的時刻。在時刻t63，第3設定構件116變化為第2狀態。此時，在第3設定構件116的爪部116A與第3太陽齒輪92之間，沒有轉矩作用，所以第3臂部122C，能使第3設定構件116順暢地變化成第2狀態。 [0130] 在進行從第1增速比R1變更成第2增速比R2的設定動作的情況，在時刻t51之後，即使在第2設定構件114成為第1狀態之前的期間較第28圖更長的情況，也能與第1實施方式第18圖及第19圖同樣適當地變更變速比。在進行從第3增速比R3變更成第4增速比R4的設定動作的情況，在時刻t61之後，即使在第4設定構件118成為第1狀態之前的期間較第29圖更長的情況，也能與第1實施方式第18圖及第19圖同樣適當地變更變速比。 [0131] (變形例) 關於上述實施方式的說明，是本發明的自行車用變速器及具備該變速器的自行車用輔助系統所採取的型態的例子，並非意圖限制其形態。本發明的自行車用變速器及具備該變速器的自行車用輔助系統，可採取例如以下所示的上述各實施方式的變形例及未相互矛盾的至少兩個變形例組合的型態。在以下的變形例，針對與實施方式共通的部分，加上與實施方式相同的符號，省略其說明。 [0132] 第1設定構件112的爪部112A的形狀、第3設定構件116的爪部116A的形狀、第1太陽齒輪72的溝部72S的形狀、及第3太陽齒輪92的溝部92S的形狀，也可如第30圖變更。第2設定構件114的爪部114A的形狀、第4設定構件118的爪部118A的形狀、第2太陽齒輪80的溝部80S的形狀、及第4太陽齒輪100的溝部100S的形狀，也可如第31圖變更。也可如第30圖及第31圖所示，讓第1太陽齒輪72的溝部72S的數量大於第2太陽齒輪80的溝部80S的數量、及第4太陽齒輪100的溝部100S的數量。也可如第30圖及第31圖所示，讓第3太陽齒輪92的溝部92S的數量大於第4太陽齒輪100的溝部100S的數量。 [0133] 也可將各實施方式的傳遞機構52、52A變更成：將來自輸入體58的旋轉以兩階段的變速比傳遞到輸出體60的傳遞機構。在該情況也可在設定動作，將第2傳遞體從旋轉狀態設定為限制狀態之後，將第1傳遞體從限制狀態設定為旋轉狀態，藉此能適當地變更變速比。在該變形例，可將第1變速機構62A及第2變速機構62B的其中一方省略。 [0134] 各變速機構62A、62B也可包含3個以上的行星齒輪機構。在該情況，預定的太陽齒輪，是與齒數更少一階段的太陽齒輪相對的第1傳遞體，齒數更少一階段的太陽齒輪，是與預定的太陽齒輪相對的第2傳遞體。 [0135] 也可從第2變速機構62B、162B將第3行星機構68、68A及第4行星機構70、70A的其中一方省略。 [0136] 也可將行星機構64、64A、66、66A、68、68A、70、70A的至少一個變更成行星滾子機構。 也可將行星機構64、64A、66、66A、68、68A、70、70A的至少一個變更成：將來自輸入體58的旋轉減速而輸出的減速機構。 [0137] 也可在未包含馬達42的自行車10搭載自行車用變速器50。 也可將自行車用變速器50設置在曲柄軸20A周圍。在該情況，自行車用變速器50，將輸入到曲柄軸20A的旋轉變速而輸出到前旋轉體24。 [0138] 自行車10，也可設置有用來控制自行車用變速器50的控制部。例如，控制部將自行車用變速器50控制成讓踏頻成為預定的範圍來變更變速檔位。[0034] (First Embodiment) With reference to FIGS. 1 to 19, a bicycle 10 equipped with a bicycle assist system 40 of the first embodiment will be described. [0035] 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 handlebar 12B attached to the frame 12A. [0036] 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 crank shaft 20A and a crank arm 20B. The driving mechanism 14 transmits the human driving force applied to the pedal 22 to the rear wheel 18. The front rotating body 24 includes a sprocket, a pulley, or a helical gear. The rear rotating body 28 includes a sprocket, a pulley, or a helical gear. The transmission member 26 transmits 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 makes the front rotating body 24 rotate forward when the crank 20 rotates forward, and does not make the front rotating body 24 rotate backward when the crank 20 rotates backward. The front rotating body 24 may be coupled to the crankshaft 20A without using a one-way clutch. [0037] 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. [0038] The motor 42 is used to assist the human driving force. The motor 42 is supported by the frame 12A. In one example, the motor 42 is disposed 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 16A of the front wheel 16 or the axle 18A of the rear wheel 18, and transmits the torque of the motor 42 to the front wheel 16 or the rear wheel 18. [0039] The operation unit 44 is operated by human hands in order to operate the bicycle transmission 50. In one example, the operation part 44 is provided in the handlebar 12B. The operation part 44 is attached with one end of a Bourdon-type cable (not shown). By operating the operation part 44 by the user, the inner cable C1 (refer to FIG. 2) of the Bourdon-type cable is moved. The other end of the Bourdon-type cable is attached to the bicycle transmission 50. [0040] The battery unit 46 supplies electric power to the motor 42. The battery unit 46 includes a battery element 46A and a holder 46B that mounts the battery unit 46 to the frame 12A. [0041] The bicycle transmission 50 changes the gear ratio of the bicycle 10 in response to the operation of the operating unit 44. The bicycle transmission 50 includes a transmission mechanism 62. The transmission mechanism 62 is a built-in transmission. The bicycle transmission 50 includes a hub 18C. That is, as shown in FIG. 2, the bicycle transmission 50 is a built-in hub provided integrally with the hub 18C. [0042] As shown in FIG. 3, a transmission 50 for a bicycle, which is a built-in transmission hub, is provided with a transmission mechanism 52 and a setting mechanism 54. The hub 18C is used to accommodate the transmission mechanism 52 and the 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 18A of the rear wheel 18. The input body 58 and the rear rotating body 28 are provided around the supporting member 56 so as to be integrally rotatable. The output body 60 is a hub shell cover. The output body 60 is provided with a flange portion 60A for attaching the spokes 18B of the rear wheel 18. The bicycle transmission 50 shifts the rotation of the input body 58 and transmits it to the output body 60. [0043] The transmission mechanism 52 includes a plurality of speed change mechanisms 62. The plural speed change mechanisms 62 include at least a first speed change mechanism 62A. The plural speed change mechanisms 62 further include a second speed change mechanism 62B. The transmission mechanism 52 transmits the rotation from the input body 58 to the output body 60 at a speed ratio of three or more stages. The speed change mechanism 62 can change the speed of the rotation from the input body 58 and output it to the output body 60. The speed change mechanism 62 includes four or more gear positions for increasing the speed ratio step by step. The speed change mechanism 62 includes five or more gear positions for increasing the speed ratio step by step. The speed change mechanism 62 shown in FIG. 3 includes five speed shift positions. [0044] The plurality of speed change mechanisms 62 respectively include at least one planetary mechanism 64, 66, 68, 70. The plural speed change mechanisms 62 include a first planetary mechanism 64 and a second planetary mechanism 66. The plural speed change mechanisms 62 further include a third planetary mechanism 68 and a fourth planetary mechanism 70. Specifically, the first transmission 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 arranged next to the input body 58 in the axial direction of the bicycle transmission 50. The second planetary mechanism 66 is arranged beside the first planetary mechanism 64 and on the opposite side of the input body 58 in the axial direction of the bicycle transmission 50. The fourth planetary mechanism 70 is arranged beside 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 beside the fourth planetary mechanism 70 and on the opposite side of the second planetary mechanism 66 in the axial direction of the bicycle transmission 50. [0045] 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 shaft of the support member 56. The first ring gear 74 is arranged around the first sun gear 72. The first planetary gear 76 is engaged with the first sun gear 72 and can revolve relative 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 respectively rotatably supports a plurality of first planetary gears 76. The first carrier 78 is provided so as to be rotatable around the axis of the supporting member 56. The plural first planetary gears 76 respectively revolve around the first sun gear 72 in accordance with the rotation of the first carrier 78. The first carrier 78 is connected to the input body 58 and transmits rotation from the input body 58. The first planetary mechanism 64 increases the speed of the rotation from the input body 58 and outputs it. [0046] 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 shaft of the support member 56. The second ring gear 82 is arranged around the second sun gear 80. The second planetary gear 84 is engaged with the second sun gear 80 and can revolve relative 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 a plurality of second planetary gears 84, respectively. The second carrier 86 is provided so as to be rotatable around the axis of the supporting member 56. The plural second planetary gears 84 respectively revolve around the second sun gear 80 in accordance with the rotation of the second carrier 86. The second planetary mechanism 66 increases the speed of the rotation from the input body 58 and outputs it. The second carrier 86 is connected to the input body 58 and transmits rotation from the input body 58. [0047] Both the first planetary mechanism 64 and the second planetary mechanism 66 increase the speed of the rotation from the input body 58 to output. The number of teeth of the first sun gear 72 is less than the number of teeth of the second sun gear 80. The number of teeth of the first planetary gear 76 is more 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 88A is commonly used 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 in 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 formed integrally. [0048] 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 shaft of the support member 56. The third ring gear 94 is arranged around the third sun gear 92. The third planetary gear 96 is engaged with the third sun gear 92 and can revolve relative 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 rotatably supports a plurality of third planetary gears 96, respectively. The third carrier 98 is provided so as to be rotatable around the axis of the supporting member 56. The plural third planetary gears 96 respectively revolve around the third sun gear 92 in accordance with the rotation of the third carrier 98. The third carrier 98 is connected to the first ring gear member 88 and transmits rotation from the first ring gear member 88. [0049] 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 shaft of the support member 56. The fourth ring gear 102 is arranged around the fourth sun gear 100. The fourth planetary gear 104 is engaged with the fourth sun gear 100 and can revolve relative 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 rotatably supports a plurality of fourth planetary gears 104, respectively. The fourth carrier 106 is provided so as to be rotatable around the axis of the supporting member 56. The plural fourth planetary gears 104 revolve around the fourth sun gear 100 in accordance with the rotation of the fourth carrier 106, respectively. The fourth carrier 106 is connected to the first ring gear member 88 and transmits rotation from the first ring gear member 88. [0050] The third planetary mechanism 68 increases the speed of the rotation from the input body 58 and outputs it. The fourth planetary mechanism 70 increases the speed of the rotation from the input body 58 and outputs it. The number of teeth of the third sun gear 92 is less than the number of teeth of the fourth sun gear 100. The number of teeth of the third planetary gear 96 is more 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 108A is commonly used 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 formed integrally. [0051] The speed change mechanism 62 includes a plurality of transmission bodies (here, sun gears) supported by a support member 56. The transmission body can be set to either a rotatable rotation state or a restricted state that restricts rotation. The plural transfer bodies include a first transfer body and a second transfer body. The first transmission body of the first transmission mechanism 62A is the first sun gear 72, and the second transmission body is the second sun gear 80. The first transmission body of the second transmission mechanism 62B is the third sun gear 92, and the second transmission body is the fourth sun gear 100. [0052] The setting mechanism 54 is used to set the transmission path S on the transmission mechanism 52 of the rotation of the input body 58. The setting mechanism 54 is used to set one of a plurality of shifting routes S. The plural shifting paths S include the first shifting path S10 (FIG. 11). The plural shifting routes S further include a second shifting route S20 (Figure 12). The transmission mechanism 52 is further formed with a non-shifting path S0 for outputting to the output body 60 without changing the rotation of the input body 58 (FIG. 10). [0053] 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, and a first switch Section 124, and second switching section 126. In this embodiment, the first setting member 112, the second setting member 114, the third setting member 116, and the fourth setting member 118 are respectively claw members, which are arranged around the support member 56 and can be engaged with the transmitting body, that is, The inner circumference of the sun gear. That is, the setting mechanism 54 includes a claw member that is arranged around the support member 56 and can be engaged with the inner peripheral portion of the transmission body. [0054] The first setting member 112 sets the first sun gear 72 to one of a rotation state that is rotatable with respect to the support member 56 and a restricted state that cannot be rotated. The second setting member 114 sets the second sun gear 80 to one of a rotation state that is rotatable with respect to the support member 56 and a restricted state that cannot be rotated. The third setting member 116 sets the third sun gear 92 to one of a rotation state that is rotatable with respect to the support member 56 and a restricted state that cannot be rotated. The fourth setting member 118 sets the fourth sun gear 100 to one of a rotation state that is rotatable with respect to the support member 56 and a restricted state that cannot be rotated. [0055] The control member 120 is arranged to be rotatable around the supporting member 56 relative to it. The control member 120 is connected to the rotating body C2 (refer to FIG. 2). The rotating body C2 is connected to the end of the inner cable C1 and can rotate integrally with the rotating body C2. The rotating body C2 rotates when the inner cable C1 moves by the operation of the operation part 44 (refer to FIG. 1). Therefore, the control member 120 also rotates around the support member 56 in accordance with the rotation of the rotating body C2. [0056] As shown in FIG. 4, the sleeve 122 includes a first arm portion 122A, a second arm portion 122B, a third arm portion 122C, a fourth arm portion 122D, and a base portion 122E. The arm portions 122A to 122D are bent along the circumferential direction of the support member 56. The base portion 122E extends in the axial direction of the support member 56 to connect the respective arm portions 122A to 122D. The number of arms 122A to 122D is equal to the number of setting members 112, 114, 116, and 118. In each of the arm portions 122A to 122D, an inclined surface is formed at the end or the middle portion in the extending direction. The sleeve 122 is embedded in the control member 120 and rotates integrally with the control member 120 around the support member 56. [0057] As shown in FIGS. 5 to 8, the first setting member 112 is arranged between the first transmission body, that is, the first sun gear 72 and the support member 56. In the inner peripheral portion of the first transmission body, that is, the first sun gear 72, a groove portion 72S into which the claw member, that is, the first setting member 112 can be fitted, is formed. The pawl member, which is the first setting member 112, is arranged around the support member 56 and can be engaged with the inner peripheral portion of the first sun gear 72. The pawl member, which is the first setting member 112, includes a pawl portion 112A and an engaging portion 112B that engages with 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 is rotated. The state where the pawl portion 112A protrudes toward the groove portion 72S (the concave portion of the inner peripheral portion) of the first sun gear 72 (solid line in FIG. 5) forms a restricted state in which the first sun gear 72 cannot rotate with respect to the support member 56. Hereinafter, the state where the claw portion 112A protrudes toward the groove portion 72S is referred to as the first state of the first setting member 112. The state where the claw portion 112A is separated from the groove portion 72S (the recessed portion of the inner peripheral portion) of the first sun gear 72 (the two-dot chain line in FIG. 5) forms a rotational state in which the first sun gear 72 is rotatable relative to the support member 56 . Hereinafter, the state where the claw portion 112A is separated from the inside of the groove portion 72S is referred to as the second state of the first setting member 112. Hereinafter, the position where the first setting member 112 can form the first arm 122A in the first state is referred to as the protruding position. Hereinafter, the position of the second arm portion 122B where the first setting member 112 can maintain the second state is referred to as the non-protruding position. When the first arm 122A is at the protruding position, the first setting member 112 can assume both the first state and the second state. When the first arm 122A is in the incapable of protruding position, the first setting member 112 can only take the second state. As shown in Figure 6, when the first setting member 112 is in the first state and the pawl portion 112A is engaged with the groove portion 72S, the pawl member is the first setting member 112 and restricts the first transmission body, which is the first sun gear. 72 moves in the first direction A. In Figures 5 to 8, although the relationship between the first setting member 112 and the first sun gear 72 and the first arm portion 122A is described, the sun gears 80, 92, 100 are formed by the same structure for other members. The state of rotation and restriction. The second sun gear 80 is formed in a rotating state and a restricted state by the second setting member 114 and the second arm portion 122B. The third sun gear 92 is formed in a rotating state and a restricted state by the third setting member 116 and the third arm portion 122C. The fourth sun gear 100 is formed in a rotating state and a restricted state by the fourth setting member 118 and the fourth arm portion 122D. The second arm portion 122B moves between the protruding position where the claw member, that is, the second setting member 114 can form the first state, and the non-protruding position, where the claw member, that is, the second setting member 114 maintains the second state. The third arm portion 122C moves between the protruding position where the claw member, that is, the third setting member 116 can form the first state, and the non-protruding position, where the claw member, that is, the third setting member 116 maintains the second state. The fourth arm portion 122D moves between the protruding position where the claw member, which is the fourth setting member 118, can form the first state, and the non-protruding position where the claw member, which is the fourth setting member 118, maintains the second state. In Figures 5, 6, and 8, the symbols of the setting members other than the first setting member 112 and the symbols of the sun gear other than the first sun gear 72 are displayed in parentheses, while the actual other setting members and the sun The size and shape of the gear may be different from the first setting member 112 and the first sun gear 72. [0058] As shown in FIG. 7, the setting mechanism 54 further includes an elastic member 119. The biasing member 119 is provided on the first setting member 112, the second setting member 114, the third setting member 116, and the fourth setting member 118, respectively, for biasing the first setting member 112, the second setting member 114, and the third setting member. The setting member 116 and the fourth setting member 118. Each biasing member 119 applies a force toward each setting member 112, 114, 116, 118 toward the transmitting body, that is, the direction in which each sun gear 72, 80, 92, 100 protrudes. The elastic member 119 is a coil spring in one example. As shown in FIG. 8, the biasing member 119 is fitted into the recess 112C extending in the circumferential direction of the first setting member 112 and is hung around the support member 56. The biasing member 119 is similarly provided for other setting members. [0059] The setting mechanism 54 shown in FIG. 4 controls the first setting member 112 and the second setting member 114 to allow the first sun gear 72 and the second sun gear 80 to be in a restricted state. The other of the gear 72 and the second sun gear 80 is in a rotating state. The setting mechanism 54 controls the third setting member 116 and the fourth setting member 118 to make the third sun gear 92 and the fourth sun gear 100 if one of the third sun gear 92 and the fourth sun gear 100 is in the restricted state. The other side is in a rotating state. The setting mechanism 54 is used to switch the rotation state and the restriction state of the sun gears 72, 80, 92, 100 by setting the inclined surfaces of the arms 122A to 122D of the sleeve 122 at different positions in the circumferential direction. The rotation phase of the member 120 is different. [0060] The first switching unit 124 and the second switching unit 126 form a first state in which the rotation of the input body 58 is output to the output body 60 via the speed change of the second speed change mechanism 62B, and the rotation of the input body 58 is not The second state of the output body 60 is output to the second state of the output body 60 through the speed change of the second speed change mechanism 62B. [0061] The 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 arranged 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 124A permits relative rotation of the second ring gear member 108 and the output body 60 when the rotation speed of the second ring gear member 108 is lower than the rotation speed of the output body 60. The first one-way clutch 124A rotates the first ring gear member 88 and the output body 60 integrally when the rotation speed of the second ring gear member 108 is equal to or higher than the rotation speed of the output body 60. [0062] The second switching unit 126 includes a second one-way clutch 126A. The second one-way clutch 126A is, for example, a one-way clutch having pawls. The second one-way clutch 126A is arranged between the third carrier 98 and the fourth carrier 106 and the output body 60. The second one-way clutch 126A 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. [0063] When both the first sun gear 72 and the second sun gear 80 are in a rotating state, and the third sun gear 92 and the fourth sun gear 100 are both in a rotating state, the input is not input to the first planetary mechanism 64 and the second The rotation speeds of the planetary mechanism 66, the third planetary mechanism 68, and the fourth planetary mechanism 70 are increased. Therefore, the rotation of the input body 58 is not transmitted through the first planetary mechanism 64, the second planetary mechanism 66, the third planetary mechanism 68, and the fourth planetary mechanism 70, but is output to the output through the first switching unit 124体60. The second switching part 126 allows the relative rotation of the third carrier 98 and the fourth carrier 106 and the output body 60. [0064] When one of the first sun gear 72 and the second sun gear 80 is in a rotating state, and both the third sun gear 92 and the fourth sun gear 100 are in a rotating state, the input to the third planetary mechanism 68 and The rotation speed of the fourth planetary mechanism 70 is increased. Therefore, the rotation of the input body 58 is output to the output body 60 through the first switching unit 124, not through the speed change of the third planetary mechanism 68 and the fourth planetary mechanism 70. The second switching part 126 allows the relative rotation of the third carrier 98 and the fourth carrier 106 and the output body 60. [0065] When one of the first sun gear 72 and the second sun gear 80 is in the restricted state, and one of the third sun gear 92 and the fourth sun gear 100 is in the restricted state, the input is input to the third planetary mechanism 68 or The rotation speed of the fourth planetary mechanism 70 is increased. Therefore, the rotation of the input body 58 is output to the output body 60 through the speed change of the third planetary mechanism 68 or the fourth planetary mechanism 70 and then through the second switching unit 126. [0066] The transmission mechanism 52 is formed with at least a first shift path S10 and a second shift path S20. The first speed change path S10 transmits at least the speed of the first speed change mechanism 62A, and transmits the rotation from the input body 58 to the output body 60 at one of the first speed ratio and the second speed ratio among three or more speed ratios. . The second speed change path S20 is different from the speed change mechanism 62 through the first speed change path S10. The speed change via the second speed change mechanism 62B makes the rotation from the input body 58 larger than the first speed ratio and the second speed ratio. The gear ratio of φ is transmitted to the output body 60. [0067] The first shifting route S10 includes a first planetary shifting route S11 and a second planetary shifting route S12. In the first planetary transmission path S11, the rotation of the input body 58 is transmitted to the output body 60 at the first transmission ratio without the transmission by the second planetary mechanism 66 without the transmission of the transmission through the first planetary mechanism 64. The second planetary shift path S12 transmits the rotation from the input body 58 to the output body 60 at the second gear ratio without the shift by the first planetary mechanism 64 but the shift by the second planetary mechanism 66. [0068] The setting mechanism 54 sets the transmission mechanism 52 so as not to be shifted by the first planetary mechanism 64 in the second shift path S20. The second shifting route S20 includes a third planetary shifting route S21 and a fourth planetary shifting route S22. In the third planetary shift path S21, the speed of the third planetary mechanism 68 is not changed by the fourth planetary mechanism 70, and the rotation from the input body 58 is transmitted to the output at a third speed ratio that is larger than the second speed ratio.体60. The fourth planetary transmission path S22 transmits the rotation of the input body 58 to the output via the fourth planetary mechanism 70 without the third planetary mechanism 68, but the rotation from the input body 58 is transmitted to the output at the fourth gear ratio which is larger than the third gear ratio.体60. [0069] In the first speed change path S10, the rotation from the input body 58 is transmitted to the output body 60 at a first predetermined speed ratio among three or more speed ratios through at least the speed change of the first speed change mechanism 62. The second speed change path S20 is used for speed change via a speed change mechanism 62 different from the speed change mechanism 62 passed through the first speed change path S10, and the rotation from the input body 58 is changed to a second predetermined speed greater than the first predetermined speed ratio. The ratio is passed to the output body 60. The setting mechanism 54 sets the transmission mechanism 52 such that, in the case of a speed change in the second speed change route S20 via the speed change mechanism 62 passed in the first speed change route S10, it corresponds to a speed ratio greater than the second predetermined speed ratio. The speed change path S is a speed change via the speed change mechanism 62 passed through in the first speed change path S10. [0070] The shift path S of the transmission mechanism 52 includes a first path SA and a second path SB. In the first route SA, the rotation from the input body 58 is transmitted to the output body through a first transmission body (the first sun gear 72 in the first speed change mechanism 62A, and the third sun gear 92 in the second speed change mechanism 62B). 60. In the second route SB, the rotation from the input body 58 is compared to the first route SA via the second transmission body (the second sun gear 80 in the first transmission mechanism 62A, and the fourth sun gear 100 in the second transmission mechanism 62B). The larger gear ratio is shifted and transmitted to the output body 60. With respect to the first speed change mechanism 62A, the first route SA corresponds to the first planetary speed change route S11, and the second route SB corresponds to the second planetary speed change route S12. With respect to the second speed change mechanism 62B, the first route SA corresponds to the third planetary speed change route S21, and the second route SB corresponds to the fourth planetary speed change route S22. [0071] The setting mechanism 54 performs a setting operation of setting the shifting route S from the first route SA to the second route SB. In the setting operation, the setting mechanism 54 sets the first transmitting body from the restricted state to the rotating state, and sets the second transmitting body from the rotating state to the restricted state. In the setting operation, the setting mechanism 54 sets the second transmission body from the rotation state to the restricted state, and sets the first transmission body from the restriction state to the rotation state. The setting operation includes a first setting operation performed on the first transmission mechanism 62A, and a second setting operation performed on the second transmission mechanism 62B. [0072] In the first setting operation, the setting mechanism 54 sets the first transmitting body, that is, the first sun gear 72, from the restricted state to the rotating state by the first setting member 112, and the second setting member 114 sets the The 2 transmitting body, that is, the second sun gear 80 is set from the rotating state to the restricted state. In the first setting action, the setting mechanism 54 sets the second transmission body, that is, the second sun gear 80 from the rotating state to the restricted state, by the second setting member 114, and the first transmission body is set by the first setting member 112 That is, the first sun gear 72 is set from the restricted state to the rotating state. Specifically, the setting mechanism 54 sets the second sun gear 80 from the rotating state to the restricted state by the second setting member 114 by moving the second arm 122B from the rotatable position to the non-rotatable position. Specifically, the setting mechanism 54 sets the first sun gear 72 from the restricted state to the rotating state by the first setting member 112 by moving the first arm 122A from the non-rotatable position to the rotatable position. [0073] In the second setting operation, the setting mechanism 54 sets the first transmitting body, that is, the third sun gear 92, from the restricted state to the rotating state by the third setting member 116, and the fourth setting member 118 sets the The second transmitting body, that is, the fourth sun gear 100 is set from the rotating state to the restricted state. In the second setting action, the setting mechanism 54 sets the second transmitting body, that is, the fourth sun gear 100 from the rotating state to the restricted state by the fourth setting member 118, and the third setting member 116 sets the first transmitting body That is, the third sun gear 92 is set from the restricted state to the rotating state. Specifically, the setting mechanism 54 sets the fourth sun gear 100 from the rotating state to the restricted state by the fourth setting member 118 by moving the fourth arm 122D from the rotatable position to the non-rotatable position. Specifically, the setting mechanism 54 sets the third sun gear 92 from the restricted state to the rotated state by the third setting member 116 by moving the third arm 122C from the non-rotatable position to the rotatable position. [0074] The setting mechanism 54 removes the first transmission body from the state in which the torque acting on the claw member, that is, the first setting member 112, and the first transmission body, that is, the first sun gear 72 is below a predetermined value M The restricted state is set to the rotating state. The predetermined value M is preferably 15 Nm. The predetermined value M is set based on the shape of the claw portion 112A of the first setting member 112, the shape of the groove portion 72S of the first sun gear 72, and the elastic force of the biasing member 119. The setting mechanism 54 sets the first transmission body from the restricted state when the torque acting on the claw member, that is, the third setting member 116, and the first transmission body, that is, the third sun gear 92 is below the predetermined value M In the rotating state. The predetermined value M is set based on the shape of the claw portion 116A of the third setting member 116, the shape of the groove 92S of the third sun gear 92, and the elastic force of the biasing member 119. [0075] With reference to FIGS. 9 to 14 and Table 1, the relationship between each gear position and the constituent elements of the transmission mechanism 52 will be described. As shown in Figure 9 and Table 1, in the first gear position, the first sun gear 72 is in a rotating 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 Rotating state. As shown in FIG. 10, in the first shift position, the shift path S forms a non-shift path S0. In this case, the gear ratio is the minimum gear ratio T0. The minimum gear ratio T0 is "1". [0076] As shown in Figure 9 and Table 1, in the second gear position, 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 The gear 100 is in a rotating state. As shown in FIG. 11, in the second shift position, the shift path S forms the first speed-increasing path S1. The first speed-increasing line S1 passes through the first speed-change line S10 and does not pass through the second speed-change line S20. The shifting route S is formed with a first speed-increasing route S1 that only passes through the first planetary shifting route S11 among the first shifting routes S10. In this case, the gear ratio becomes the first gear ratio T1 that is larger than the minimum gear ratio T0. The first speed increasing ratio T1 corresponds to the "first predetermined speed ratio". [0077] As shown in Figure 9 and Table 1, in the third gear position, 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 is in a restricted state. The gear 100 is in a rotating state. As shown in FIG. 12, in the third gear position, the shift path S forms a second speed-increasing path S2. The second speed increasing route S2 passes through the first speed changing route S10 and the second speed changing route S20. The shifting route S forms a second speed-increasing route S2. The second speed-increasing route S2 passes through: the first planetary shift route S11 in the first shift route S10 and the third planetary shift route in the second shift route S20 S21. In this case, the gear ratio becomes the second speed increase ratio T2 which is larger than the first speed increase ratio T1. The second speed increasing ratio T2 corresponds to the "first speed ratio" and the "second predetermined speed ratio". [0078] As shown in Figure 9 and Table 1, in the fourth gear position, 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 The gear 100 is in a restricted state. As shown in FIG. 13, in the fourth shift position, the shift path S forms a third speed-increasing path S3. The third speed increasing route S3 passes through the first speed changing route S10 and the second speed changing route S20. The shifting route S forms a third speed-increasing route S3, which passes through: the first planetary shifting route S11 in the first shifting route S10 and the fourth planetary shifting route in the second shifting route S20 S22. In this case, the gear ratio becomes the third speed increase ratio T3 which is larger than the second speed increase ratio T2. The third speed increasing ratio T3 corresponds to the "second speed ratio" and the "speed ratio greater than the second predetermined speed ratio". [0079] As shown in Figure 9 and Table 1, in the fifth gear position, the first sun gear 72 is in a rotating state, the second sun gear 80 is in a restricted state, the third sun gear 92 is in a rotating state, and the fourth sun The gear 100 is in a restricted state. As shown in FIG. 14, in the fifth gear position, the shift path S forms a fourth speed-increasing path S4. The fourth speed increasing route S4 passes through the first speed changing route S10 and the second speed changing route S20. The shifting route S forms a fourth speed-increasing route S4. The fourth speed-increasing route S4 passes through: the second planetary shift route S12 in the first shift route S10 and the fourth planetary shift route in the second shift route S20 S22. In this case, the gear ratio becomes the fourth speed increase ratio T4 which is larger than the third speed increase ratio T3. The fourth speed increasing ratio T4 corresponds to the "third speed ratio" and the "speed ratio greater than the second predetermined speed ratio". [0080] [Table 1] [0081] Table 2 shows an example of the number of gear teeth of the planetary mechanisms 64, 66, 68, and 70 of this embodiment. [0082] [表2] [0083] The first action of the bicycle transmission 50 of the first embodiment will be described with reference to FIG. 9, FIG. 15 and Table 1. The solid arrows in FIG. 15 indicate changes in the first shift path S10 and the second shift path S20 through which the shift path S passes when the shift position of the transmission mechanism 52 is raised. The transmission mechanism 52 changes from the first planetary transmission path S11 to the second planetary transmission path S12 when changing from the fourth gear position to the fifth gear position. After the transmission mechanism 52 is changed from the first planetary transmission path S11 to the second planetary transmission path S12, the first planetary transmission path S11 will no longer be used in a larger gear position. The transmission mechanism 52 changes from the third planetary transmission path S21 to the fourth planetary transmission path S22 when changing from the third gear position to the fourth gear position. After the transmission mechanism 52 is changed from the third planetary shifting route S21 to the fourth planetary shifting route S22, the third planetary shifting route S21 is no longer used in a larger shift position. [0084] The conventional bicycle transmission is provided with a switching portion that connects the first transmission mechanism and the second transmission mechanism with the movement of the inner cable C1 and switches to transmit rotation from the second transmission mechanism. To the state of the output body. In the conventional bicycle transmission, when the gear ratio is increased from, for example, the third gear ratio to the fourth gear ratio, the gear is shifted from the state of using the sun gear of the second planetary gear mechanism to the state of using the first planetary gear mechanism. The state in which the sun gear is shifting. In the conventional bicycle transmission, at the same time, the first transmission mechanism and the second transmission mechanism are connected to switch from a state in which rotation is transmitted from the second transmission mechanism to the output body to a state in which rotation is transmitted from the first transmission mechanism to the output body. state. In other words, when the gear ratio is increased from the third gear ratio to the fourth gear ratio, perform: switching between the first planetary gear mechanism and the second planetary gear mechanism, and the connection with the first gear mechanism and the second gear mechanism Both sides of the state switch. For example, in FIG. 15, after the second gear position indicated by the solid arrow, the hypothetical third gear position and the hypothetical fourth gear position are formed in the order indicated by the two-dot chain arrow. The assumed third gear position passes through the second planetary gear path S12, but not from the second gear path S20. The assumed fourth gear position passes through the first planetary transmission path S11 and the third planetary transmission path S21. Therefore, when switching from the assumed third gear position to the assumed fourth gear position, switching from the second planetary gear shift route S12 to the first planetary gear shift route S11 is performed. Therefore, the composition of the shifting route is complicated. [0085] The bicycle transmission 50 is in a state where rotation is transmitted from the first transmission mechanism 62A to the output body 60, and the rotation is transmitted from the second transmission mechanism 62B to the output body 60 from the first transmission mechanism 62A via the second transmission mechanism 62B. The switching of the state is performed by the first one-way clutch 124A. That is, the switching can be performed without using external force such as the inner cable C1. Therefore, compared with the conventional bicycle transmission, even when the torque input to the bicycle transmission 50 is large, the speed change performance is less likely to decrease. [0086] As shown in Table 1, in the bicycle transmission 50, when changing the gear position, only any of the first sun gear 72, the second sun gear 80, the third sun gear 92, and the fourth sun gear 100 are changed. One changes from the rotating state to the restricted state. Therefore, compared with a structure in which the plural sun gears 72, 80, 92, and 100 are changed from the rotating state to the restricted state, it is possible to suppress the reduction in the speed change performance when changing to the restricted state. [0087] In the bicycle transmission 50, even if the torque input to the bicycle transmission 50 is increased by the driving of the motor 42 for assisting the human driving force, it is possible to appropriately suppress the deterioration of the transmission performance. [0088] The second action of the bicycle transmission 50 of the first embodiment will be described with reference to FIGS. 16 to 19 and Table 1. [0089] FIG. 16 shows one of the changes in the state of each member when the setting action is changed from the third speed-increasing ratio T3 (4th gear position) to the fourth speed-increasing ratio T4 (5th gear position) example. Time t11 indicates the time when the control member 120 moves in the direction in which the gear ratio becomes larger when the third gear ratio T3 is formed. When the time t11 is reached, the first arm 122A is located at a position where it can be projected, and the second arm portion 122B is located at a position where it cannot be projected. Therefore, the first setting member 112 is maintained in the first state, the first sun gear 72 is maintained in the restricted state, the second setting member 114 is maintained in the second state, and the second sun gear 80 is maintained in the rotating state. At time t11, the second arm portion 122B moves from the position where it cannot be projected to the position where it can be projected. Therefore, the second setting member 114 is brought into a transitional state that changes from the second state to the first state. The second setting member 114 changes from the transient state to the first state when the claw portion 114A is fitted into the groove portion 80S of the rotating second sun gear 80. [0090] Time t12 indicates that the pawl portion 114A of the second setting member 114 is fitted into the groove portion 80S of the second sun gear 80, the second setting member 114 is changed to the first state, and the pawl portion 114A is engaged with the second sun. The time of the groove portion 80S of the gear 80. At this time, the second sun gear 80 is changed from the rotating state to the restricted state. By changing the second sun gear 80 from the rotating state to the restricted state, the gear ratio changes from the third speed increasing ratio T3 to the fourth speed increasing ratio T4. At this time, although the first setting member 112 is in the first state, a no-load state where no torque (driving torque) acts between the claw portion 112A of the first setting member 112 and the first sun gear 72 is. [0091] Time t13 indicates the time when the first arm 122A moves from the projectable position to the non-projectable position. At time t13, the first setting member 112 changes to the second state. At this time, since no torque acts between the claw portion 112A of the first setting member 112 and the first sun gear 72, the first arm portion 122A can smoothly change the first setting member 112 to the second state. [0092] FIG. 17 shows one of the changes in the state of each member when the setting operation of changing from the second speed increasing ratio T2 (the third gear position) to the third speed increasing ratio T3 (the fourth gear position) is performed example. Time t21 indicates the time when the control member 120 moves in the direction in which the speed ratio becomes larger when the second speed increase ratio T2 is formed. When the time t21 is reached, the third arm portion 122C is at a position where it can be projected, and the fourth arm portion 122D is at a position where it cannot be projected. Therefore, the third setting member 116 is maintained in the first state, the third sun gear 92 is maintained in the restricted state, the fourth setting member 118 is maintained in the second state, and the fourth sun gear 100 is maintained in the rotating state. At time t21, the fourth arm 122D is moved from the incapable of protruding position to the protruding position. Therefore, the fourth setting member 118 is brought into a transitional state from the second state to the first state. The fourth setting member 118 changes from the transient state to the first state when the claw portion 118A is fitted into the groove portion 100S of the rotating fourth sun gear 100. [0093] Time t22 indicates that the pawl portion 118A of the fourth setting member 118 is fitted into the groove portion 100S of the fourth sun gear 100, the fourth setting member 118 is changed to the first state, and the pawl portion 118A is engaged with the fourth sun. The time of the groove 100S of the gear 100. At this time, the fourth sun gear 100 is changed from the rotating state to the restricted state. By changing the fourth sun gear 100 from the rotating state to the restricted state, the gear ratio changes from the second speed increasing ratio T2 to the third speed increasing ratio T3. At this time, although the third setting member 116 is in the first state, no torque (driving torque) is applied between the claw portion 116A of the third setting member 116 and the third sun gear 92 in a no-load state. [0094] Time t23 indicates the time when the third arm 122C moves from the projectable position to the non-projectable position. At time t23, the third setting member 116 changes to the second state. At this time, since no torque acts between the claw 116A of the third setting member 116 and the third sun gear 92, the third arm 122C can smoothly change the third setting member 116 to the second state. [0095] FIG. 18 shows that the period from when the second setting member 114 is formed to the first state when the second setting member 114 becomes the first state is longer than that in FIG. 16, and the third speed increase ratio T3 is changed. An example of the change in the state of each member during the setting operation of the fourth speed increasing ratio T4. [0096] At time t31, the same state as that at time t11 in FIG. 16 is displayed. Time t32 is displayed when the first setting member 112 is in the first state, and the second setting member 114 is in the transition state, and the first arm 122A moves from the protruding position to the incapable position. The torque acting between the pawl portion 112A of the first setting member 112 and the first sun gear 72 is less than the predetermined value M, so it is compared with the pawl portion 112A acting on the first setting member 112 and the first sun gear 72 The first setting member 112 can be moved to the second state more smoothly than when the torque therebetween is greater than the predetermined value M. At time t32, when the claw portion 114A of the second setting member 114 is fitted into the groove portion 80S of the second sun gear 80 and the second setting member 114 is changed to the first state, the second sun gear 80 is changed from the rotating state In a restricted state, the gear ratio is changed from the third speed increasing ratio T3 to the fourth speed increasing ratio T4. Since the first arm 122A moves from the protruding position to the incapable position, the first sun gear 72 changes from the restricted state to the rotating state. [0097] FIG. 19 shows that the period from when the second setting member 114 is formed to the first state when the second setting member 114 becomes the first state is longer than that in FIG. 18, and the third speed increase ratio T3 is changed. An example of the change in the state of each member during the setting operation of the fourth speed increasing ratio T4. [0098] At time t41, the same state as that at time t11 in FIG. 16 is displayed. Time t42 is displayed when the first setting member 112 is in the first state and the second setting member 114 is in the transition state, and the first arm 122A has moved to a position before the non-protruding position among the protruding positions. Until the force applied to the first setting member 112 from the first arm 122A exceeds the torque acting between the claw 112A of the first setting member 112 and the first sun gear 72, the first arm 122A will not move to Cannot highlight the position. [0099] Time t43 indicates the time when the claw portion 114A of the second setting member 114 is fitted into the groove portion 80S of the second sun gear 80 and the second setting member 114 is changed to the first state. At this time, the second sun gear 80 is changed from the rotating state to the restricted state. By changing the second sun gear 80 to the restricted state, the gear ratio changes from the third speed increasing ratio T3 to the fourth speed increasing ratio T4. At this time, although the first setting member 112 is in the first state, a no-load state where no torque (driving torque) acts between the claw portion 112A of the first setting member 112 and the first sun gear 72 is. [0100] Time t44 shows that when the force applied from the first arm 122A to the first setting member 112 exceeds the torque acting between the claw 112A of the first setting member 112 and the first sun gear 72, 1 The moment when the arm 122A moves to the position where it cannot be projected. At time t43, since the state where no torque acts between the claw portion 112A of the first setting member 112 and the first sun gear 72 is formed, the first arm portion 122A can smoothly move to the non-protruding position. [0101] In the case of performing the setting operation of changing the second speed increasing ratio T2 to the third speed increasing ratio T3, after time t21, even the period before the fourth setting member 118 becomes the first state is longer than that in FIG. If it is long, the gear ratio can be changed appropriately as in Fig. 18 and Fig. 19. [0102] (Second Embodiment) The transmission mechanism 52A of the bicycle transmission 50 of the second embodiment will be described with reference to FIGS. 20 to 29. The transmission mechanism 52A of the second embodiment is the same as the transmission mechanism 52 of the first embodiment except for the difference in the number of teeth of the gears of the transmission mechanism 52 of the first embodiment and the shape of the sleeve 128. The structure common to the embodiment is denoted by the same reference numeral as that of the first embodiment, and the repeated description is omitted. [0103] As shown in FIG. 20, the transmission mechanism 52A includes a plurality of speed change mechanisms 162. The plural speed change mechanisms 162 include at least a first speed change mechanism 162A. The plural speed change mechanisms 162 further include a second speed change mechanism 162B. The transmission mechanism 52A transmits rotation from the input body 58 to the output body 60 at a speed ratio of three or more stages. [0104] The plurality of speed change mechanisms 162 respectively include at least one planetary mechanism 64A, 66A, 68A, and 70A. The plural speed change mechanisms 162 include a first planetary mechanism 64A and a second planetary mechanism 66A. The plural speed change mechanisms 162 further include a third planetary mechanism 68A and a fourth planetary mechanism 70A. Specifically, the first transmission mechanism 162A includes a first planetary mechanism 64A and a second planetary mechanism 66A. The second transmission mechanism 162B includes a third planetary mechanism 68A and a fourth planetary mechanism 70A. The first planetary mechanism 64A is arranged at a position adjacent to the input body 58 in the axial direction of the bicycle transmission 50. The second planetary mechanism 66A is arranged beside the first planetary mechanism 64 and on the opposite side of the input body 58 in the axial direction of the bicycle transmission 50. The fourth planetary mechanism 70A is arranged beside the second planetary mechanism 66A and on the opposite side of the first planetary mechanism 64A in the axial direction of the bicycle transmission 50. The third planetary mechanism 68A is arranged beside the fourth planetary mechanism 70 and on the opposite side of the second planetary mechanism 66A in the axial direction of the bicycle transmission 50. [0105] The first planetary mechanism 64A includes a first sun gear 72, a first ring gear 74, a first planetary gear 76, and a first carrier 78. The second planetary mechanism 66A includes a second sun gear 80, a second ring gear 82, a second planetary gear 84, and a second carrier 86. Both the first planetary mechanism 64A and the second planetary mechanism 66A increase the speed of the rotation from the input body 58 to output. [0106] The third planetary mechanism 68A includes a third sun gear 92, a third ring gear 94, a third planetary gear 96, and a third carrier 98. The fourth planetary mechanism 70A includes a fourth sun gear 100, a fourth ring gear 102, a fourth planetary gear 104, and a fourth carrier 106. The third planetary mechanism 68A increases the speed of the rotation from the input body 58 and outputs it. The fourth planetary mechanism 70A increases the speed of the rotation from the input body 58 and outputs it. [0107] 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 128, a first switching unit 124, and a second switching部126. [0108] As shown in FIG. 21, the sleeve 128 includes a first arm portion 128A, a second arm portion 128B, a third arm portion 128C, a fourth arm portion 128D, and a base portion 128E. The respective arm portions 128A to 128D are bent along the circumferential direction of the support member 56. The base portion 128E extends in the axial direction of the support member 56 to connect the respective arm portions 128A to 128D. The number of arms 128A to 128D is equal to the number of setting members 112, 114, 116, and 118. In each of the arm portions 128A to 128D, an inclined surface is formed at an end or a middle portion in the extending direction. The sleeve 128 is embedded in the control member 120 and rotates integrally with the control member 120 around the support member 56. [0109] The first setting member 112 (refer to FIG. 5) is arranged between the first sun gear 72 and the support member 56. The first setting member 112 includes a claw portion 112A and an engaging portion 112B that engages with the inner peripheral surface of the first arm portion 128A. When the first arm portion 128A rotates around the supporting member 56, the engaging portion 112B moves along the inclined surface of the first arm portion 128A, and the first setting member 112 is rotated. The second sun gear 80 is formed in a rotating state and a restricted state by the second setting member 114 and the second arm portion 128B. The third sun gear 92 is formed in a rotating state and a restricted state by the third setting member 116 and the third arm portion 128C. The fourth sun gear 100 is formed in a rotating state and a restricted state by the fourth setting member 118 and the fourth arm portion 128D. The setting mechanism 54 is used to switch the rotation state and the restriction state of the sun gears 72, 80, 92, 100 by setting the inclined surfaces of the arms 128A to 128D of the sleeve 128 at different positions in the circumferential direction. The rotation phase of the member 120 is different. [0110] The transmission mechanism 52A is formed with at least a first shift path S10 and a second shift path S20. The first gear shift path S10 transmits the rotation from the input body 58 to the output body 60 at one of the first gear ratio and the second gear ratio among three or more gear ratios through at least the gear shift of the first gear shift mechanism 162A. . The second speed change path S20 is different from the speed change mechanism 162 through the first speed change path S10. The speed change via the second speed change mechanism 162B makes the rotation from the input body 58 larger than the first speed ratio and the second speed ratio. The gear ratio of φ is transmitted to the output body 60. The fourth planetary gear shifting route S22 transmits the rotation from the input body 58 to the output at a fourth gear ratio that is larger than the third gear ratio without the gear shift of the fourth planetary mechanism 70A without the gear shift of the third planetary mechanism 68A.体60. The setting mechanism 54 sets the transmission path S so that the transmission path S corresponding to a transmission ratio larger than the fourth transmission ratio is not shifted by the third planetary mechanism 68A. [0111] The first shifting route S10 includes a first planetary shifting route S11 and a second planetary shifting route S12. In the first planetary transmission path S11, the rotation of the input body 58 is transmitted to the output body 60 at the first transmission ratio without the transmission of the transmission by the second planetary mechanism 66A through the transmission of the first planetary mechanism 64A. The second planetary shift path S12 transmits the rotation from the input body 58 to the output body 60 at the second speed ratio without shifting by the first planetary mechanism 64A but through the second planetary mechanism 66A. [0112] The setting mechanism 54 sets the transmission mechanism 52A so as not to be shifted by the first planetary mechanism 64A in the second shifting path S20. The second shifting route S20 includes a third planetary shifting route S21 and a fourth planetary shifting route S22. In the third planetary shifting route S21, the speed of the third planetary mechanism 68A is not shifted by the fourth planetary mechanism 70, and the rotation from the input body 58 is transmitted to the output at a third gear ratio that is larger than the second gear ratio.体60. The fourth planetary gear shifting route S22 transmits the rotation from the input body 58 to the output at a fourth gear ratio that is larger than the third gear ratio without the gear shift of the fourth planetary mechanism 70A without the gear shift of the third planetary mechanism 68A.体60. [0113] In the first speed change path S10, a speed change via at least one speed change mechanism 162 transmits the rotation from the input body 58 to the output body 60 at a first predetermined speed ratio among three or more speed ratios. The second speed change route S20 is used for speed change via the speed change mechanism 162 different from the speed change mechanism 162 passed through the first speed change route S10, and the rotation from the input body 58 is changed to a second predetermined speed greater than the first predetermined speed ratio. The ratio is passed to the output body 60. The setting mechanism 54 sets the transmission mechanism 52A such that when the transmission mechanism 162 through the first transmission path S10 is used in the second transmission path S20, the transmission mechanism is set to correspond to a transmission ratio greater than the second predetermined transmission ratio. The speed change path S is a speed change via the speed change mechanism 162 passed through the first speed change path S10. [0114] With reference to Fig. 20, Figs. 22 to 26, and Table 3, the relationship between each gear position and the constituent elements of the transmission mechanism 52A will be described. As shown in Figure 20 and Table 3, in the first gear position, the first sun gear 72 is in a rotating 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 Rotating state. As shown in FIG. 22, in the first shift position, the shift path S forms a non-shift path SX0. In this case, the gear ratio is the minimum gear ratio R0. The minimum gear ratio R0 is "1". [0115] As shown in Figure 20 and Table 3, in the second gear position, 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 is in a rotating state. The gear 100 is in a rotating state. As shown in FIG. 23, in the second shift position, the shift path S forms the first speed-increasing path SX1. The first speed-increasing line SX1 passes through the first speed-change line S10 and does not pass through the second speed-change line S20. The shifting route S is formed with a first speed-increasing route SX1 that only passes through the first planetary shifting route S11 among the first shifting routes S10. In this case, the gear ratio becomes the first speed increasing ratio R1 which is larger than "1". The first speed increasing ratio R1 corresponds to the "first speed ratio". [0116] As shown in Figure 20 and Table 3, in the third gear position, the first sun gear 72 is in a rotating state, the second sun gear 80 is in a restricted state, the third sun gear 92 is in a rotating state, and the fourth sun gear is in a rotating state. The gear 100 is in a rotating state. As shown in FIG. 24, in the third gear position, the shift path S forms a second speed-increasing path SX2. The second speed-increasing line SX2 passes through the first speed-changing route S10, but not from the second speed-changing route S20. The shifting route S is formed with a second speed-increasing route SX2 that passes through the second planetary shifting route S12 among the first shifting routes S10. In this case, the gear ratio becomes the second speed increase ratio R2 which is larger than the first speed increase ratio R1. The second speed increasing ratio R2 corresponds to the "second speed ratio" and the "first predetermined speed ratio". [0117] As shown in Figure 20 and Table 3, in the fourth gear position, the first sun gear 72 is in a rotating state, the second sun gear 80 is in a restricted state, the third sun gear 92 is in a restricted state, and the fourth sun gear is in a restricted state. The gear 100 is in a rotating state. As shown in FIG. 25, in the fourth shift position, the shift path S forms a third speed-increasing path SX3. The third speed increasing route SX3 passes through the first speed changing route S10 and the second speed changing route S20. The shifting route S forms a third speed-increasing route SX3, which passes through: the second planetary shifting route S12 in the first shifting route S10, and the third planetary shifting route in the second shifting route S20 S21. In this case, the gear ratio becomes the third speed increase ratio R3 which is larger than the second speed increase ratio R2. The third speed increasing ratio R3 corresponds to the "third speed ratio" and the "second predetermined speed ratio". [0118] As shown in Figure 20 and Table 3, in the fifth gear position, the first sun gear 72 is in a rotating state, the second sun gear 80 is in a restricted state, the third sun gear 92 is in a rotating state, and the fourth sun gear is in a rotating state. The gear 100 is in a restricted state. As shown in FIG. 26, in the fifth gear position, the shift path S forms a fourth speed increase path SX4. The fourth speed increasing route SX4 passes through the first speed changing route S10 and the second speed changing route S20. The shifting route S forms a fourth speed-increasing route SX4. The fourth speed-increasing route SX4 passes through: the second planetary shift route S12 in the first shift route S10 and the fourth planetary shift route in the second shift route S20 S22. In this case, the gear ratio becomes the fourth speed increase ratio R4 which is larger than the third speed increase ratio R3. The fourth speed increasing ratio R4 corresponds to the "fourth speed ratio" and the "speed ratio greater than the second predetermined speed ratio". [0119] [Table 3] [0120] Table 4 shows an example of the number of gear teeth of the planetary mechanisms 64A, 66A, 68A, and 70A in this embodiment. [0121] [表4] [0122] The first action of the bicycle transmission 50 of the second embodiment will be described with reference to FIG. 27. The solid arrows in FIG. 27 indicate changes in the first and second shift paths S10 and S20 through which the shift path S passes when the shift position of the transmission mechanism 52A is raised. The transmission mechanism 52A changes from the first planetary transmission path S11 to the second planetary transmission path S12 when changing from the second gear position to the third gear position. After the transmission mechanism 52A is changed from the first planetary transmission path S11 to the second planetary transmission path S12, the first planetary transmission path S11 is no longer used in a larger gear position. The transmission mechanism 52A changes from the third planetary transmission path S21 to the fourth planetary transmission path S22 when changing from the fourth gear position to the fifth gear position. After the transmission mechanism 52A is changed from the third planetary transmission path S21 to the fourth planetary transmission path S22, the third planetary transmission path S21 is no longer used in a larger gear position. With the bicycle transmission 50 of the second embodiment, the same effects as those of the first embodiment can be obtained. [0123] With reference to FIG. 28, FIG. 29, and Table 3, the second action of the bicycle transmission 50 of the second embodiment will be described. [0124] FIG. 28 shows one of the changes in the state of each member when the setting action is changed from the first speed-up ratio R1 (the second gear position) to the second speed-up ratio R2 (the third gear position) example. Time t51 indicates the time when the control member 120 moves in the direction in which the speed ratio becomes larger when the first speed increase ratio R1 is formed. When the time t51 is reached, the first arm 122A is located at a position where it can be projected, and the second arm portion 122B is located at a position where it cannot be projected. Therefore, the first setting member 112 is maintained in the first state, the first sun gear 72 is maintained in the restricted state, the second setting member 114 is maintained in the second state, and the second sun gear 80 is maintained in the rotating state. At time t51, the second arm portion 122B moves from the incapable position to the protruding position. Therefore, the second setting member 114 is brought into a transitional state that changes from the second state to the first state. The second setting member 114 changes from the transient state to the first state when the claw portion 114A is fitted into the groove portion 80S of the rotating second sun gear 80. [0125] Time t52 indicates that the pawl portion 114A of the second setting member 114 is fitted into the groove portion 80S of the second sun gear 80, the second setting member 114 is changed to the first state, and the pawl portion 114A is engaged with the second sun. The time of the groove portion 80S of the gear 80. At this time, the second sun gear 80 is changed from the rotating state to the restricted state. By changing the second sun gear 80 from the rotating state to the restricted state, the gear ratio changes from the first speed increasing ratio R1 to the second speed increasing ratio R2. At this time, although the first setting member 112 is in the first state, a no-load state where no torque (driving torque) acts between the claw portion 112A of the first setting member 112 and the first sun gear 72 is. [0126] Time t53 indicates the time when the first arm 122A moves from the projectable position to the projectable position. At time t53, the first setting member 112 changes to the second state. At this time, since no torque acts between the claw portion 112A of the first setting member 112 and the first sun gear 72, the first arm portion 122A can smoothly change the first setting member 112 to the second state. [0127] FIG. 29 shows one of the changes in the state of each member when the setting operation is performed to change from the third speed-increasing ratio R3 (the fourth gear position) to the fourth speed-increasing ratio R4 (the fifth gear position) example. Time t61 indicates the time when the control member 120 moves in the direction in which the gear ratio becomes larger when the third speed increasing ratio R3 is formed. When the time t61 is reached, the third arm portion 122C is located at a position where it can be projected, and the fourth arm portion 122D is located at a position where it cannot be projected. Therefore, the third setting member 116 is maintained in the first state, the third sun gear 92 is maintained in the restricted state, the fourth setting member 118 is maintained in the second state, and the fourth sun gear 100 is maintained in the rotating state. At time t61, the fourth arm 122D is moved from the position where it cannot be projected to the position where it can be projected. Therefore, the fourth setting member 118 is brought into a transitional state from the second state to the first state. The fourth setting member 118 changes from the transient state to the first state when the claw portion 118A is fitted into the groove portion 100S of the rotating fourth sun gear 100. [0128] Time t62 indicates that the claw portion 118A of the fourth setting member 118 is fitted into the groove portion 100S of the fourth sun gear 100, the fourth setting member 118 is changed to the first state, and the claw portion 118A is engaged with the fourth sun. The time of the groove 100S of the gear 100. At this time, the fourth sun gear 100 is changed from the rotating state to the restricted state. By changing the fourth sun gear 100 from the rotating state to the restricted state, the gear ratio changes from the third speed increasing ratio R3 to the fourth speed increasing ratio R4. At this time, although the third setting member 116 is in the first state, no torque (driving torque) is applied between the claw portion 116A of the third setting member 116 and the third sun gear 92 in a no-load state. [0129] Time t63 indicates the time when the third arm 122C moves from the projectable position to the non-projectable position. At time t63, the third setting member 116 changes to the second state. At this time, since no torque acts between the claw 116A of the third setting member 116 and the third sun gear 92, the third arm 122C can smoothly change the third setting member 116 to the second state. [0130] In the case of performing the setting operation of changing the first speed increasing ratio R1 to the second speed increasing ratio R2, after time t51, even the period before the second setting member 114 enters the first state is longer than that in FIG. 28 If it is long, the gear ratio can be appropriately changed as in the 18th and 19th figures of the first embodiment. In the case of performing the setting operation of changing the third speed increasing ratio R3 to the fourth speed increasing ratio R4, after time t61, even if the period before the fourth setting member 118 enters the first state is longer than that in Fig. 29 In the same manner as in Figs. 18 and 19 of the first embodiment, the gear ratio can also be appropriately changed. [0131] (Modifications) The description of the above-mentioned embodiment is an example of the form of the bicycle transmission of the present invention and the bicycle assist system provided with the transmission, and is not intended to limit the form. The bicycle transmission of the present invention and the bicycle auxiliary system provided with the transmission can take, for example, a combination of at least two modified examples of the above-described embodiments and at least two modified examples that are not contradictory to each other as shown below. In the following modification examples, the same reference numerals as in the embodiment are added to the parts common to the embodiment, and the description thereof is omitted. [0132] The shape of the claw portion 112A of the first setting member 112, the shape of the claw portion 116A of the third setting member 116, the shape of the groove portion 72S of the first sun gear 72, and the shape of the groove portion 92S of the third sun gear 92, It can also be changed as shown in Figure 30. The shape of the claw portion 114A of the second setting member 114, the shape of the claw portion 118A of the fourth setting member 118, the shape of the groove portion 80S of the second sun gear 80, and the shape of the groove portion 100S of the fourth sun gear 100 may also be as Figure 31 is changed. As shown in FIGS. 30 and 31, the number of grooves 72S of the first sun gear 72 may be greater than the number of grooves 80S of the second sun gear 80 and the number of grooves 100S of the fourth sun gear 100. As shown in FIGS. 30 and 31, the number of grooves 92S of the third sun gear 92 may be greater than the number of grooves 100S of the fourth sun gear 100. [0133] The transmission mechanisms 52 and 52A of the respective embodiments may be changed to a transmission mechanism that transmits the rotation from the input body 58 to the output body 60 at a two-stage gear ratio. In this case, after the setting operation is performed to set the second transmission body from the rotation state to the restricted state, the first transmission body may be set from the restricted state to the rotation state, whereby the gear ratio can be changed appropriately. In this modification, one of the first speed change mechanism 62A and the second speed change mechanism 62B may be omitted. [0134] Each speed change mechanism 62A, 62B may include three or more planetary gear mechanisms. In this case, the predetermined sun gear is the first transmitting body opposed to the sun gear having a lower number of teeth, and the sun gear having the lower number of teeth is the second transmitting body opposed to the predetermined sun gear. [0135] One of the third planetary mechanisms 68, 68A and the fourth planetary mechanisms 70, 70A may be omitted from the second transmission mechanisms 62B, 162B. [0136] At least one of the planetary mechanisms 64, 64A, 66, 66A, 68, 68A, 70, 70A may be changed to a planetary roller mechanism. At least one of the planetary mechanisms 64, 64A, 66, 66A, 68, 68A, 70, 70A may be changed to a deceleration mechanism that decelerates and outputs the rotation from the input body 58. [0137] The bicycle transmission 50 may be mounted on the bicycle 10 that does not include the motor 42. The bicycle transmission 50 may be provided around the crankshaft 20A. In this case, the bicycle transmission 50 shifts the rotation input to the crankshaft 20A and outputs it to the front rotating body 24. [0138] The bicycle 10 may be provided with a control unit for controlling the bicycle transmission 50. For example, the control unit controls the bicycle transmission 50 so that the cadence becomes a predetermined range to change the gear shift position.