TW201314077A - Link-type stepless speed change device - Google Patents
Link-type stepless speed change device Download PDFInfo
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- TW201314077A TW201314077A TW100135390A TW100135390A TW201314077A TW 201314077 A TW201314077 A TW 201314077A TW 100135390 A TW100135390 A TW 100135390A TW 100135390 A TW100135390 A TW 100135390A TW 201314077 A TW201314077 A TW 201314077A
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Abstract
Description
本發明係有關一種連桿式無段變速裝置，特別是指一種具有N組連動機構之連桿式無段變速裝置 ，其兼具齒輪傳動之無段變速及可調整變速效果等優點及功效。The invention relates to a link type stepless speed change device, in particular to a link type stepless speed change device with N sets of linkage mechanisms, which has the advantages and functions of a gearless stepless shifting and an adjustable shifting effect.
傳統的無段變速器大多使用皮帶或是齒輪傳動，但兩者係分別存在著不同之優缺點：Conventional stepless transmissions mostly use belts or gears, but there are different advantages and disadvantages:
[1]使用皮帶傳動。使用皮帶傳動雖然具有價格便宜、較輕巧、噪音低等優點，但皮帶是使用摩擦力傳動，要增加摩擦力就必須將皮帶調緊，無形中會造成軸承的負載，使用久了皮帶會老化，造成軸承壽命減少且容易打滑使傳輸效率變差。[1] Use a belt drive. Although the belt drive has the advantages of low price, light weight, low noise, etc., the belt is driven by friction force. To increase the friction force, the belt must be tightened, which will inevitably cause the load of the bearing, and the belt will age after being used for a long time. The bearing life is reduced and the slippage is easy to make the transmission efficiency worse.
[2]使用齒輪傳動。使用齒輪傳動雖然具有效率高、壽命長、傳動比準確等優點，但一般齒輪傳動無法達到無段變速的功能。[2] Use gear transmission. Although the gear transmission has the advantages of high efficiency, long service life, accurate transmission ratio, etc., the general gear transmission cannot achieve the function of stepless speed change.
因此，有必要研發新產品，以解決上述缺點及問題。Therefore, it is necessary to develop new products to solve the above shortcomings and problems.
本發明之目的在於提供一種連桿式無段變速裝置，其兼具齒輪傳動之無段變速及可調整變速效果等優點及功效，用以解決習知技術無法同時兼具效率高、壽命長、傳動比準確及無段變速之問題。The object of the present invention is to provide a link type stepless speed change device, which has the advantages and functions of the gearless stepless shifting and the adjustable shifting effect, and is capable of solving the conventional technology and has the advantages of high efficiency and long service life. The gear ratio is accurate and the problem of stepless speed change.
本發明解決上述問題之技術手段係提供一種連桿式無段變速裝置，其包括：The technical means for solving the above problems of the present invention provides a link type stepless speed change device, which comprises:
一機架，其係具有N個機架樞接部；N係為一正整數且N≧3；a rack having N rack pivoting portions; N is a positive integer and N≧3;
一圓盤架，其係具有一圓盤及一軸部；該圓盤係具有N個圓盤樞接部；該軸部係固定於該機架上；a disc holder having a disc and a shaft portion; the disc has N disc pivoting portions; the shaft portion is fixed to the frame;
一輸入軸，其係具有一輸入端及一連動端；該輸入軸係可樞轉的穿設於該軸部上；An input shaft having an input end and a linkage end; the input shaft is pivotally disposed on the shaft portion;
一偏心圓盤，其係具有一偏心連接部及一導引槽；該偏心連接部係連接該輸入軸之連動端；An eccentric disk having an eccentric connecting portion and a guiding groove; the eccentric connecting portion is connected to the linking end of the input shaft;
一輸出部；An output unit;
N組連動機構，每一連動機構係具有一控制桿、一搖桿、一滑動桿、一輸出桿及一單向帶動部；該控制桿、該滑動桿及該輸出桿之其中一端係相互樞接，該控制桿之另一端係樞接於該圓盤樞接部上，該滑動桿係可滑動的設於該搖桿上，該輸出桿之另一端係連接該單向帶動部；該搖桿之一端係樞接於該機架樞接部，另一端係可滑動的設於該偏心圓盤之導引槽；而該單向帶動部係用以連動該輸出部轉動；The N-group linkage mechanism has a control rod, a rocker, a sliding rod, an output rod and a one-way driving part; the control rod, the sliding rod and one end of the output rod are mutually pivoted The other end of the control rod is pivotally connected to the pivotal portion of the disk, the sliding rod is slidably disposed on the rocker, and the other end of the output rod is connected to the one-way driving portion; One end of the rod is pivotally connected to the pivoting portion of the frame, and the other end is slidably disposed on the guiding groove of the eccentric disk; and the one-way driving portion is configured to rotate the output portion;
藉此，驅動該輸入軸轉動後，係會帶動該偏心圓盤偏心轉動，使N組連動機構依序作動，進而連動該輸出部轉動。Thereby, after the input shaft is driven to rotate, the eccentric disk is driven to rotate eccentrically, so that the N sets of interlocking mechanisms are sequentially operated, and the output portion is linked to rotate.
本發明之上述目的與優點，不難從下述所選用實施例之詳細說明與附圖中，獲得深入瞭解。The above objects and advantages of the present invention will be readily understood from the following detailed description of the preferred embodiments illustrated herein.
請參閱第一至第四圖，其係本發明之連桿式無段變速裝置的第一實施例，其包括：一機架10、一圓盤架20、一輸入軸30、一偏心圓盤40、一輸出部50及三組連動機構60。Please refer to the first to fourth figures, which are a first embodiment of the link type stepless transmission of the present invention, comprising: a frame 10, a disc holder 20, an input shaft 30, and an eccentric disc. 40. An output unit 50 and three sets of linkage mechanisms 60.
關於該機架10，其係具有三個機架樞接部11。Regarding the frame 10, it has three frame pivoting portions 11.
該圓盤架20係具有一圓盤21、一軸部22、一固定元件23及一輔助太陽齒輪部24；該圓盤21係具有三個圓盤樞接部211；該軸部22係固定於該機架10上；該固定元件23係用以將該軸部22固定於該機架10上。The disc holder 20 has a disc 21, a shaft portion 22, a fixing member 23 and an auxiliary sun gear portion 24; the disc 21 has three disc pivoting portions 211; the shaft portion 22 is fixed to The frame 10 is configured to fix the shaft portion 22 to the frame 10.
關於該輸入軸30，其係具有一輸入端31及一連動端32；該輸入軸30係可樞轉的穿設於該軸部22上。The input shaft 30 has an input end 31 and a linkage end 32. The input shaft 30 is pivotally disposed on the shaft portion 22.
該偏心圓盤40係具有一偏心連接部41及一導引槽42；該偏心連接部41係連接該輸入軸30之連動端32。The eccentric disk 40 has an eccentric connecting portion 41 and a guiding groove 42; the eccentric connecting portion 41 is connected to the linking end 32 of the input shaft 30.
該輸出部50係具有一輸出太陽齒輪部51及一輸出軸52，該輸出軸52係固定於該輸出太陽齒輪部51。The output unit 50 has an output sun gear portion 51 and an output shaft 52, and the output shaft 52 is fixed to the output sun gear portion 51.
而每一組連動機構60係具有一控制桿61、一搖桿62、一滑動桿63、一輸出桿64及一單向帶動部65；該控制桿61、該滑動桿63及該輸出桿64之其中一端係相互樞接，該控制桿61之另一端係樞接於該圓盤樞接部211上，該滑動桿63係可滑動的設於該搖桿62上，該輸出桿64之另一端係連接該單向帶動部65；該搖桿62之一端係樞接於該機架樞接部11，另一端係可滑動的設於該偏心圓盤40之導引槽42；而該單向帶動部65係用以連動該輸出部50轉動。又，該單向帶動部65係具有一連動桿651、一對單向連動元件652及一對行星齒輪部653；該對單向連動元件652係設於該連動桿651之兩端，並限制該對行星齒輪部653只能進行單向轉動；而該對行星齒輪部653可分別連動該輔助太陽齒輪部24及該輸出太陽齒輪部51轉動，進而使該輸出軸52達到轉動。Each of the linkage mechanisms 60 has a control rod 61, a rocker 62, a sliding rod 63, an output rod 64 and a one-way driving portion 65; the control rod 61, the sliding rod 63 and the output rod 64 One end of the control rod 61 is pivotally connected to the disc pivoting portion 211. The sliding rod 63 is slidably disposed on the rocker 62, and the output rod 64 is another One end of the rocker 62 is pivotally connected to the frame pivoting portion 11 and the other end is slidably disposed on the guiding groove 42 of the eccentric disk 40; The driving portion 65 is configured to interlock the rotation of the output portion 50. Moreover, the one-way driving portion 65 has a linkage rod 651, a pair of one-way linkage elements 652 and a pair of planetary gear portions 653; the pair of one-way linkage elements 652 are disposed at both ends of the linkage rod 651 and are limited The pair of planetary gear portions 653 can only perform one-way rotation; and the pair of planetary gear portions 653 can respectively rotate the auxiliary sun gear portion 24 and the output sun gear portion 51 to rotate the output shaft 52.
藉此，驅動該輸入軸30轉動後，係會帶動該偏心圓盤40偏心轉動，使N組連動機構60依序作動，進而連動該輸出部50轉動。Thereby, after the input shaft 30 is driven to rotate, the eccentric disk 40 is driven to rotate eccentrically, and the N sets of interlocking mechanisms 60 are sequentially operated to interlock the output portion 50 to rotate.
舉例來說，如第五A及第五B圖所示，假設本發明具有一第一連動機構60A、一第二連動機構60B及一第三連動機構60C，且該單向傳動元件652係限制該對行星齒輪部653只能進行一第一轉動方向A1之轉動；當該輸入軸30受到驅動而進行一第二轉動方向A2之轉動，使該偏心轉盤40由一第一位置P1被帶動至一第二位置P2時，其導引槽42係會帶動該搖桿62於該機架樞接部11上偏轉，使該滑動桿63同步偏轉並連動該輸出桿64，進而使該第一連動機構60A及該第二連動機構60B之行星齒輪部653被推動(即實心箭頭所示)而沿該輸出太陽齒輪部51移動，同時產生第一轉動方向A1之轉動(也就是空轉，無法帶動該輸出太陽齒輪部51轉動)，而該第三連動機構之行星齒輪部653被拉動(即空心箭頭所示)而沿該輸出太陽齒輪部51移動，且轉動方向受到限制(無法進行該第二轉動方向A2之轉動)，故會帶動該輸出太陽齒輪部51、該輸出軸52進行該第二轉動方向A2之轉動。For example, as shown in FIGS. 5A and 5B, it is assumed that the present invention has a first linkage mechanism 60A, a second linkage mechanism 60B, and a third linkage mechanism 60C, and the one-way transmission element 652 is limited. The pair of planetary gear portions 653 can only rotate in a first rotational direction A1; when the input shaft 30 is driven to rotate in a second rotational direction A2, the eccentric turntable 40 is driven by a first position P1 to In a second position P2, the guiding groove 42 drives the rocker 62 to deflect on the frame pivoting portion 11, so that the sliding rod 63 is synchronously deflected and interlocked with the output rod 64, thereby making the first linkage The planetary gear portion 653 of the mechanism 60A and the second interlocking mechanism 60B is pushed (ie, shown by a solid arrow) to move along the output sun gear portion 51, and at the same time, the rotation of the first rotational direction A1 is generated (that is, the idling is impossible to drive the The output sun gear portion 51 rotates, and the planetary gear portion 653 of the third linkage mechanism is pulled (ie, indicated by a hollow arrow) to move along the output sun gear portion 51, and the rotation direction is restricted (the second rotation cannot be performed) Direction A2 rotation), so The output sun gear driving portion 51, the rotation of the output shaft 52 of the second rotational direction A2.
如第五C圖所示，該偏心轉盤40由該第二位置P2被帶動至一第三位置P3時，該第二連動機構60B及該第三連動機構60C之行星齒輪部653係被推動而沿該輸出太陽齒輪部51移動，同時產生第一轉動方向A1之轉動，而該第一連動機構60A之行星齒輪部653則被拉動而沿該輸出太陽齒輪部51移動，且轉動方向受到限制，故會帶動該輸出太陽齒輪部51、該輸出軸52進行該第二轉動方向A2之轉動。As shown in FIG. 5C, when the eccentric turntable 40 is driven to the third position P3 by the second position P2, the second interlocking mechanism 60B and the planetary gear portion 653 of the third linking mechanism 60C are pushed. Moving along the output sun gear portion 51, the rotation of the first rotation direction A1 is simultaneously generated, and the planetary gear portion 653 of the first linkage mechanism 60A is pulled to move along the output sun gear portion 51, and the rotation direction is restricted. Therefore, the output sun gear portion 51 and the output shaft 52 are rotated in the second rotation direction A2.
如第五D圖所示，該偏心轉盤40由該第三位置P3被帶動至一第四位置P4時，該第一連動機構60A及該第二連動機構60B之行星齒輪部653係被拉動而沿該輸出太陽齒輪部51移動，且轉動方向受到限制，故會帶動該輸出太陽齒輪部51、該輸出軸52進行該第二轉動方向A2之轉動；而該第三連動機構之行星齒輪部653被推動而沿該輸出太陽齒輪部51移動，同時進行第一轉動方向A1之空轉。As shown in FIG. 5D, when the eccentric turntable 40 is driven to the fourth position P4 by the third position P3, the first interlocking mechanism 60A and the planetary gear portion 653 of the second linking mechanism 60B are pulled. Moving along the output sun gear portion 51, and the rotation direction is restricted, so that the output sun gear portion 51 and the output shaft 52 are rotated in the second rotation direction A2; and the planetary gear portion 653 of the third linkage mechanism It is pushed to move along the output sun gear portion 51 while performing the idle rotation in the first rotational direction A1.
由此可知，本發明藉由三組連動機構60被該偏心轉盤40帶動時所產生連動變化，使得該輸出部50可達到預定轉動方向之變轉速輸出；當然，該行星齒輪部653之轉向限制設計，係可使該輸出部50只進行單一轉動方向之轉動。It can be seen that the interlocking change occurs when the three sets of interlocking mechanism 60 are driven by the eccentric turntable 40, so that the output portion 50 can reach the variable rotational speed output of the predetermined rotational direction; of course, the steering limitation of the planetary gear portion 653 The design allows the output portion 50 to be rotated only in a single direction of rotation.
由於該圓盤架20係藉由該固定元件23而固定於該機架10上，因此，將該固定元件23拆卸或調鬆(若為鎖合固定時)，則可使該圓盤21達到轉動；藉由該圓盤21之轉動，係可帶動該控制桿61之位置變化，同時連動該滑動桿63於該搖桿62上滑動，改變該控制桿61、滑動桿63及該輸 出桿64相互樞接之一端至該機架樞接部11之距離（如第六A及第六B圖所示，該圓盤21轉動一預定角度θ後，該控制桿61、滑動桿63及該輸出桿64相互樞接之一端至該機架樞接部11之距離係由一第一距離S1縮短成一第二距離S2），進而改變該連動機構60帶動該輸出部50之變速效果(其距離變化，可依所需之速度而調整)。Since the disc frame 20 is fixed to the frame 10 by the fixing member 23, the fixing member 23 is detached or loosened (if it is locked and fixed), the disc 21 can be reached. Rotation; by the rotation of the disc 21, the position of the control rod 61 can be changed, and the sliding rod 63 is slid on the rocker 62, and the control rod 61, the sliding rod 63 and the output rod 64 are changed. The distance between one end of the pivotal connection to the frame pivoting portion 11 (as shown in FIGS. 6A and 6B, after the disk 21 is rotated by a predetermined angle θ, the lever 61, the sliding lever 63 and the output The distance from the one end of the rod 64 to the frame pivoting portion 11 is shortened by a first distance S1 to a second distance S2), thereby changing the shifting effect of the linking mechanism 60 to drive the output portion 50 (the distance change thereof) , can be adjusted according to the speed required).
如第七A及第七B圖所示，其係為本發明之第二實施例，該控制桿61、該滑動桿63及該輸出桿64相互樞接之一端，係樞設於該機架樞接部11上；當該輸入軸30轉動而使該偏心轉盤40帶動該搖桿62偏擺時(該搖桿62與該滑動桿63以該機架樞接部11為軸心偏擺)，該輸出桿64係不會做推、拉之動作，只能達到空轉(也就是該輸出部50係不會被該連動機構60所帶動，形成空檔狀態)。As shown in the seventh embodiment of the present invention, the control rod 61, the sliding rod 63 and the output rod 64 are pivotally connected to one another, and are pivoted to the frame. When the input shaft 30 rotates to cause the eccentric turntable 40 to yaw the rocker 62 (the rocker 62 and the sliding rod 63 are pivoted with the frame pivoting portion 11 as an axis) The output rod 64 is not pushed or pulled, and can only be idling (that is, the output portion 50 is not driven by the linkage mechanism 60 to form a neutral state).
由以上說明可知，本發明利用至少三組連動機構60進行連動，在該偏心轉盤40轉動至不同位置時，都至少會帶動一組連動機構60連動該輸出部50(也就是至少有一組連動機構60之行星齒輪部653不會呈空轉)，進而使輸出動力達到連續不間斷之功能，並可達到無段變速之功能；如第八圖所示，其係該偏心轉盤40轉動至不同角度時，三組連動機構60之輸出桿64輸出角速度變化(分別為一第一曲線L1、一第二曲線L2及一第三曲線L3)，由其變化可知，三組輸出桿64係隨該偏心轉盤40之轉動角度變化依序輸出，使輸出動力達到連續不間斷之功能。As can be seen from the above description, the present invention utilizes at least three sets of linkage mechanisms 60 for interlocking. When the eccentric turntable 40 is rotated to different positions, at least one set of linkage mechanisms 60 is linked to the output portion 50 (that is, at least one set of linkage mechanisms) The planetary gear portion 653 of the 60 is not idling, so that the output power reaches a continuous uninterrupted function, and the function of the stepless shifting can be achieved; as shown in the eighth figure, when the eccentric turntable 40 is rotated to different angles The output rods 64 of the three sets of interlocking mechanisms 60 output angular velocity changes (a first curve L1, a second curve L2, and a third curve L3, respectively), and as the change thereof, the three sets of output rods 64 are associated with the eccentric turntable. The change of the rotation angle of 40 is sequentially output, so that the output power reaches a continuous uninterrupted function.
綜上所述，本發明之優點及功效可歸納為：In summary, the advantages and effects of the present invention can be summarized as follows:
[1]齒輪傳動之無段變速。一般無段變速器若以皮帶傳動，會造成軸承壽命減少且容易打滑使傳輸效率變差，而一般齒輪傳動雖可改善皮帶傳動之缺點，但卻無法達到無段變速的功能；而本發明利用該連動機構60之設計，不但可達到齒輪傳動之效率高、壽命長、傳動比準確等優點，且兼具無段變速之功能。[1] Stepless shifting of gear transmission. Generally, if the stepless transmission is driven by a belt, the bearing life is reduced and the slippage is easy to make the transmission efficiency worse. However, the general gear transmission can improve the shortcoming of the belt transmission, but cannot achieve the function of the stepless shifting; The design of the linkage mechanism 60 not only achieves the advantages of high efficiency, long life, accurate transmission ratio, and the like, and has the function of stepless speed change.
[2]可調整變速效果。本發明改變該滑動桿63與該控制桿61之樞接點至該機架樞接部11之距離，即改變該連動機構60帶動該輸出部50之變速效果。[2] Adjustable shifting effect. The invention changes the distance between the pivoting point of the sliding rod 63 and the control rod 61 to the frame pivoting portion 11, that is, changes the shifting effect of the linking mechanism 60 to drive the output portion 50.
以上僅是藉由較佳實施例詳細說明本發明，對於該實施例所做的任何簡單修改與變化，皆不脫離本發明之精神與範圍。The present invention has been described in detail with reference to the preferred embodiments of the present invention, without departing from the spirit and scope of the invention.
由以上詳細說明，可使熟知本項技藝者明瞭本發明的確可達成前述目的，實已符合專利法之規定，爰提出發明專利申請。From the above detailed description, it will be apparent to those skilled in the art that the present invention can achieve the foregoing objects, and the invention has been in accordance with the provisions of the patent law.
10．．．機架10. . . frame
11．．．機架樞接部11. . . Rack pivot
20．．．圓盤架20. . . Disc holder
21．．．圓盤twenty one. . . disc
211．．．圓盤樞接部211. . . Disc pivot
22．．．軸部twenty two. . . Shaft
23．．．固定元件twenty three. . . Fixed component
24．．．輔助太陽齒輪部twenty four. . . Auxiliary sun gear
30．．．輸入軸30. . . Input shaft
31．．．輸入端31. . . Input
32．．．連動端32. . . Linked end
40．．．偏心圓盤40. . . Eccentric disc
41．．．偏心連接部41. . . Eccentric connection
42．．．導引槽42. . . Guide slot
50．．．輸出部50. . . Output department
51．．．輸出太陽齒輪部51. . . Output sun gear
52．．．輸出軸52. . . Output shaft
60．．．連動機構60. . . Linkage mechanism
60A．．．第一連動機構60A. . . First linkage mechanism
60B．．．第二連動機構60B. . . Second linkage mechanism
60C．．．第三連動機構60C. . . Third linkage mechanism
61．．．控制桿61. . . Controller
62．．．搖桿62. . . Rocker
63．．．滑動桿63. . . Slider
64．．．輸出桿64. . . Output rod
65．．．單向帶動部65. . . One-way driving part
651．．．連動桿651. . . Linkage rod
652．．．單向連動元件652. . . One-way linkage element
653．．．行星齒輪部653. . . Planetary gear
θ．．．預定角度θ. . . Predetermined angle
P1．．．第一位置P1. . . First position
P2．．．第二位置P2. . . Second position
P3．．．第三位置P3. . . Third position
P4．．．第四位置P4. . . Fourth position
A1．．．第一轉動方向A1. . . First direction of rotation
A2．．．第二轉動方向A2. . . Second direction of rotation
S1．．．第一距離S1. . . First distance
S2．．．第二距離S2. . . Second distance
L1．．．第一曲線L1. . . First curve
L2．．．第二曲線L2. . . Second curve
L3．．．第三曲線L3. . . Third curve
第一圖係本發明之連桿式無段變速裝置之示意圖The first figure is a schematic diagram of the link type stepless speed change device of the present invention.
第二圖係本發明之連桿式無段變速裝置之內部示意圖The second figure is an internal schematic diagram of the link type stepless speed change device of the present invention.
第三圖係本發明之連桿式無段變速裝置之分解示意圖The third figure is an exploded view of the link type stepless speed change device of the present invention.
第四圖係本發明之連桿式無段變速裝置之局部剖視示意圖The fourth figure is a partial cross-sectional view of the link type stepless speed change device of the present invention.
第五A圖係本發明之連動機構動作一之示意圖Figure 5A is a schematic diagram of the action of the linkage mechanism of the present invention
第五B圖係本發明之連動機構動作二之示意圖Figure 5B is a schematic diagram of the action 2 of the linkage mechanism of the present invention
第五C圖係本發明之連動機構動作三之示意圖The fifth C diagram is a schematic diagram of the action 3 of the linkage mechanism of the present invention
第五D圖係本發明之連動機構動作四之示意圖The fifth D diagram is a schematic diagram of the action 4 of the linkage mechanism of the present invention
第六A圖係本發明之滑動桿調整動作一之示意圖Figure 6A is a schematic diagram of the adjustment action of the sliding rod of the present invention
第六B圖係本發明之滑動桿調整動作二之示意圖Figure 6B is a schematic view of the adjustment action 2 of the sliding rod of the present invention
第七A圖係本發明之第二實施例之示意圖Figure 7A is a schematic view of a second embodiment of the present invention
第七B圖係本發明之第二實施例之俯視示意圖Figure 7B is a top plan view of a second embodiment of the present invention
10．．．機架10. . . frame
11．．．機架樞接部11. . . Rack pivot
20．．．圓盤架20. . . Disc holder
21．．．圓盤twenty one. . . disc
211．．．圓盤樞接部211. . . Disc pivot
22．．．軸部twenty two. . . Shaft
23．．．固定元件twenty three. . . Fixed component
24．．．輔助太陽齒輪部twenty four. . . Auxiliary sun gear
30．．．輸入軸30. . . Input shaft
31．．．輸入端31. . . Input
32．．．連動端32. . . Linked end
40．．．偏心圓盤40. . . Eccentric disc
41．．．偏心連接部41. . . Eccentric connection
42．．．導引槽42. . . Guide slot
50．．．輸出部50. . . Output department
51．．．輸出太陽齒輪部51. . . Output sun gear
52．．．輸出軸52. . . Output shaft
60．．．連動機構60. . . Linkage mechanism
61．．．控制桿61. . . Controller
62．．．搖桿62. . . Rocker
63．．．滑動桿63. . . Slider
64．．．輸出桿64. . . Output rod
65．．．單向帶動部65. . . One-way driving part
651．．．連動桿651. . . Linkage rod
652．．．單向連動元件652. . . One-way linkage element
653．．．行星齒輪部653. . . Planetary gear
Claims (4)
一機架，其係具有N個機架樞接部；N係為一正整數且N≧3；
一圓盤架，其係具有一圓盤及一軸部；該圓盤係具有N個圓盤樞接部；該軸部係固定於該機架上；
一輸入軸，其係具有一輸入端及一連動端；該輸入軸係可樞轉的穿設於該軸部上；
一偏心圓盤，其係具有一偏心連接部及一導引槽；該偏心連接部係連接該輸入軸之連動端；
一輸出部；
N組連動機構，每一連動機構係具有一控制桿、一搖桿、一滑動桿、一輸出桿及一單向帶動部；該控制桿、該滑動桿及該輸出桿之其中一端係相互樞接，該控制桿之另一端係樞接於該圓盤樞接部上，該滑動桿係可滑動的設於該搖桿上，該輸出桿之另一端係連接該單向帶動部；該搖桿之一端係樞接於該機架樞接部，另一端係可滑動的設於該偏心圓盤之導引槽；而該單向帶動部係用以連動該輸出部轉動；
藉此，驅動該輸入軸轉動後，係會帶動該偏心圓盤偏心轉動，使N組連動機構依序作動，進而連動該輸出部轉動。A link type stepless speed change device comprising:
a rack having N rack pivoting portions; N is a positive integer and N≧3;
a disc holder having a disc and a shaft portion; the disc has N disc pivoting portions; the shaft portion is fixed to the frame;
An input shaft having an input end and a linkage end; the input shaft is pivotally disposed on the shaft portion;
An eccentric disk having an eccentric connecting portion and a guiding groove; the eccentric connecting portion is connected to the linking end of the input shaft;
An output unit;
The N-group linkage mechanism has a control rod, a rocker, a sliding rod, an output rod and a one-way driving part; the control rod, the sliding rod and one end of the output rod are mutually pivoted The other end of the control rod is pivotally connected to the pivotal portion of the disk, the sliding rod is slidably disposed on the rocker, and the other end of the output rod is connected to the one-way driving portion; One end of the rod is pivotally connected to the pivoting portion of the frame, and the other end is slidably disposed on the guiding groove of the eccentric disk; and the one-way driving portion is configured to rotate the output portion;
Thereby, after the input shaft is driven to rotate, the eccentric disk is driven to rotate eccentrically, so that the N sets of interlocking mechanisms are sequentially operated, and the output portion is linked to rotate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TW100135390A TWI434000B (en) | 2011-09-29 | 2011-09-29 | Connecting rod type stepless speed change device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TW100135390A TWI434000B (en) | 2011-09-29 | 2011-09-29 | Connecting rod type stepless speed change device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| TW201314077A true TW201314077A (en) | 2013-04-01 |
| TWI434000B TWI434000B (en) | 2014-04-11 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| TW100135390A TWI434000B (en) | 2011-09-29 | 2011-09-29 | Connecting rod type stepless speed change device |
Country Status (1)
| Country | Link |
|---|---|
| TW (1) | TWI434000B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105003632A (en) * | 2015-07-10 | 2015-10-28 | 席昊 | Direct mechanical stepless speed changer |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI512219B (en) * | 2014-10-24 | 2015-12-11 | Univ Nat Formosa | Connecting rod type variable speed transmission device |
-
2011
- 2011-09-29 TW TW100135390A patent/TWI434000B/en active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105003632A (en) * | 2015-07-10 | 2015-10-28 | 席昊 | Direct mechanical stepless speed changer |
Also Published As
| Publication number | Publication date |
|---|---|
| TWI434000B (en) | 2014-04-11 |
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