1314199 九、發明說明： 【發明所屬之技術領域】 -· ^發明大致上係關於一 v型皮帶式無段變速系統，且特 _ -別是關於一用以驅動供變速系統用之可變齒輪比機構及 \ 其之滑輪可移動半部。 【先前技術】 在一 V型皮帶式無段變速系'统中，—滑輪固定半部被堅 鲁固至一旋轉軸而一滑輪移動半部被裝附至旋轉軸，以使不 能互相相對地旋轉及可在輛向方向上移動。在一被包含在 習知V型皮帶式無段變速系統中之滑輪移動半部的驅動 機構中之螺紋進給機構係如下地配置。一轴向地固定侧螺 紋部位被經由-軸承固持在__旋轉軸上且被裝附至一變 連箱外殼，以使不能旋轉及在轴向方向上移動。一轴向地 可移動側螺紋部位係與前述軸向地較側螺紋部位的外 圓周螺紋嚙合。此一軸向地可移動侧螺紋部位係經由一軸 鲁承裝附至滑輪可移動半部，以使可互相相料旋轉及不能 在軸向方向上移動。此外，一馬達經由一減速齒輪機構將 之旋轉。當馬達被啟動時，轴向地可移動側螺紋部位於旋 轉夺同時軸向地移動，以在軸向方向中移動滑輪可移動半 部（例如參照專利文件1 )。 關於則述組態’經由—與之整合的齒輪’軸向地可移動 侧螺紋部位盘在姑酿說α +士 、、、 /、在破驅動地旋轉時本身在軸向方向上移動 =減速ω輪機構的最終齒輪喷合。因而，減速齒輪機構的 :終齒輪本身必須在軸向方向中伸長，導致變速系統機構 312χρ/發明說明書(補件)/95-11/95125619 1314199 增大尺寸。 而且，在一習知技術的已知範 :與固定半部之間的距離，係由設有電動3之：㈣半 :所控制’而從動輪之可移動半部與固定、半 利文:二動::合t齒輪機構所設定(例如:照專 乾例提供複雜的聯鎖機構。 [專利文件1]專利號碼3099〇23(圖㈧。 [專利文件2 ]曰本專利公開號踩9 【發明内容】 寻開柄2咖-_93(圖6)。 (發明所欲解決之問題） 士發明之目的係提供可經由改善滑輪可移動半部之驅 動機構而減小尺寸的V型皮帶式無段變速系統。 本發明之另一目的係經由提供被一電動馬達驅動之變 速提速器給每-主動輪與從動輪，而非經由f知複雜齒輪 機構聯結主動輪與從動輪，以使簡化可變齒輪比機構之結 構。 … (解決問題之手段） 本發明已解決前述之問題，且申請專利範圍第丨項中描 述的V型皮帶式無段變速系統包括：一滑輪固定半部，其 被固定地支承在一旋轉軸上；一滑輪移動半部，其被支承 在旋轉軸上，以便面向滑輪固定半部，使可軸向地移動但 被禁止相對於旋轉軸旋轉，滑輪固定半部與滑輪移動半部 協力以夾持皮帶於其間；及一螺紋進給機構，包含：一袖 向地固定側螺紋組件，其設有一軸向地固定側螺紋部位， 發明說明書(補件)/95-11/95125619 8 1314199 被固持使得可相對地旋轉但禁止相對於旋轉轴軸向地移 動’且被電動馬達經由一減速齒輪機構驅動地旋轉；及一 軸向地移動側螺紋組件，其設有被配接至軸向地固定側螺 •.紋部位之軸向地移動側螺紋部位’被固持使得可在旋轉轴 '之轴向方向上移動，但禁止相對於變速箱外殼之旋轉；其 中螺纹進給機構之軸向地旋轉側螺紋組件被裝附至滑輪 移動半部，使得不能互相相對地軸向移動，但可互相相對 地旋轉。 在申請專利範圍第2項中描述的本發明，係在申請專利 範圍第i項的V型皮帶式無段變速系統中，軸向地移動侧 螺紋部位係經由-ϋ承構件而才皮支承在滑輪移動半部 上’使可互相相對地旋轉而不能互相相對地軸向移動.且 ，向地移動側螺紋部位與軸承構件均被提供在軸向地固 定側螺紋部位之内側。 在申請專利範圍 〜”令放明，係在曱請真 =1項的V型皮帶式無段變速系統中，減速齒輪之 二=在界定於被包含在螺紋進給機構中的軸向地 二側螺紋組件之輸人齒輪與滑輪移動半 間的間隙中。 午I丨位 本發明已解決前述問題，且在 、+、丄w τ明寻利範圍第4項中 述的本發明，係在申請專利 矛貝千 變速系統中進一步包含··— 皮▼式無 半部；一從動& 3人门 動輪，包含固定半部與移 干口丨，攸動輪，包含固定丰邱彻μ & , 、$哭/ 千與移動半部；及一蠻祙 速益’被提供給每-主動輪與從動輪；其+變速提= 1314199 二與每；主動輪與從動輪之移動半部結合的進給機 輪均互相獨3 =給機構之電動馬達，且主動輪與從動 ==範圍第5項中描述的本發明，係在申請專利 範圍苐4項的v型皮帶式無段變速系 :構=越從動輪的固定半部與移動半部而:=; 於一離合器構件。 丁 範=!3範圍第6項中描述的本發明，係在申請專利 2第4項的v型皮帶式無段變速系 構中的至少其-係包含—推力調整機構。 進、。機 A在申請專·圍第7項中描述的本發明，係在巾 耗圍第4項的V型皮帶式 包含H 推力調整機構 範圍第8項中描述的本發明係在申請專利 ㈣V型皮帶式無段變速系統中，推 包彈酱及一用以偵測該彈箸之伸長與縮回的衝3 測态，且該二滑輪均根據衝程感測器之偵測值而 ‘’ (發明效果） 在申請專利範圍第丨項的發明中，與減速絲機構的最 終齒輪喃合且被其驅動之螺紋進給機構的輸人齒輪，係 向地固㈣紋組件之齒輪a不在軸向方向上移動。因而， 可減少減速齒輪機構之最終齒輪寬度，如此可縮小 統之尺寸。 于、 依據申晴專利㈣第2項的發明，轴向地移動側螺紋部 312XP/發明說明書(補件)/95-11/95125619 1〇 1314199 位與轴承構件均被經由使㈣向地固定螺紋部位之寬产 方向Μ⑽部份裝設。㈣，經由有效地利用死角（㈣ space)，可縮小變速系統之尺寸。 依據申請專·圍第3項之發明，經由有效地利用界定 在軸向地❹件的輸人齒輪與滑輪㈣半部的 芈5L 4位之間的死角裝設減速齒輪之—。因而，可縮小變 速系統之尺寸。 依據申請專利範圍第4項之發明’可輕易獲取適用以配 置進給機構之空間 此外，可確保電動馬達之冷卻性能。 依據申請翻範圍第5項之發明，可有效地利用位於互 相對面之從動輪的H傘型部位外部表面侧上之空 間。 依據申請專利範圍帛6項之發明，可調整v型皮帶之橫 向壓力，使可改善皮帶之耐用性。 j據中請專利範圍第7項之發明1推力可被包含彈簧之 簡單結構調整’使可在任何時間中輕易地最佳化皮帶之橫 向壓力。 依據申請專利範圍第8項之發明，可輕易地依據皮帶橫 向壓力之調整量實施滑輪控制。 【實施方式】 一圖1係依據本發明之動力單元】的側視圖。此一動力單 兀被裝配在-摩托車上，且包含被固定至車輛的頂上 (overhead)四衝程循環二汽缸水冷式内燃機2、變速系統 3、後輪支承部位4及後輪，其均被以整合方式構成。變 312XP/發明說明書(補件)/95-11/95125619 1314199 速相3係被内燃機2支承以便直立地環繞一曲軸丨丨擺 動。箭頭F代表内燃機2的前方。 動力單元1的引擎2包含一曲軸箱6、汽缸體7、汽缸 頭8、汽缸頭外蓋9及被該組成件所環繞之部位。面向前 方且此极向上之汽缸體7被接合至曲軸箱6的前端。汽缸 頭8被接合至况缸體7的前端。汽缸頭外蓋9被接合至汽 缸頭8的前端。後輪軸6〇被建於後輪支承部位4中，以 自引擎傳送動力至後輪。 1圖2係在一平面上示出圖1的A-A剖面，B-B剖面及C-C 面的秩剖面展開圖。曲軸箱6由左曲軸箱6L與右曲軸 箱6R構成。曲軸11係被承載以供被左與右曲轴箱6L與 6R之個別頸軸承肌肖⑽旋轉。另一方面，汽缸内徑 12均被形成在汽缸體7中且個別部位13均被滑動地配接 進入汽缸内徑12内。連桿16具有二末端，其之一末端被 曲軸11經由曲軸銷14樞轉地支承，且其另一末端被活塞 13經由活塞銷15 _地支承。活塞13的往復運動旋轉 曲軸1卜燃燒室20被界定在汽缸頭8面向活塞13之端 面的底面上。以點火塞21的引導端面向燃燒室2〇的方 式，自汽缸頭外蓋9的頂部裝附點火塞21。 汽缸頭 形成具有進氣口及連續於燃燒室2〇之 口 mi與排氣閥均被滑動地配接進人汽缸頭8内。 氣闕開啟/關閉進氣口在燃燒室側上的開口，且 啟/關閉排氣口在燃燒室側上的開口。圖2示出右：燒 的排氣閥27。 312XP/發明說明書(補件)/95-11/95125619 12 1314199 8=外曲軸U且被承載在汽-頭 軸28上之凸輪驅動二二均被形成在凸輪 ' 29。捲％在驅動鏈輪3〇與從動鍵輪3ι ,32^^#,^28〇^^3〇^ 的右手部位，且從動鏈輪31在凸輪軸28的右手部位上。 右曲軸箱外殼33被提供在右曲轴箱6R的外側上 機％係由-被固定至右曲軸箱外殼33内部表面的^ 籲34及-被固定至曲#11以環繞定子％之轉子3 ::被提供鄰近於發電機36的從動齒輪3?係適用以承： 來自一未不於圖之起動馬達的旋轉驅動力。 變速箱外殼38_ “容納動力單幻的 $其中。變速箱外殼38係由右變速箱外殼咖、左變速 箱外殼38L、及分隔壁Μς拔_ 、 8S構成。右變速箱外殼38R係被 可移動地支承在曲軸箱&的左手與右手側上。如示於圖 5,在曲軸箱的左手側上’右變速箱外殼_被滾珠轴承 可移動地支承。一被以螺栓22裝附至左曲軸箱乩的 支承金屬39固持滾珠轴承4〇。在曲軸箱的右手侧上，右 變速箱外殼被滾動轴承42所固持之連接金屬復、 43B可移動地支承。—被裝附至右曲軸箱外蓋μ的支承 2ί '，㈣#承42 °連接金屬43A、43B被以螺栓 °。變速箱外殼外蓋23被提供在左變速箱外殼38L的 外側上。 左變速箱外殼38L與分隔壁383均個別以螺栓接合右變 312ΧΡ/發明說明書(補件)/95-11/95125619 13 1314199 :! : 38R。供變速系統3用的變速箱外殼38之後端 =係作用為後輪支承部位4。變速系統3係由V型皮; 速糸統45及機械減速齒輪單元46構成。無段變 私:②係被提供使得其之前半部被I設在左變速箱外 二二右變速箱外殼繼之間’且其之後半部被裝設在 二=*目外殼38L與分隔壁38S之間。此外，減速齒輪單 6被裝設在分隔壁挪與右變速箱外殼38R之間。 無段變速系統45的驅動軸係曲軸u。無段變速系統^ =動輪47被裝附至曲軸u之左端。主動輪以係由固 H 48與可移動半部49構成。無段變速系統託之從 動軸50係被承載以供被左變速箱外㉟胤、分隔壁咖 及右變速箱外殼識旋轉。無段變速系統45的從動輪52 係經由離心式離合器51裝附至從_ 5卜從動輪⑴系 由固定半部53與可移動半部54構成。—無端7型皮帶式 55被跨展在主動輪47與從動輪52之間，以使傳送主動 輪47的旋轉至從動輪52。當從動輪52之旋轉速率超過 預定旋轉速率時，被裝設在從動輪52與從動軸5〇之間的 離心式離合器51進入結合狀態，從動軸5〇開始旋轉。 減速齒輪單元46係由被承載在三㈣軸上的齒輪群組 成。第一軸係由右變速箱外殼38R與分隔壁38S所承載之 變速系、统45#從⑽50右半部位。第—轴形成具有縮小 直徑齒輪56於其上。第二軸係被承载用以被右變速箱外 殼38R與分隔壁38S旋轉之中間軸57。中間軸57具有被 整合地配接於其上之放大直徑齒輪58，其用以嚙合從動 312XP/發明說明書(補件)/95_11/95125619 14 1314199 轴〇之縮小直徑齒輪。此外，中間轴π形成具有鄰 近於放大直控齒輪58之縮小直徑齒輪59。第三轴係被承 載用以被刀隔壁38S、右變速箱外殼38R及被接合至連接 金屬43A的臂62所旋轉之後輪轴6G。後輪軸6G具有被 配接於其上之放大直經齒輪Η，其與中間軸^的縮小直 仫ui、輪59嚙合。以此—組態，從動軸5〇的扭矩係經由前 、’〔咸速齒輪群減少且傳送至後輪軸6〇。後輪5被整合地 緊固至後輪轴6 0。 圖3係一放大橫剖面_，描述主動輪47及其之周邊構 件被組合至曲軸u的狀態。主動輪47係由主動輪固定半 部48與主動輪移動半部49構成。曲軸^在其之左半部 位處形成具有第-縮小直徑部位lu與第二縮小直徑部 位ιΐΒ。第-縮小直徑部位11Α被界定在階級 之間，且第二縮小直徑部位UB界定在階級⑽與曲轴端 面Uc之間。第一縮小直徑部位ha形成具有一栓槽lld 於其之末端部位處，且第二縮小直徑部位UB形成具有一 栓槽11 e於其之末端部位處。 滾珠軸承63的内座圈、第一支承套筒64、及導引套筒 65均被配接至第一縮小直徑部# lu上。第二支承㈣ 66與主動輪固定半部48均被配接至第二縮小直徑部位 11B上。套筒64、65、66均由鋼鐵製成，且主動輪固定 +部48係由鋁製成。經由墊片67與一螺接入形成在曲軸 U末端中的螺紋孔内之螺栓68緊固前述組件，且被固著 使得不能在曲軸Η方向上移動。於前述組件争，導引套 312ΧΡ/發明說明書(補件)/95-11/95125619 15 1314199 =65經由被褒設在栓槽nd内侧之栓槽⑽配接至第一 ^直立11A的栓槽ud上。主動輪固定半部48設 ^一中央孔及-形成在巾央孔_之栓槽他，並經由检 曰48a配接至第二縮小直徑部位11β的栓槽⑴上。因 而，前述組件均被㈣，使得不能相對於㈣U移動。 主動輪固定半部48係與曲軸U 一起旋轉。 輪移動半部49係由面對固定半部之伞狀部位 丨及與傘狀部位49A整合形成以使環繞前述套筒.I Μ的圓筒型部位權構成。傘狀部位他係由銘合金製 成^圓筒型部位49B係由鋼鐵製成。傘狀部位49A係以柳 2 44整合地接合至圓筒型部位的凸緣部位。主動輪移動 =49的圓筒型部位伽在其之内側上形成具有一向内 出栓槽49Ba。突出栓槽他被配接至形成在導 套同65外部圓周上的外側栓槽_上。因為導引套筒 :的外，栓槽65b在軸向方向上延伸，突出栓槽的如^ ㈣軸向方向上滑動。因而’雖然不能相對於曲 軸11、旋轉’絲輪旋動半部49被保持可在軸向方向上 Ϊ接ΓΓ槽1Η、心、㈣、伽，主動輪移動半部49 承接來自曲軸Π的扭矩且與曲轴u —域轉。油 加至被包含在導引套筒65令的外侧栓槽咖之槽二： 許圓筒型部位彻的突出栓槽他平滑地滑動：； 半部圓筒型部位權在其之二末端處提供密封件69；^ 以預防油脂洩漏及塵埃進入。 用 圖4係沿圖3之線IV_IV取得的僅有轴部位（即，不包 312XP/發明說明書(補件)/95-11/95125619 1314199 放大橫剖面圖。互相喃合之曲軸11的栓 二 引套同65之内部栓槽65a均為漸開線栓槽。 ’亦互相嚙合之導5丨套筒65的外部栓槽㈣ =以均為漸開線检槽。為使空氣與油脂可與突出： 動，間隙70被界定在導引套筒的外部圓 ”移動半部圓筒型部位棚之内部圓周表面之間。 ，穿珠固持滾珠軸承63的外座圈之圓筒型形狀的 能相對地在軸向…：: 裝附曲軸11使得不 #白方向上移動。一内螺紋圓筒型構件76係 :圓2:整合地接合至滾珠軸承外座圈固持構件75的 行型1!。一内齒輪77以螺栓78接合至内螺紋圓 =構件76的外圓周凸緣76a。滾珠轴承外座圈固 :牛二内螺紋圓筒型構件76、及内齒輪77均 =紋組件79。曲轴n以滾珠轴承63承載此一内： 於^轴7 ’因此雖然不能在轴向方向上移動’其可獨立 為於 而&轉。内螺紋組件79的内齒輪7 =麦說明之變速提速器9。的第二中間齒請之= 直徑齒輪1 〇2驅動地旋轉。 n軸承72的内座圈係裝附至被包含在主動輪移動半 中之圓同型部位權的外圓周，使得不能在轴向方 持2。一外螺紋圓筒型構件80之内圓周係整合地固 蟫= 的外座圈。外螺紋圓筒型構件80的外圓周 位係唾合内螺紋圓筒型構件之内圓周螺紋部位。— 疋才件81以螺栓82緊固至形成在外螺紋圓筒型構件 312XP/發明說明書(補件)/95-U/95125619 17 1314199 80的-末端處之凸緣8〇a。外螺紋圓筒型構件8 構件W及螺栓82均被統合以構成外螺紋組件…^ :㈣81具有鎖定軸部位…、及被形 ： ，的二侧突出之突出部位_。突出二 _则。因而，當内螺紋組件79旋轉 83僅可在曲軸的軸向方向上移動而被抑制繞著曲 轉。内螺紋組件79與外螺紋組件 車疋 > 89。 干d構成—螺紋進給機構 -前停止器81。被整合地形成在鎖定構 二以便_外螺紋組件83向後位移之限制。^ '8 5以一螺栓8 6被裝附至包含在鎖定構件8工中的軸邻 位81a之後端’以便偵測外螺紋組件 8ld m 一被形成於其之軸部位外部的伸長件 d。此一伸長件81d係接觸自衝程感㈣的一末 =之=的尖梢’其係被制間測可移動㈣之目前位 偵測係經由侧被彈簧推出衡程感測器87末端 才干的位移而進行。橡膠伸縮囊環 87之近端部位被連接至右變速料殼^。。心測器 系統3的前半部之橫剖面展開圖。圖6係齒 面圖’顯示自側邊觀看時之變速系統的前半 邛。變速k速器90驅動地旋轉内螺紋組件Μ。此一提速 器9〇係由電動馬達91與減速齒輪機構92構成。電動馬 312XP/發明說明書(補件)/95·11/95125619 18 1314199 達91係根據車速、節流開口、及内燃機速率而自動地受 控旋轉。減速齒輪外殼93被緊固至右變速箱外殼38R。 此一減速齒輪外殼93係由右外殼構件93R、左外殼構件 • · 93L、及末端外殼構件93E構成’其界定一減速齒輪室94 '於其間。電動馬達91經由一裝附板95裝附至減速齒輪外 威93之右外设構件93R。一小齒輪96被形成在延伸進入 減速齒輪室94内的馬達之旋轉軸上。 與小齒輪96嚙合之放大直徑齒輪97及鄰近的縮小直徑 ⑩齒輪98均被整合地形成以構成第一中間齒輪卯。第一中 間齒輪99係被支承以供被減速齒輪外殼93經由滾珠軸承 100而旋轉。 與縮小直徑齒輪98嚙合之放大直徑齒輪1〇1及鄰近的 被配接至旋轉軸1 〇3上之縮小直徑齒輪丨〇2，整合地構成 第二中間齒輪104。第二中間齒輪1G4係被支承以供被減 速齒輪外殼93經由滾珠轴承105而旋轉。前述縮小直徑 齒輪102係嚙合較早說明之内螺紋組件79的内齒輪π f 當電動馬達91反應一控制指示而以正常方向旋轉時： 由第-與第二中間齒輪99、1〇4傳送至内螺紋組 =#轉。不能旋轉之外螺紋組件的外螺紋圓筒型構 牛80之螺紋部位，係與内螺紋圓筒型構件 口齒合。__从丄田， 心3^手' 紋部位 此m㈣μ的職部位承接來 筒型構件76之螺紋部位的以曲軸之軸：螺紋圓 力。因而’外螺紋組件83在曲軸的軸向1 ::推 被外螺紋圓筒型構件8。㈣紋部位承接之推力==珠 312Xp^mmmm/95-W95125619 19 1314199 軸承72被傳送至主動輪移動半部w 方向上移動。此-運動減少在移動半部、4 的軸向 半部48之間的距離， /、動輪固定 帶。〜知“ 因而在外圓周方向上位移V型* 據與前述相反之過向方向旋轉時’依 日久&幻私，在主動輪固定半部48盥 動半部49之間的距離被增加 -動輪移 皮帶。 以因而朝向中心位移¥型 圖:係艾速系統3的後半部之橫剖面 52係由從動輪固定半部53與從動輪移動半部 ^ 部53係由銘製成之傘型部位聊與鋼鐵製=圓 间型部位53B構成。從動輪移動半部54亦由紹製成 型部位54A與鋼鐵製成的圓筒型部位54β構成。固 53的傘型部位係以螺栓147緊固至圓筒型部位末端。移 動半部54的傘型部位係經由鑄造而被整合地接合 型部位末端。 s1314199 IX. Description of the invention: [Technical field to which the invention pertains] - The invention relates generally to a v-belt type stepless transmission system, and specifically relates to a variable gear for driving a transmission system It can move half of the mechanism and its pulley. [Prior Art] In a V-belt type stepless speed change system, the pulley fixing half is fixed to a rotating shaft and a pulley moving half is attached to the rotating shaft so that they cannot be opposite each other Rotate and move in the direction of the vehicle. The thread feed mechanism in a drive mechanism included in the pulley moving half of the conventional V-belt type stepless shifting system is configured as follows. An axially fixed side thread portion is held by the - bearing on the __rotating shaft and attached to a transition case to be unable to rotate and move in the axial direction. An axially movable side threaded portion is threadedly engaged with the outer circumference of the aforementioned axially more lateral threaded portion. The axially movable side threaded portion is attached to the movable portion of the pulley via a shaft so that it can rotate relative to each other and cannot move in the axial direction. Further, a motor is rotated via a reduction gear mechanism. When the motor is activated, the axially movable side threaded portion is axially moved while being rotated to move the pulley movable half in the axial direction (for example, refer to Patent Document 1). With regard to the configuration, the "transport-integrated gear" axially movable side threaded portion of the disk is said to move in the axial direction when the crank is said to be α + ±, , / The final gear of the ω wheel mechanism is sprayed. Thus, the reduction gear mechanism: the final gear itself must be elongated in the axial direction, resulting in an increase in size of the shifting mechanism mechanism 312 χ / invention specification (supplement) / 95-11/95125619 1314199. Moreover, a known art of the prior art: the distance from the fixed half is provided by the electric motor 3: (four) half: controlled 'and the movable half of the driven wheel and fixed, half-liter: two moving ::The t-gear mechanism is set (for example, a complicated interlocking mechanism is provided according to a special case. [Patent Document 1] Patent No. 3099〇23 (Fig. 8) [Patent Document 2] 曰本专利发布号 step 9 [Invention Contents] Looking for the handle 2 coffee - _93 (Fig. 6). (Problems to be solved by the invention) The purpose of the invention is to provide a V-belt type without a section that can be reduced in size by a drive mechanism that improves the movable half of the pulley. A shifting system. Another object of the present invention is to simplify the variable by providing a variable speed speed governor driven by an electric motor to each of the driving wheel and the driven wheel instead of coupling the driving wheel and the driven wheel via a complex gear mechanism. The structure of the gear ratio mechanism. (Means for Solving the Problem) The present invention has solved the aforementioned problems, and the V-belt type stepless shifting system described in the scope of the patent application includes: a pulley fixing half which is fixed Supported on a rotating shaft; a pulley moving half supported on the rotating shaft so as to face the pulley fixing half so as to be axially movable but prohibited from rotating relative to the rotating shaft, the pulley fixing half cooperates with the pulley moving half to clamp the belt And a thread feeding mechanism comprising: a sleeve-wise fixed side threaded component provided with an axially fixed side threaded portion, the invention specification (supplement)/95-11/95125619 8 1314199 being held such that it is relatively Rotating but not axially moving relative to the axis of rotation' and being driven to rotate by the electric motor via a reduction gear mechanism; and axially moving the side threaded assembly, which is configured to be axially fixed to the side screw The axially moving side threaded portion 'of the land portion is held so as to be movable in the axial direction of the rotating shaft', but rotation relative to the gearbox housing is prohibited; wherein the threaded feed mechanism axially rotates the side threaded assembly Attached to the pulley moving half so that they cannot move axially relative to each other, but can rotate relative to each other. The invention described in claim 2 is applied for In the V-belt type stepless speed change system of the item i, the axially moving side threaded portion is supported by the bearing member on the pulley moving half by the bearing member, so that they can rotate relative to each other without being opposite to each other. Axial movement. Moreover, the moving side thread portion and the bearing member are both provided on the inner side of the axially fixed side thread portion. In the patent application scope, the "V-type" In the belt type stepless speed change system, the second of the reduction gears is in the gap between the input gear and the pulley half defined by the axially two-sided threaded assembly included in the thread feed mechanism. The foregoing problem has been solved, and the invention described in item 4 of the +, 丄w τ, and the Scope of the Vision is further included in the patented spear-thousand-speed shifting system. Moving & 3 person door moving wheel, including fixed half and dry mouth, swaying wheel, including fixed Feng Qiuqiu μ &, , crying / thousand and moving half; and a savage speed Per-drive wheel and driven wheel; its + shifting speed = 1314199 And each of the feed wheels combined with the moving half of the driving wheel and the driven wheel are mutually independent 3 = the electric motor of the mechanism, and the invention described in the driving wheel and the driven == range item 5 is applied for Patented 苐4 item v-belt type stepless speed change system: structure = the fixed half of the driven wheel and the moving half: == a clutch member. The present invention described in the sixth aspect of the present invention is the at least one of the v-belt type stepless shifting system of claim 4, which includes the thrust adjusting mechanism. Progress. The invention described in the application No. 7 of the application A is the V-belt type including the H-thrust adjustment mechanism in the fourth item of the towel consumption, and the invention described in the eighth item is applied for a patent (four) V-belt. In the stepless speed change system, the push pack sauce and a punch 3 for detecting the elongation and retraction of the magazine, and the two pulleys are based on the detected value of the stroke sensor. [Effects] In the invention of the third aspect of the patent application, the input gear of the screw feed mechanism that is coupled with and driven by the final gear of the speed reducing wire mechanism is not in the axial direction of the gear a of the ground (four) grain assembly Move on. Therefore, the final gear width of the reduction gear mechanism can be reduced, which can reduce the size of the system. According to the invention of Shenqing Patent (4) item 2, the axially moving side threaded portion 312XP/invention specification (supplement)/95-11/95125619 1〇1314199 and the bearing member are both fixed to the ground by (4) Part of the wide production direction Μ (10) is installed. (4) By effectively utilizing the dead angle ((4) space), the size of the shifting system can be reduced. According to the invention of the third application, the reduction gear is mounted by effectively utilizing the dead angle between the input gear defined in the axial direction and the 芈5L 4 position of the half (4) of the pulley. Thus, the size of the variable speed system can be reduced. According to the invention of claim 4, the space for applying the feed mechanism can be easily obtained. In addition, the cooling performance of the electric motor can be ensured. According to the invention of claim 5, the space on the outer surface side of the H-shaped portion of the driven wheel located on the opposite side can be effectively utilized. According to the invention of Patent Application No. 6, the lateral pressure of the v-belt can be adjusted to improve the durability of the belt. According to the invention of claim 7 of the patent scope, the thrust can be adjusted by the simple structure of the spring, so that the lateral pressure of the belt can be easily optimized at any time. According to the invention of claim 8 of the patent application, the pulley control can be easily implemented in accordance with the adjustment amount of the lateral pressure of the belt. Embodiments Fig. 1 is a side view of a power unit according to the present invention. The power unit is mounted on a motorcycle and includes an overhead four-stroke cycle two-cylinder water-cooled internal combustion engine 2, a shifting system 3, a rear wheel support portion 4, and a rear wheel, both of which are fixed to the vehicle. Constructed in an integrated manner. Variable 312XP / Invention Specification (Supplement) / 95-11/95125619 1314199 The fast phase 3 system is supported by the internal combustion engine 2 so as to swing upright around a crankshaft. Arrow F represents the front of the internal combustion engine 2. The engine 2 of the power unit 1 includes a crankcase 6, a cylinder block 7, a cylinder head 8, a cylinder head outer cover 9, and a portion surrounded by the component. The cylinder block 7 facing forward and this pole upward is joined to the front end of the crankcase 6. The cylinder head 8 is engaged to the front end of the cylinder block 7. The cylinder head outer cover 9 is joined to the front end of the cylinder head 8. The rear axle 6〇 is built into the rear wheel support portion 4 to transmit power from the engine to the rear wheel. 1 is a plan view showing a cross section of the A-A section, the B-B section, and the C-C plane of FIG. 1 on a plane. The crankcase 6 is composed of a left crankcase 6L and a right crankcase 6R. The crankshaft 11 is carried for rotation by the individual neck bearing muscles (10) of the left and right crankcases 6L and 6R. On the other hand, the cylinder inner diameters 12 are all formed in the cylinder block 7 and the individual portions 13 are slidably fitted into the cylinder inner diameter 12. The link 16 has two ends, one end of which is pivotally supported by the crankshaft 11 via the crank pin 14, and the other end of which is supported by the piston 13 via the piston pin 15_. Reciprocating Rotation of the Piston 13 The crankshaft 1 is defined on the bottom surface of the cylinder head 8 facing the end face of the piston 13. The ignition plug 21 is attached from the top of the cylinder head outer cover 9 in such a manner that the leading end of the ignition plug 21 faces the combustion chamber 2''. The cylinder head is formed with an intake port and a port continuous with the combustion chamber 2, and the exhaust valve is slidably fitted into the cylinder head 8. The gas cylinder opens/closes the opening of the intake port on the combustion chamber side, and opens/closes the opening of the exhaust port on the combustion chamber side. Figure 2 shows the right: burned exhaust valve 27. 312XP/Invention Manual (Refill)/95-11/95125619 12 1314199 8=The outer crankshaft U and the cam drive 22 carried on the steam-head shaft 28 are both formed on the cam '29. The volume % is on the right hand portion of the drive sprocket 3 〇 and the driven key wheel 3 ι , 32 ^ ^ #, ^ 28 〇 ^ ^ 3 〇 ^, and the driven sprocket 31 is on the right hand portion of the cam shaft 28. The right crankcase casing 33 is provided on the outer side of the right crankcase 6R, and is fixed to the inner surface of the right crankcase casing 33, and is fixed to the curved #11 to surround the rotor of the stator %: : The driven gear 3 provided adjacent to the generator 36 is adapted to: a rotational driving force from a starting motor that is not shown. The transmission case 38_ "accommodates the power single illusion. The transmission case 38 is composed of the right transmission case coffee, the left transmission case 38L, and the partition wall _, 8S. The right transmission case 38R is movable Supported on the left and right hand sides of the crankcase & As shown in Fig. 5, on the left hand side of the crankcase, the 'right gearbox housing _ is movably supported by the ball bearings. One is attached to the left by bolts 22. The bearing metal 39 of the crankcase 固 holds the ball bearing 4 〇. On the right hand side of the crankcase, the right transmission housing is movably supported by the connecting metal, 43B held by the rolling bearing 42. - is attached to the right crankcase The support of the outer cover μ 2, 'four' # 42 ° connection metal 43A, 43B is bolted. The transmission case outer cover 23 is provided on the outer side of the left transmission case 38L. The left transmission case 38L and the partition 383 Each of them is individually bolted to the right 312 ΧΡ / invention manual (supplement) / 95-11 / 95125619 13 1314199 :! : 38R. The rear end of the gearbox housing 38 for the transmission system 3 acts as the rear wheel support portion 4. The shifting system 3 is made of V-shaped leather; The mechanical reduction gear unit 46 is constructed. There is no section change: the 2 series is provided such that the front half is set to be outside the left gearbox and the second right gearbox casing is followed by 'and the latter half is installed at two= * between the outer casing 38L and the partition wall 38S. Further, the reduction gear unit 6 is disposed between the partition wall and the right transmission case 38R. The drive shaft of the stepless transmission system 45 is a crankshaft u. The moving wheel 47 is attached to the left end of the crankshaft u. The driving wheel is composed of a fixed H 48 and a movable half 49. The driven shaft 50 of the stepless shifting system is carried by the outer gearbox 35 胤The partition wall coffee cup and the right gearbox housing are rotated. The driven wheel 52 of the stepless speed change system 45 is attached to the slave wheel via the centrifugal clutch 51. The driven wheel (1) is composed of the fixed half 53 and the movable half 54. The endless type 7 belt type 55 is spanned between the driving wheel 47 and the driven wheel 52 to rotate the transmission driving wheel 47 to the driven wheel 52. When the rotating speed of the driven wheel 52 exceeds a predetermined rotation rate, it is loaded. The centrifugal clutch 51 disposed between the driven wheel 52 and the driven shaft 5〇 enters a combined state The driven shaft 5〇 starts to rotate. The reduction gear unit 46 is composed of a gear group carried on the three (four) shaft. The first shaft is a shifting system carried by the right transmission housing 38R and the partition wall 38S, and the system 45# From the right half of (10) 50. The first shaft is formed with a reduced diameter gear 56. The second shaft is carried by an intermediate shaft 57 that is rotated by the right transmission housing 38R and the partition wall 38S. The intermediate shaft 57 has an integrated An enlarged diameter gear 58 coupled thereto for engaging a reduced diameter gear of the driven 312XP/invention specification (supplement)/95_11/95125619 14 1314199 shaft. Further, the intermediate shaft π is formed to have a reduced diameter gear 59 adjacent to the enlarged straight control gear 58. The third shaft system is loaded with the wheel shaft 6G after being rotated by the blade partition 38S, the right transmission case 38R, and the arm 62 joined to the connection metal 43A. The rear axle 6G has an enlarged straight gear Η coupled thereto, which meshes with the reduced straight ui and the wheel 59 of the intermediate shaft. With this configuration, the torque of the driven shaft 5〇 is reduced by the front, '[the salt speed gear group is reduced and transmitted to the rear wheel axle 6〇. The rear wheel 5 is integrally fastened to the rear axle 60. Fig. 3 is an enlarged cross section _ showing a state in which the driving wheel 47 and its peripheral members are combined to the crankshaft u. The driving wheel 47 is composed of a driving wheel fixing half 48 and a driving wheel moving half 49. The crankshaft ^ is formed at its left half position with a first-reduced diameter portion lu and a second reduced diameter portion ι. The first reduced diameter portion 11 is defined between the classes, and the second reduced diameter portion UB is defined between the class (10) and the crank end Uc. The first reduced diameter portion ha is formed at a portion having a pin groove 11d at its end portion, and the second reduced diameter portion UB is formed at a tip end portion thereof with a pin groove 11e. The inner race of the ball bearing 63, the first support sleeve 64, and the guide sleeve 65 are all coupled to the first reduced diameter portion #lu. The second support (four) 66 and the drive wheel fixing half 48 are both coupled to the second reduced diameter portion 11B. The sleeves 64, 65, 66 are each made of steel, and the drive wheel fixing portion 48 is made of aluminum. The aforementioned assembly is fastened via a spacer 67 and a bolt 68 that is threaded into a threaded hole formed in the U-end of the crankshaft, and is fixed so as not to be movable in the direction of the crankshaft. In the foregoing assembly, the guide sleeve 312ΧΡ/invention specification (supplement)/95-11/95125619 15 1314199=65 is coupled to the bolt groove of the first ^upright 11A via the bolt groove (10) which is disposed inside the bolt groove nd Ud. The driving wheel fixing half 48 is provided with a central hole and a pin formed in the center hole of the towel, and is coupled to the bolt groove (1) of the second reduced diameter portion 11β via the inspection 48a. Therefore, the aforementioned components are all (four), so that they cannot be moved relative to the (four) U. The drive wheel fixed half 48 is rotated with the crankshaft U. The wheel moving half 49 is formed by integrating the umbrella portion facing the fixed half and the umbrella portion 49A so as to surround the cylindrical portion of the sleeve. The umbrella-shaped part is made of Ming alloy. The cylindrical part 49B is made of steel. The umbrella portion 49A is integrally joined to the flange portion of the cylindrical portion by the willow 2 44. The cylindrical portion of the driving wheel movement = 49 is formed on the inner side thereof to have an inwardly releasing groove 49Ba. The protruding pin groove is fitted to the outer pin groove_ formed on the outer circumference of the guide sleeve 65. Because of the outer portion of the guide sleeve, the pin groove 65b extends in the axial direction, and the protruding pin groove slides in the axial direction. Thus, although it is not possible to hold the groove half turn 49 in the axial direction relative to the crankshaft 11, the rotary wheel half 49 is slidable in the axial direction, and the drive wheel moving half 49 receives the torque from the crankshaft. And with the crankshaft u-domain turn. The oil is applied to the groove 2 of the outer pin groove contained in the guide sleeve 65: the cylindrical portion is completely protruded from the slot, and it slides smoothly: the half cylindrical portion is at the end of the second portion Provide seals 69; ^ to prevent grease leakage and dust ingress. Figure 4 is a shaft-only portion taken along line IV_IV of Figure 3 (i.e., without the package 312XP / invention specification (supplement) / 95-11/95125619 1314199 enlarged cross-sectional view. The inner bolt groove 65a of the guide sleeve and the 65 is an involute bolt groove. 'The outer bolt groove of the sleeve 65 which is also in mesh with each other (4) = is the involute slot. For air and grease Prominently, the gap 70 is defined between the outer circumference of the guiding sleeve and the inner circumferential surface of the moving cylindrical portion of the cylindrical portion. The ability of the bead to hold the cylindrical shape of the outer race of the ball bearing 63 Relatively in the axial direction::: The crankshaft 11 is attached so as not to move in the white direction. An internally threaded cylindrical member 76 is: Round 2: Integratedly coupled to the row type 1 of the ball bearing outer race retaining member 75! An internal gear 77 is joined by bolts 78 to the outer circumferential flange 76a of the internal thread circle = member 76. The ball bearing outer race is secured by a cylindrical internal member 76 and an internal gear 77. The crankshaft n is carried by the ball bearing 63 in this one: the shaft 7' so that although it cannot move in the axial direction, it can be independent The internal gear 7 of the internal threaded assembly 79 = the variable speed governor 9 of the wheat description. The second intermediate tooth is required to rotate = the diameter gear 1 〇 2 is driven to rotate. The inner race of the bearing 72 is attached. The outer circumference of the circular isomorphic portion included in the moving half of the driving wheel is such that it cannot be held in the axial direction. 2. The inner circumference of an externally threaded cylindrical member 80 is integrally fixed to the outer race of the outer ring. The outer circumferential position of the threaded cylindrical member 80 is the inner circumferential threaded portion of the cylindrical member of the internal thread. The member 81 is fastened with a bolt 82 to the cylindrical member 312XP formed in the external thread (invention) ) / 95 - U / 95125619 17 1314199 80 - the flange 8 〇 a at the end. The externally threaded cylindrical member 8 member W and the bolt 82 are integrated to form the externally threaded assembly ... ^ : (4) 81 has a locking shaft portion ... And the shape of the protrusion of the two sides of the protrusion _. The protrusion _. Thus, when the internal rotation of the internal thread assembly 79 can only be moved in the axial direction of the crankshaft to be suppressed from rotating around. 79 and external thread assembly rut > 89. Dry d composition - thread feed mechanism - front stop The device 81 is integrally formed in the locking mechanism to limit the rearward displacement of the external thread assembly 83. ^ '8 5 is attached to the rear end of the shaft adjacent position 81a included in the locking member 8 by a bolt 8.6 In order to detect the externally threaded component 8ldm, an elongate member d formed on the outer portion of the shaft portion thereof. The elongate member 81d is in contact with a tip of the self-stroke feeling (4) = The current position detection of the movement (4) is performed by the displacement of the end of the balance sensor 87 by the spring being pushed out by the spring. The proximal end portion of the rubber bellows 87 is connected to the right shift housing ^. . A cross-sectional view of the front half of the hearth system 3 is shown. Fig. 6 is a front view showing the front half of the shifting system when viewed from the side. The variable speed k-speed 90 drives the internal thread assembly 驱动 to rotate. This speed increaser 9 is composed of an electric motor 91 and a reduction gear mechanism 92. Electric horse 312XP/Invention manual (supplement)/95·11/95125619 18 1314199 The 91 series is automatically controlled to rotate according to the speed of the vehicle, the throttle opening, and the speed of the internal combustion engine. The reduction gear housing 93 is fastened to the right transmission housing 38R. The reduction gear housing 93 is composed of a right outer casing member 93R, a left outer casing member ·············· The electric motor 91 is attached to the right peripheral member 93R of the reduction gear outer 93 via an attachment plate 95. A pinion 96 is formed on the rotating shaft of the motor that extends into the reduction gear chamber 94. The enlarged diameter gear 97 meshed with the pinion gear 96 and the adjacent reduced diameter 10 gear 98 are integrally formed to constitute the first intermediate gear 卯. The first intermediate gear 99 is supported for rotation by the reduction gear housing 93 via the ball bearing 100. The enlarged diameter gear 1〇1 meshing with the reduced diameter gear 98 and the adjacent reduced diameter gear 丨〇2 coupled to the rotating shaft 1 〇3 integrally constitute the second intermediate gear 104. The second intermediate gear 1G4 is supported for rotation by the reduction gear housing 93 via the ball bearing 105. The reduced diameter gear 102 is engaged with the internal gear π f of the internally threaded assembly 79 described earlier. When the electric motor 91 reacts in a normal direction in response to a control indication: is transmitted by the first and second intermediate gears 99, 1〇4 to Internal thread group = #转. The externally threaded cylindrical structure of the external threaded component cannot be rotated. The threaded portion of the cow 80 is engaged with the internally threaded cylindrical member. __From the field, the heart 3^ hand's pattern part The position of the m (four) μ is taken from the axis of the crankshaft of the cylindrical member 76: the circular force of the thread. Thus, the externally threaded member 83 pushes the externally threaded cylindrical member 8 in the axial direction of the crankshaft. (4) The thrust of the groove portion == beads 312Xp^mmmm/95-W95125619 19 1314199 The bearing 72 is transmitted to the direction of the driving wheel moving half w. This - motion reduces the distance between the moving halves, the axial half 48 of the 4, and the moving wheel strap. ~ know "therefore the displacement of the V-shape in the outer circumferential direction * according to the opposite direction of the opposite direction of rotation," the distance between the drive wheel fixing half 48 and the swaying half 49 is increased. The wheel is moved toward the center. Therefore, the cross section 52 of the rear half of the system is composed of a driven wheel fixing half 53 and a driven wheel moving half 53. The part talks is composed of a steel system = round-shaped portion 53B. The driven wheel moving half 54 is also composed of a cylindrical portion 54β made of steel and a steel portion 54A. The umbrella portion of the solid 53 is fastened with a bolt 147. It is fixed to the end of the cylindrical portion. The umbrella portion of the moving half 54 is integrally joined to the end of the joint portion by casting.
• 從動軸50係形成具有階級部位50a、50b及50C。滾珠 軸承110被提供在從動軸的外部圓周上以使鄰近於階級 部位50a，且滾動軸承lu被提供在從動軸的外部圓周上 以使鄰近於階級部位50b。固定半部53的圓筒型部位53B 係被滾珠軸承110及滾動軸承ηι所支承，用以相對於從 動軸5 0旋轉。 移動半部之圓筒型部位54B被滑動地配接至固定半部 的圓筒型部位53B之外圓周。銷112被直立地提供在固定 半部之圓筒型部位53B外圓周中的四個點處。移動半部的 31ZXP/發明說明書(補件)/95-11/95125619 20 1314199 Z =部，54B纟圓周方向的四個位置處形成具有凸輪 槽 1 1 3，每一1'； /m ^ ^ 3. μ槽U彳二向方向通過圓筒型部位54B，以相 $於軸向方向傾斜地延伸。每—銷112之頭部配接進入柄 认應的凸輪槽113内。因而，雖然被銷112所限制，從動 半部54可以互相相對之軸向方向，及依據凸輪槽 A角又的互相相對之凸輪槽圓周方向，朝向從動輪固定半 4 5 3移動。 ^圓筒型構件114被固著至從動輪移動半部54的圓筒型 雜54B之外圓周，使不能移動在轴向方向中以覆 ^部位的凸輪槽113。油脂被施加在凸輪槽113中以協助 被鎖112所限制之從動輪移動半部的滑動。此外，密封件 ::供在圓筒型構件114二末端之内側，以預防油脂由此 及滾珠轴承115的内座圈被固持在圓筒型構件114右 端的外圓周上。環槽構件116係接觸滾珠轴幻15的外座• The driven shaft 50 is formed to have class portions 50a, 50b, and 50C. The ball bearing 110 is provided on the outer circumference of the driven shaft so as to be adjacent to the class portion 50a, and the rolling bearing lu is provided on the outer circumference of the driven shaft so as to be adjacent to the class portion 50b. The cylindrical portion 53B of the fixed half portion 53 is supported by the ball bearing 110 and the rolling bearing ηι for rotation with respect to the driven shaft 50. The cylindrical portion 54B of the moving half is slidably coupled to the outer circumference of the cylindrical portion 53B of the fixed half. The pin 112 is provided upright at four points in the outer circumference of the cylindrical portion 53B of the fixed half. Moving the half of the 31ZXP / invention manual (supplement) / 95-11 / 95125619 20 1314199 Z = part, 54B 四个 in the circumferential direction at four positions formed with cam grooves 1 1 3, each 1 '; / m ^ ^ 3. The μ-groove U彳 direction passes through the cylindrical portion 54B and extends obliquely in the axial direction. The head of each pin 112 is mated into the cam groove 113 of the shank. Therefore, although limited by the pin 112, the driven half 54 can move toward the driven wheel fixing half 4 5 3 in the axial direction opposite to each other and in the circumferential direction of the cam groove which is opposed to each other in accordance with the cam groove A angle. The cylindrical member 114 is fixed to the outer circumference of the cylindrical mold 54B of the driven wheel moving half 54, so that the cam groove 113 in the axial direction cannot be moved. Grease is applied in the cam groove 113 to assist in the sliding of the moving wheel moving half limited by the lock 112. Further, a seal member is provided on the inner side of both ends of the cylindrical member 114 to prevent grease and thus the inner race of the ball bearing 115 from being held on the outer circumference of the right end of the cylindrical member 114. The ring groove member 116 is in contact with the outer seat of the ball shaft phantom 15
圈Q 滾珠軸承117的内座圈被以螺帽118緊固i提供在外圓 周上之階級部位，且位於從動輪固定半部53的圓筒型部 =53B左端處。外螺紋圓筒型構件12()被固著至滾珠轴承 7的内座圈’使不能在轴向方向上移動。外螺紋圓筒型 件=之旋轉係被防止經由滾珠軸承m傳送至從動輪 2。鎖定構件12ι被固著至外螺紋圓筒型構件，且設 有-被固著至變速箱外㉟38(未示於圖）的末端。因而& 獨立於從動軸50與從動輪52，外螺紋圓筒型構件ΐ2〇可 保持在轴向與旋轉方向中之相關於變速箱外殼％的固定 mXP/發明說明書(補件)/95-11/95125619 21 1314199 狀態。 内螺紋圓筒型構件122覆蓋外螺 螺紋部位，錢於此敎結合。-㈣輪 =二螺紋圓筒型構件122的凸緣122"螺紋： =構件122、内齒輪123及螺检124構成一内螺紋組件 =後敘述之第二中間齒輪144的縮小直徑齒輪142驅動 地紋轉内齒輪123。内螺紋圓筒型構件122在其之内螺紋 響部位處承接來自固定外螺紋圓筒型構# 12〇的外螺紋部 位之推力，且在被旋轉時軸向地驅動。圓形彈簀1被間 置插入在内螺紋圓筒型構件122之末端與被固著至滾^ 軸承115外圓周上的環槽構件116之間。以此一組態，内 螺紋圓筒型構件122的軸向位移導致從動輪移動半部 經由圓形彈簧126、環槽構件116、滾珠轴承115及圓筒 型構件114在軸向方向上移動。外螺紋圓筒型構件12〇與 鲁内螺紋組件12 5構成螺紋進給機構丨2 7。 變速長:速器13 0驅動地旋轉内螺紋組件12 5。此一提速 器130係由電動馬達131與減速齒輪機構132構成。電動 馬達131係根據車速、節流開口、及内燃機速率而自動地 受控旋轉。施加在V型皮帶上的從動輪移動半部之壓擠 力，係經由測量圓形彈簧126之應變所偵測，且被反饋以 供控制之用。 減速齒輪外殼133被緊固至左變速箱外殼38L以界定一 減速齒輪室134於其間。電動馬達131經由配接板135而 312XP/發明說明書(補件)/95-11/95125619 22 1314199 裝附至減速齒輪外殼133。形成在馬達旋轉軸上的小齒輪 136延伸進入減速齒輪室134内。與小齒輪136嚙合之放 j直徑齒輪137與鄰近之縮小直徑齒輪138整合地構成第 :中間齒輪139。第一中間齒輪139被支承以供被左變速 箱外殼38L及減速齒輪外殼133經由滾珠軸承14〇而旋 轉。 、與縮小直徑齒輪138嚙合之放大直徑齒輪141及鄰近的 被配接至旋轉軸143上整合地形成之縮小直徑齒輪142 , ，成第二中間齒輪144 °第二中間齒輪144被支承以供被 變速箱外殼38L及減速齒輪外殼133經由滾珠軸承145 旋轉。縮小直徑齒輪142在軸向方向中較長，使可於任 何軸向位置處嚙合内螺紋組件125之内齒輪123。、 /圖8係齒輪等之配置平面圖，顯示自侧邊觀看時之變速 =統的後半部。在圖7之狀態中，當電動馬達ΐ3ι反應一 制指不而以正常方向旋轉時，動力被經由第一與第二中 :齒輪139、144傳送至與外螺紋圓筒型構件122的螺紋 二：嚙合之内螺紋組件125以旋轉。此一内螺紋組件US 圓开二動其本身在從動軸50之軸向方向中，因而經由 =wrn、環槽構件116、滾珠轴承115及圓筒型構 :昼擠從動輪移動㈣54。如此導致減少從動 =心與從動輪以半部53之間的距離，其在圓周方 :移V型皮帶。當電動馬達反應一控制指示而以 =轉半與:述相反之過程，在從動輪固定半部 動輪移動+部54之間的距離被增加，以因而朝向 312XP/發明說明書(補件)/95-11/95125619 23 1314199 二型皮帶。附帶地，内螺紋組件的左停止請a 破誕供在鎖定構件1 9 lcl 件向左移動之極限。另一末端處，以使制内螺紋組 .著的内部旋轉構件51“皮以螺栓147固 旋轉在半::右端面。離心式離合器51的外部 栓槽轉構件51Α的竭 外部旋轉構件5 i Β的外部圓巧霜之不能互相相對地旋轉。 從動輪達到預定旋轉-欠S i覆盍内部旋轉構件51A。當 件5U與外部旋轉構件5ΐβ傳^轉係經由内部旋轉構 轉。如來昭n 9如、+、 傳仫至從動軸50以開始旋 從動軸旌鐘 經由減速齒輪單元46之齒輪減少 攸動軸50的旋轉，且因 以驅動後輪5。 被減〆之㈣傳送至後輪軸60 在申請專利範圍中敘述的 體例中相關於主動輪移動半二對應於—在别述具 位，該部位係參照圖3至6說明=轴向驅動機構的部 中，「螺紋進給機構」代表示二請專利範圍的說明 「轴向固定侧螺紋部位」代表的螺紋進給機構89， 側螺紋部位」代表外螺紋圓表:型^ 動側螺紋組件」代表外螺紋Of/ 8G’且「軸向地移 帶式無段變速系統產生下述效果。 U)與減速齒輪機構的最終 直徑齒輪1〇2)喷合且被其驅動之輪虫^二中間齒輪的縮小 輪（内齒輪7Ό，係被包含在進給機構的輸入齒 Π地固疋側螺紋組件（内螺 312XP/發明說明書(補件)/95-11/95】25619 24 1314199 、.文組件79)中且不能軸向地移 因而，可減少減速齒輪 機:構之取終齒輪（第二中間齒 ^ , m ^ ^ 门茴輪的縮小直徑齒輪102)的寬 度’因而縮小變速機構之尺寸。 (2 )軸向地移動側螺紋部位（ 永爐杜h “ 1位（外螺紋圓筒型構件80)及軸 碑料回〜 田使用在軸向固定螺紋部位（内 螺、、文圓同型構件7 6 )的寬戶r 士 卞0川見度口Η立中之内側部份褒設。因 而，經由有效地利用死角’可縮小變速系統尺寸。 传HI速齒輪之—（第二中間齒輪之放大尺寸齒輪_ 二有效地利用被界定在軸向地固定側螺紋組件(内螺 ⑼的輸人齒輪（㈣輪77)與主動輪移動半部的 :°卩位（主動輪移動半部之傘型部位49A)之間的死角果 設。因而可縮小變速系統尺寸。 < 進-步的’具體例中之無段變速系統經由提供被電 2動的變速提速器給每—主動輪與從動輪而簡化其之 m構，而非經由習知複雜齒輪機構連結主動輪與從 本具體例之組態達到下述效果。 (1)可輕易獲取適用以配置進給機構之空間。此外， 確保電動馬達之冷卻性能。 (—2)可有效地利用位於互相面對之從動輪的二傘型部位 之母一外表面側上的空間。 (3) 可調整V型皮帶之橫向壓力，而可改善皮帶之 性。 J π (4) 經由一包括彈簧的簡單結構來調整推力。該結構可 在任何時間點輕易最佳化皮帶的橫向壓力。 σ 312ΧΡ/發明說明書(補件)/95-11/95125619 25 1314199 調整量輕易地實施滑輪控制。 (5)可依據皮帶橫向壓力 圖式簡單說明】 圚1係依據本發明之動力單元的侧視圖。The inner race of the ring Q ball bearing 117 is fastened by the nut 118 to the step portion on the outer circumference, and is located at the left end of the cylindrical portion = 53B of the driven wheel fixing half portion 53. The externally threaded cylindrical member 12 () is fixed to the inner race of the ball bearing 7 so as not to be movable in the axial direction. The rotation of the externally threaded cylindrical member = is prevented from being transmitted to the driven pulley 2 via the ball bearing m. The locking member 12i is fixed to the externally threaded cylindrical member and is provided - fixed to the end of the outer gearbox 3538 (not shown). Thus & independent of the driven shaft 50 and the driven wheel 52, the externally threaded cylindrical member ΐ2〇 can be held in the axial and rotational directions relative to the gearbox housing % of the fixed mXP / invention specification (supplement) / 95 -11/95125619 21 1314199 Status. The internally threaded cylindrical member 122 covers the outer threaded portion, and the money is combined therewith. - (four) wheel = flange 122 of the two-threaded cylindrical member 122 " Thread: = member 122, internal gear 123 and screw 124 constitute an internal threaded component = reduced diameter gear 142 of the second intermediate gear 144 described later drives the ground pattern Turn the internal gear 123. The internally threaded cylindrical member 122 receives the thrust from the externally threaded portion of the fixed externally threaded cylindrical structure at its threaded portion and is axially driven when rotated. The circular magazine 1 is interposed between the end of the internally threaded cylindrical member 122 and the ring groove member 116 fixed to the outer circumference of the roller bearing 115. With this configuration, the axial displacement of the internally threaded cylindrical member 122 causes the driven wheel moving half to move in the axial direction via the circular spring 126, the annular groove member 116, the ball bearing 115, and the cylindrical member 114. The externally threaded cylindrical member 12A and the internal threaded member 12 5 constitute a thread feeding mechanism 丨27. The shifting length is: the speeder 13 0 drives the rotating internal thread assembly 12 5 . This speed adjuster 130 is composed of an electric motor 131 and a reduction gear mechanism 132. The electric motor 131 is automatically controlled to rotate in accordance with the vehicle speed, the throttle opening, and the engine speed. The pressing force of the driven wheel moving half applied to the V-belt is detected by measuring the strain of the circular spring 126 and is fed back for control. The reduction gear housing 133 is fastened to the left transmission housing 38L to define a reduction gear chamber 134 therebetween. The electric motor 131 is attached to the reduction gear housing 133 via a mating plate 135 and 312XP/invention specification (supplement)/95-11/95125619 22 1314199. A pinion 136 formed on the rotating shaft of the motor extends into the reduction gear chamber 134. The j-diameter gear 137 meshing with the pinion gear 136 is integrated with the adjacent reduced-diameter gear 138 to constitute the intermediate gear 139. The first intermediate gear 139 is supported for rotation by the left transmission case 38L and the reduction gear housing 133 via the ball bearings 14A. The enlarged diameter gear 141 meshing with the reduced diameter gear 138 and the adjacent reduced diameter gear 142 integrally formed on the rotating shaft 143 are supported as a second intermediate gear 144 ° second intermediate gear 144 for being supported by The transmission case 38L and the reduction gear housing 133 are rotated via the ball bearings 145. The reduced diameter gear 142 is longer in the axial direction so that the internal gear 123 of the internally threaded assembly 125 can be engaged at any axial position. / Figure 8 is a plan view of the gears, etc., showing the rear half of the shifting gear when viewed from the side. In the state of FIG. 7, when the electric motor ΐ3ι reacts and the finger does not rotate in the normal direction, the power is transmitted to the screw thread with the externally threaded cylindrical member 122 via the first and second: gears 139, 144. : Engaged internal threaded assembly 125 to rotate. The internally threaded component US is rotated twice in its axial direction in the driven shaft 50, thus via the =wrn, the ring groove member 116, the ball bearing 115 and the cylindrical configuration: the driven wheel moves (four) 54. This results in a reduction in the follower = the distance between the heart and the driven wheel with the half 53, which is on the circumference: the V-belt. When the electric motor reacts to a control indication and the opposite is reversed, the distance between the driven wheel fixed half moving wheel movement + portion 54 is increased so as to face the 312XP / invention specification (supplement) / 95 -11/95125619 23 1314199 Type 2 belt. Incidentally, the left stop of the internally threaded component is a broken limit for the leftward movement of the locking member 1 9 lcl member. At the other end, the inner rotating member 51 of the inner threaded group is fixedly rotated by a bolt 147 at a half:: the right end face. The outer rotating member 5 of the outer pinch member 51 of the centrifugal clutch 51 The outer circular frost of the crucible cannot rotate relative to each other. The driven wheel reaches a predetermined rotation-under S i covering the inner rotating member 51A. When the member 5U and the outer rotating member 5 are rotated, the rotation is performed via internal rotation. 9, +, pass to the driven shaft 50 to start the spinning slave shaft 旌 clock reduces the rotation of the raking shaft 50 via the gear of the reduction gear unit 46, and drives the rear wheel 5 to be reduced (4) to The rear axle 60 is related to the driving wheel movement half-two in the embodiment described in the patent application scope - in the other description, the portion is described in the section of the axial driving mechanism with reference to Figs. 3 to 6, "thread feeding" The mechanism indicates the description of the patent range, the thread feeding mechanism 89 represented by the "axial fixed side thread portion", and the side thread portion "representing the external thread round table: the type of the side threaded component" represents the external thread Of / 8G' And "axially moving the belt without a segment The shifting system produces the following effects: U) the reduction wheel of the rotifer's intermediate gear that is sprayed and driven by the final diameter gear 1〇2) of the reduction gear mechanism (the internal gear 7Ό is included in the feed mechanism) Input gear Π 疋 疋 螺纹 螺纹 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 312 : The width of the final gear (the second intermediate tooth ^, m ^ ^ the reduced diameter gear 102 of the door horn wheel) is thus reduced the size of the shifting mechanism. (2) The side thread portion is moved axially (Yong furnace Duh "1 position (external-threaded cylindrical member 80) and the shaft material back to the field. The use of the axially fixed threaded part (inner screw, and the same-shaped member of the same type) is wide. The inner part of the center is erected. Therefore, the size of the shifting system can be reduced by effectively utilizing the dead angle'. The HI speed gear is transmitted - (the second intermediate gear is enlarged and the gear _ is effectively utilized to be defined in the axial fixed Side threaded assembly (input screw ((4) wheel 77) and drive wheel movement of inner screw (9) Part: The dead angle between the 卩 position (the movable part moves the half of the umbrella part 49A). Therefore, the size of the shifting system can be reduced. < The step-by-step shifting system in the specific example of the step-by-step The electric 2 speed shifting speed simplifies the structure of each of the driving wheel and the driven wheel, instead of connecting the driving wheel via a conventional complicated gear mechanism and achieving the following effects from the configuration of the specific example. It is easy to obtain space for configuring the feed mechanism. In addition, the cooling performance of the electric motor is ensured. (-2) The space on the outer surface side of the mother of the two umbrella portions located facing each other can be effectively utilized. (3) The lateral pressure of the V-belt can be adjusted to improve the belt. J π (4) The thrust is adjusted via a simple structure including a spring. This structure easily optimizes the lateral pressure of the belt at any point in time. σ 312ΧΡ/Invention manual (supplement)/95-11/95125619 25 1314199 Adjustment amount is easily implemented for pulley control. (5) According to the lateral pressure of the belt, the drawing is a brief description. 圚 1 is a side view of the power unit according to the present invention.
圖2係描述在一平面上之圖}的A_A 0 Ρ 剖面及 剖面之橫剖面展開圖。 圖3係一放大橫剖面圖 被組裝至一曲軸的狀態。 ’描述一主 動輪及其之周邊構件Fig. 2 is a cross-sectional view showing the A_A 0 剖面 section and the cross section of the figure on a plane. Fig. 3 is a view showing an enlarged cross-sectional view assembled to a crankshaft. Describe a main wheel and its surrounding components
圖4係一放大橫剖面圖’僅顯示沿圖3之IV-1 v立彳面取 得的軸部位。 圖5係變速系統的前半部之橫剖面展開圖。 圖6係齒輪等之配置平面圖，顯示自側面觀看時之變速 系統的前半部。 圖7係變速系統的後半部之橫剖面展開圖。 圖8係齒輪等之配置平面圖’顯示變速系統的後半部。 【主要元件符號說明】 1 動力單元 2 水冷式内燃機 3 變速系統 4 後輪支承部位 5 後輪 6 曲轴箱 6L 左曲軸箱 6R 右曲軸箱 7 汽缸體 312XP/發明說明書(補件)奶-11/95125619 26 1314199 8 汽缸頭 9 汽缸頭外蓋 10 頸轴承 10L 頸軸承 10R 頸軸承 11 曲轴 11A 第一縮小直徑部位 11B 第二縮小直徑部位 11a 階級 lib 階級 11c 曲轴端面 lid 栓槽 lie 栓槽 12 汽缸内徑 13 活塞 14 曲轴銷 15 活塞銷 16 連桿 20 燃燒室 21 點火塞 22 螺栓 23 外殼外蓋 27 排氣閥 28 凸輪軸 312XP/發明說明書(補件)/95-11/95125619 1314199 29 排氣凸輪 30 驅動鏈輪 31 從動鏈輪 32 無端環鏈 33 右曲軸箱外殼 34 定子 35 轉子 36 發電機 37 從動齒輪 38 變速箱外殼 38R 右變速箱外殼 38S 分隔壁 38L 左變速箱外殼 39 支承金屬 40 滾珠轴承 41 支承金屬 42 滾動軸承 43A 連接金屬 43B 連接金屬 44 鉚釘 45 V型皮帶式無段變速系統 46 減速齒輪單元 47 主動輪 48 主動輪固定半部 312XP/發明說明書(補件)/95-11/95125619 28 1314199 48a 栓槽 49 主動輪移動半部 49A 傘型部位 49B 圓筒型部位 49Ba 突出栓槽 50 從動軸 50a 階級部位 50b 階級部位 50c 階級部位 51 離心式離合器 51A 内部旋轉構件 51B 外部旋轉構件 52 從動輪 53 從動輪固定半部 53A 傘型部位 53B 圓筒型部位 54 從動輪移動半部 54A 傘型部位 54B 圓筒型部位 55 無端V型皮帶 56 縮小直徑齒輪 57 中間軸 58 放大直徑齒輪 59 縮小直徑齒輪 312XP/發明說明書(補件)/95-11/95125619 29 1314199 60 後輪轴 61 放大直徑齒輪 62 臂 63 滾珠軸承 64 第一支承套筒 65 導引套筒 65a 栓槽 65b 外側栓槽 • 66 第二支承套筒 67 墊片 68 螺栓 69 密封件 70 間隙 72 滾珠軸承 75 滾珠軸承外座圈固持構件 75a 外圓周凸緣 76 内螺紋圓筒型構件 76a 外圓周凸緣 77 内齒輪 78 螺栓 79 内螺紋組件 80 外螺紋圓筒型構件 80a 凸緣 81 鎖定構件 312XP/發明說明書(補件)/95-11/95125619 30 1314199 81a 鎖定轴部位 81b 突出部位 81c 前停止器 81d 伸長件 82 螺栓 '83 外螺紋組件 84 鎖定導執 85 後停止器 • 86 螺栓 87 衝程感測器 88 鎖定機構 89 螺紋進給機構 90 變速提速器 91 電動馬達 92 減速齒輪機構 93 減速齒輪外殼 W 93L 左側外殼構件 93E 末端外殼構件 93R 右側外殼構件 94 減速齒輪室 95 裝附板 96 小齒輪 97 放大直徑齒輪 98 縮小直徑齒輪 312XP/發明說明書(補件)/95-11/95125619 31 1314199 99 100 101 102 103 ' 104 105 110 • HI 112 113 114 115 116 117 118 籲120 121 121a 122 122a 123 124 125 第一中間齒輪 滚珠軸承 放大直徑齒輪 縮小直徑齒輪 旋轉軸 第二中間齒輪 滾珠軸承 滚珠轴承 滾動轴承 銷 凸輪槽 圓筒型構件 滾珠軸承 環槽構件 滾珠軸承 螺帽 外螺紋圓筒型構件 鎖定構件 左停止器 内螺紋圓筒型構件 凸緣 内齒輪 螺栓 内螺紋組件 312XP/發明說明書(補件)/95-11/95125619 1314199 126 圓形彈簧 127 螺紋進給機構 130 變速提速器 131 電動馬達 132 減速齒輪機構 133 減速齒輪外殼 134 減速齒輪室 135 配接板 136 小齒輪 137 放大直徑齒輪 138 縮小直徑齒輪 139 第一中間齒輪 140 滾珠軸承 141 放大直徑齒輪 142 縮小直徑齒輪 143 旋轉軸 144 第二中間齒輪 145 滾珠軸承 147 螺栓 148 栓槽 F 箭頭 312XP/發明說明書(補件)/95-11/95125619Fig. 4 is an enlarged cross-sectional view showing only the shaft portion taken along the IV-1 v vertical plane of Fig. 3. Figure 5 is a cross-sectional development view of the front half of the shifting system. Fig. 6 is a plan view showing the arrangement of gears and the like, showing the front half of the shifting system when viewed from the side. Figure 7 is a cross-sectional development view of the rear half of the shifting system. Fig. 8 is a plan view showing the arrangement of gears and the like' showing the rear half of the shifting system. [Main component symbol description] 1 Power unit 2 Water-cooled internal combustion engine 3 Transmission system 4 Rear wheel support part 5 Rear wheel 6 Crankcase 6L Left crankcase 6R Right crankcase 7 Cylinder block 312XP/Invention manual (supplement) Milk-11/ 95125619 26 1314199 8 Cylinder head 9 Cylinder head cover 10 Neck bearing 10L Neck bearing 10R Neck bearing 11 Crankshaft 11A First reduced diameter portion 11B Second reduced diameter portion 11a Class lib Class 11c Crankshaft end face pin groove lie Pin groove 12 Cylinder Diameter 13 Piston 14 Crank pin 15 Piston pin 16 Connecting rod 20 Combustion chamber 21 Ignition plug 22 Bolt 23 Housing cover 27 Exhaust valve 28 Camshaft 312XP / Invention manual (supplement) / 95-11/95125619 1314199 29 Exhaust cam 30 drive sprocket 31 driven sprocket 32 endless chain 33 right crankcase shell 34 stator 35 rotor 36 generator 37 driven gear 38 gearbox housing 38R right gearbox housing 38S partition wall 38L left gearbox housing 39 support metal 40 Ball bearing 41 Support metal 42 Rolling bearing 43A Connecting metal 43B Connecting metal 44 Rivet 45 V-shaped leather Belt type stepless speed change system 46 Reduction gear unit 47 Drive wheel 48 Drive wheel fixing half 312XP / Invention manual (supplement) / 95-11/95125619 28 1314199 48a Bolting groove 49 Driving wheel moving half 49A Umbrella part 49B round Cartridge portion 49Ba Projection bolt groove 50 Drive shaft 50a Class portion 50b Class portion 50c Class portion 51 Centrifugal clutch 51A Internal rotating member 51B External rotating member 52 Drive wheel 53 Follower wheel fixing half 53A Umbrella portion 53B Cylindrical portion 54 Drive wheel moving half 54A Umbrella type 54B Cylindrical part 55 Endless V-belt 56 Reduced diameter gear 57 Intermediate shaft 58 Magnified diameter gear 59 Reduced diameter gear 312XP / Invention manual (supplement) / 95-11/95125619 29 1314199 60 rear axle 61 enlarged diameter gear 62 arm 63 ball bearing 64 first bearing sleeve 65 guiding sleeve 65a bolt groove 65b outer bolt groove 66 66 second bearing sleeve 67 spacer 68 bolt 69 seal 70 gap 72 Ball bearing 75 Ball bearing outer race retaining member 75a Outer circumferential flange 76 Internal thread cylindrical member 76a Circumferential flange 77 internal gear 78 bolt 79 internal thread assembly 80 externally threaded cylindrical member 80a flange 81 locking member 312XP / invention specification (supplement) / 95-11/95125619 30 1314199 81a locking shaft portion 81b protruding portion 81c front Stopper 81d Extension 82 Bolt '83 Externally threaded assembly 84 Locking guide 85 Rear stop • 86 Bolt 87 Stroke sensor 88 Locking mechanism 89 Threaded feed mechanism 90 Variable speed governor 91 Electric motor 92 Reduction gear mechanism 93 Reduction gear Housing W 93L Left side housing member 93E End housing member 93R Right side housing member 94 Reduction gear chamber 95 Mounting plate 96 Pinion gear 97 Magnified diameter gear 98 Reduced diameter gear 312XP / Invention manual (supplement) / 95-11/95125619 31 1314199 99 100 101 102 103 ' 104 105 110 • HI 112 113 114 115 116 117 118 120 120 121 121a 122 122a 123 124 125 First intermediate gear ball bearing enlarged diameter gear reduced diameter gear rotating shaft second intermediate gear ball bearing ball bearing rolling bearing Pin cam groove cylindrical member ball bearing ring groove member ball shaft Nut external thread cylindrical member locking member left stopper internal thread cylindrical member flange inner gear bolt internal thread assembly 312XP / invention manual (supplement) / 95-11/95125619 1314199 126 circular spring 127 thread feed Mechanism 130 Variable Speed Speed Regulator 131 Electric Motor 132 Reduction Gear Mechanism 133 Reduction Gear Housing 134 Reduction Gear Chamber 135 Adapter Plate 136 Pinion 137 Magnification Diameter Gear 138 Reduced Diameter Gear 139 First Intermediate Gear 140 Ball Bearing 141 Magnified Diameter Gear 142 Reduced Diameter Gear 143 Rotary shaft 144 Second intermediate gear 145 Ball bearing 147 Bolt 148 Bolting groove F 312XP / Invention manual (supplement) / 95-11/95125619