JP4581562B2

JP4581562B2 - Continuously variable transmission

Info

Publication number: JP4581562B2
Application number: JP2004249464A
Authority: JP
Inventors: 祐二下村; 智巳山口; 宏泰吉岡
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2004-02-03
Filing date: 2004-08-30
Publication date: 2010-11-17
Anticipated expiration: 2024-08-30
Also published as: JP2005249184A

Description

この発明は、車両（自動車）用自動変速装置として、或はポンプ等の各種産業機械の運転速度を調節する為の変速装置として利用する、トロイダル型無段変速機と遊星歯車式変速機とを組み合わせた無段変速装置の改良に関する。 The present invention relates to a toroidal continuously variable transmission and a planetary gear type transmission that are used as an automatic transmission for vehicles (automobiles) or as a transmission for adjusting the operating speed of various industrial machines such as pumps. The present invention relates to an improvement of a combined continuously variable transmission.

自動車用自動変速装置としてトロイダル型無段変速機を使用する事が研究され、一部で実施されている。又、トロイダル型無段変速機と遊星歯車式変速機とを組み合わせて無段変速装置を構成する事が、特許文献１〜７に記載されている様に、従来から提案されている。図４は、このうちの特許文献２に記載された無段変速装置を示している。この無段変速装置は、トロイダル型無段変速機１と遊星歯車式変速機２とを組み合わせて成る。このうちのトロイダル型無段変速機１は、入力軸３と、１対の入力側ディスク４、４と、出力側ディスク５と、複数のパワーローラ６、６とを備える。 The use of a toroidal continuously variable transmission as an automatic transmission for automobiles has been studied and implemented in part. In addition, as described in Patent Documents 1 to 7, it has been conventionally proposed to configure a continuously variable transmission by combining a toroidal type continuously variable transmission and a planetary gear type transmission. FIG. 4 shows the continuously variable transmission described in Patent Document 2 among them. This continuously variable transmission is formed by combining a toroidal type continuously variable transmission 1 and a planetary gear type transmission 2. Of these, the toroidal continuously variable transmission 1 includes an input shaft 3, a pair of input side disks 4, 4, an output side disk 5, and a plurality of power rollers 6, 6.

又、上記遊星歯車式変速機２は、上記入力軸３及び一方（図４の右方）の入力側ディスク４に結合固定されたキャリア７を備え、このキャリア７の径方向中間部に、その両端部にそれぞれ遊星歯車８、９を固設した第一伝達軸１０を、回転自在に支持している。又、上記キャリア７を挟んで上記入力軸３と反対側に、その両端部に太陽歯車１１、１２を固設した第二伝達軸１３を、上記入力軸３と同心に、回転自在に支持している。そして、上記各遊星歯車８、９と、上記出力側ディスク５にその基端部（図４の左端部）を結合した中空回転軸１４の先端部（図４の右端部）に固設した太陽歯車１５又は上記第二伝達軸１３の一端部（図４の左端部）に固設した太陽歯車１１とを、それぞれ噛合させている。又、一方（図４の左方）の遊星歯車８を、別の遊星歯車１６を介して、上記キャリア７の周囲に回転自在に設けたリング歯車１７に噛合させている。 The planetary gear type transmission 2 includes a carrier 7 coupled and fixed to the input shaft 3 and one input side disk 4 (right side in FIG. 4). A first transmission shaft 10 having planetary gears 8 and 9 fixed to both ends is rotatably supported. Further, a second transmission shaft 13 having sun gears 11 and 12 fixed to both ends thereof is supported on the opposite side of the input shaft 3 with the carrier 7 interposed therebetween, and is rotatably supported concentrically with the input shaft 3. ing. The planetary gears 8 and 9 and the sun fixed to the distal end portion (the right end portion in FIG. 4) of the hollow rotary shaft 14 whose base end portion (the left end portion in FIG. 4) is coupled to the output side disk 5. The gear 15 or the sun gear 11 fixed to one end (the left end in FIG. 4) of the second transmission shaft 13 is meshed with each other. Further, one (left side in FIG. 4) planetary gear 8 is meshed with a ring gear 17 rotatably provided around the carrier 7 via another planetary gear 16.

一方、上記第二伝達軸１３の他端部（図４の右端部）に固設した太陽歯車１２の周囲に設けた第二キャリア１８に遊星歯車１９、２０を、回転自在に支持している。尚、この第二キャリア１８は、上記入力軸３及び第二伝達軸１３と同心に配置された、出力軸２１の基端部（図４の左端部）に固設されている。又、上記各遊星歯車１９、２０は、互いに噛合すると共に、一方の遊星歯車１９が上記太陽歯車１２に、他方の遊星歯車２０が、上記第二キャリア１８の周囲に回転自在に設けた第二リング歯車２２に、それぞれ噛合している。又、上記リング歯車１７と上記第二キャリア１８とを低速用クラッチ２３により係脱自在とすると共に、上記第二リング歯車２２とハウジング等の固定の部分とを、高速用クラッチ２４により係脱自在としている。 On the other hand, planetary gears 19 and 20 are rotatably supported by a second carrier 18 provided around the sun gear 12 fixed to the other end portion (right end portion in FIG. 4) of the second transmission shaft 13. . The second carrier 18 is fixed to the proximal end portion (left end portion in FIG. 4) of the output shaft 21 that is disposed concentrically with the input shaft 3 and the second transmission shaft 13. The planetary gears 19 and 20 mesh with each other, and one planetary gear 19 is provided in the sun gear 12 and the other planetary gear 20 is provided around the second carrier 18 so as to be rotatable. The ring gears 22 mesh with each other. The ring gear 17 and the second carrier 18 can be freely engaged and disengaged by a low speed clutch 23, and the second ring gear 22 and a fixed portion such as a housing can be freely disengaged by a high speed clutch 24. It is said.

上述の様な、図４に示した無段変速装置の場合、上記低速用クラッチ２３を接続すると共に上記高速用クラッチ２４の接続を断った、所謂低速モード状態では、上記入力軸３の動力が上記リング歯車１７を介して上記出力軸２１に伝えられる。そして、前記トロイダル型無段変速機１の変速比を変える事により、無段変速装置全体としての変速比、即ち、上記入力軸３と上記出力軸２１との間の変速比が変化する。この様な低速モード状態では、無段変速装置全体としての変速比は、無限大に変化する。即ち、上記トロイダル型無段変速機１の変速比を調節する事により、上記入力軸３を一方向に回転させた状態のまま上記出力軸２１の回転状態を、停止状態を挟んで、正転、逆転の変換自在となる。 In the case of the continuously variable transmission shown in FIG. 4 as described above, in the so-called low speed mode state in which the low speed clutch 23 is connected and the high speed clutch 24 is disconnected, the power of the input shaft 3 is reduced. This is transmitted to the output shaft 21 via the ring gear 17. By changing the gear ratio of the toroidal continuously variable transmission 1, the gear ratio of the continuously variable transmission, that is, the gear ratio between the input shaft 3 and the output shaft 21 changes. In such a low speed mode state, the speed ratio of the continuously variable transmission as a whole changes to infinity. That is, by adjusting the gear ratio of the toroidal-type continuously variable transmission 1, the rotation state of the output shaft 21 with the input shaft 3 rotated in one direction is changed between the forward rotation and the rotation state. , Reverse conversion is possible.

これに対して、上記低速用クラッチ２３の接続を断ち、上記高速用クラッチ２４を接続した、所謂高速モード状態では、上記入力軸３の動力が上記第一、第二伝達軸１０、１３を介して上記出力軸２１に伝えられる。そして、上記トロイダル型無段変速機１の変速比を変える事により、無段変速装置全体としての変速比が変化する。この場合には、上記トロイダル型無段変速機１の変速比を大きくする程、無段変速装置全体としての変速比が大きくなる。 On the other hand, in the so-called high speed mode state in which the low speed clutch 23 is disconnected and the high speed clutch 24 is connected, the power of the input shaft 3 is transmitted via the first and second transmission shafts 10 and 13. Is transmitted to the output shaft 21. And the gear ratio as the whole continuously variable transmission changes by changing the gear ratio of the toroidal type continuously variable transmission 1. In this case, the greater the gear ratio of the toroidal continuously variable transmission 1, the greater the gear ratio of the continuously variable transmission as a whole.

又、特願２００３−５６６８１号には、図５に示す様な無段変速装置が開示されている。この図５に示した無段変速装置は、前述の図４に示した従来から知られている無段変速装置と同様の機能を有するものであるが、遊星歯車式変速機２ａ部分の構造を工夫する事により、この遊星歯車式変速機２ａ部分の組立性を向上させている。入力軸３及び１対の入力側ディスク４ａ、４ｂと共に回転するキャリア７ａの両側面に、それぞれ１対ずつの遊星歯車２５ａ、２５ｂ、２６ａ、２６ｂを、回転自在に支持している。そして、上記キャリア７ａの各側面に支持した各遊星歯車２５ａ、２５ｂ同士、各遊星歯車２６ａ、２６ｂ同士を、互いに噛合させると共に、内径側の遊星歯車２５ａ、２６ａを、出力側ディスク５にその基端部（図５の左端部）を結合した中空回転軸１４ａの先端部（図５の右端部）及び伝達軸２７の一端部（図５の左端部）にそれぞれ固設した第一、第二太陽歯車２８、２９に、外径側の遊星歯車２５ｂ、２６ｂをリング歯車３０に、それぞれ噛合させている。 Japanese Patent Application No. 2003-56681 discloses a continuously variable transmission as shown in FIG. The continuously variable transmission shown in FIG. 5 has a function similar to that of the conventionally known continuously variable transmission shown in FIG. 4, but the structure of the planetary gear type transmission 2a portion is the same. By devising, the assemblability of the planetary gear type transmission 2a is improved. A pair of planetary gears 25a, 25b, 26a, and 26b are rotatably supported on both side surfaces of the carrier 7a that rotates together with the input shaft 3 and the pair of input side disks 4a and 4b. Then, the planetary gears 25a and 25b supported on the side surfaces of the carrier 7a and the planetary gears 26a and 26b are meshed with each other, and the planetary gears 25a and 26a on the inner diameter side are connected to the output side disk 5 on the basis thereof. First and second fixed respectively to the tip end portion (right end portion in FIG. 5) of the hollow rotary shaft 14a joined to the end portion (left end portion in FIG. 5) and one end portion (left end portion in FIG. 5) of the transmission shaft 27. The planetary gears 25b and 26b on the outer diameter side are engaged with the ring gear 30 and the sun gears 28 and 29, respectively.

一方、上記伝達軸２７の他端部（図５の右端部）に固設した第三太陽歯車３１の周囲に設けた第二キャリア１８ａに遊星歯車３２ａ、３２ｂを、回転自在に支持している。尚、この第二キャリア１８ａは、上記入力軸３と同心に配置された出力軸２１ａの基端部（図５の左端部）に固設されている。又、上記各遊星歯車３２ａ、３２ｂは、互いに噛合すると共に、内径側の遊星歯車３２ａを上記第三太陽歯車３１に、外径側の遊星歯車３２ｂを、上記第二キャリア１８ａの周囲に回転自在に設けた第二リング歯車２２ａに、それぞれ噛合させている。又、上記リング歯車３０と上記第二キャリア１８ａとを低速用クラッチ２３ａにより係脱自在とすると共に、上記第二リング歯車２２ａとハウジング等の固定の部分とを、高速用クラッチ２４ａにより係脱自在としている。 On the other hand, the planetary gears 32a and 32b are rotatably supported by the second carrier 18a provided around the third sun gear 31 fixed to the other end portion (the right end portion in FIG. 5) of the transmission shaft 27. . The second carrier 18a is fixed to the base end portion (left end portion in FIG. 5) of the output shaft 21a arranged concentrically with the input shaft 3. The planetary gears 32a and 32b mesh with each other, and the planetary gear 32a on the inner diameter side is rotatable around the third sun gear 31 and the planetary gear 32b on the outer diameter side is rotatable around the second carrier 18a. Are respectively meshed with the second ring gear 22a. Further, the ring gear 30 and the second carrier 18a can be engaged and disengaged by a low speed clutch 23a, and the second ring gear 22a and a fixed part such as a housing can be engaged and disengaged by a high speed clutch 24a. It is said.

この様に構成する改良された無段変速装置の場合、上記低速用クラッチ２３ａを接続し、上記高速用クラッチ２４ａの接続を断った状態では、上記入力軸３の動力が、上記リング歯車３０を介して上記出力軸２１ａに伝えられる。そして、トロイダル型無段変速機１の変速比を変える事により、無段変速装置全体としての変速比、即ち、上記入力軸３と上記出力軸２１ａとの間の変速比が変化する。これに対して、上記低速用クラッチ２３ａの接続を断ち、上記高速用クラッチ２４ａを接続した状態では、上記入力軸３の動力が、前記各遊星歯車２５ａ、２５ｂ、上記リング歯車３０、前記各遊星歯車２６ａ、２６ｂ、前記伝達軸２７、前記各遊星歯車３２ａ、３２ｂ、上記第二キャリア１８ａを介して、上記出力軸２１ａに伝えられる。そして、上記トロイダル型無段変速機１の変速比を変える事により、無段変速装置全体としての変速比が変化する。 In the case of the improved continuously variable transmission configured as described above, the power of the input shaft 3 causes the ring gear 30 to be driven when the low speed clutch 23a is connected and the high speed clutch 24a is disconnected. Via the output shaft 21a. By changing the gear ratio of the toroidal-type continuously variable transmission 1, the gear ratio of the continuously variable transmission, that is, the gear ratio between the input shaft 3 and the output shaft 21a changes. On the other hand, when the low speed clutch 23a is disconnected and the high speed clutch 24a is connected, the power of the input shaft 3 is applied to the planetary gears 25a, 25b, the ring gear 30, and the planetary gears. It is transmitted to the output shaft 21a through the gears 26a and 26b, the transmission shaft 27, the planetary gears 32a and 32b, and the second carrier 18a. And the gear ratio as the whole continuously variable transmission changes by changing the gear ratio of the toroidal type continuously variable transmission 1.

尚、次述する図６〜７に示す様に、外径側の遊星歯車２５として、軸方向寸法が長いものを使用すると共に、この長い遊星歯車２５を内径側の遊星歯車２５ａ、２６ａ及びリング歯車３０ａに噛合させる構造を採用しても、同様の機能を発揮できる。この場合には、直径の大きなリング歯車３０ａの軸方向寸法を短縮して、遊星歯車式変速機２ｂの軽量化を図れる。 As shown in FIGS. 6 to 7 to be described below, as the planetary gear 25 on the outer diameter side, one having a long axial dimension is used, and this long planetary gear 25 is used as the planetary gears 25a and 26a on the inner diameter side and the ring. The same function can be exhibited even if a structure for meshing with the gear 30a is employed. In this case, the axial dimension of the ring gear 30a having a large diameter can be shortened to reduce the weight of the planetary gear type transmission 2b.

前述した図４及び上述した図５の構造は、原理的なもので、具体的な構造を示したものではない。これに対して図６〜７は、先に考えた無段変速装置の具体的構造の１例を示している。尚、この構造では、上述した様に、外径側の遊星歯車２５として軸方向寸法が長いものを使用すると共に、この長い遊星歯車２５を、内径側の遊星歯車２５ａ、２６ａ及びリング歯車３０ａに噛合させている。 The structures shown in FIGS. 4 and 5 described above are fundamental and do not show a specific structure. On the other hand, FIGS. 6 to 7 show an example of a specific structure of the continuously variable transmission considered above. In this structure, as described above, the planetary gear 25 on the outer diameter side having a long axial dimension is used, and the long planetary gear 25 is used as the planetary gears 25a and 26a and the ring gear 30a on the inner diameter side. Meshing.

ハウジング３３内の所定位置に１対の支柱３４、３４を、連結板３５とバルブボディー３６とを介して支持固定している。このバルブボディー３６は、トロイダル型無段変速機１の変速比を制御する為の制御弁装置を内蔵している。又、上記各支柱３４、３４の両端部には、パワーローラ６、６（図４参照）を支持するトラニオンの両端部を揺動及び軸方向の変位自在に支持する為の支持板３７、３７を支持している。又、環状に形成した上記各支柱３４、３４の中間部同士の間に出力側ディスク５を、１対の転がり軸受３８、３８により、回転自在に支持している。そして、上記出力側ディスク５の内径側に中空回転軸１４ａの基半部（図６の左半部）を、スプライン係合に基づき、回転伝達自在に結合している。 A pair of support columns 34 are supported and fixed at predetermined positions in the housing 33 via a connecting plate 35 and a valve body 36. The valve body 36 incorporates a control valve device for controlling the gear ratio of the toroidal type continuously variable transmission 1. Further, support plates 37, 37 for supporting both ends of the trunnion supporting the power rollers 6, 6 (see FIG. 4) so as to swing and displace in the axial direction are provided at both ends of each of the columns 34, 34. Support. Further, the output side disk 5 is rotatably supported by a pair of rolling bearings 38, 38 between the intermediate portions of the respective pillars 34, 34 formed in an annular shape. And the base half part (left half part of FIG. 6) of the hollow rotating shaft 14a is coupled to the inner diameter side of the output side disk 5 based on the spline engagement so as to be able to transmit the rotation.

そして上記中空回転軸１４ａの内側に、入力軸３ａを挿通している。この入力軸３ａの中間部基端寄り部分に一方（図６の左方）の入力側ディスク４ａを、ボールスプライン３９を介して支持すると共に、油圧式の押圧装置４０により上記入力側ディスク４ａを、上記出力側ディスク５に向け、押圧自在としている。これに対して他方（図６の右方）の入力側ディスク４ｂは上記中空回転軸１４ａの中間部先端寄り（図６の右寄り）部分の周囲に、ラジアルニードル軸受４１により、回転及び軸方向の変位自在に支持している。そして、上記他方の入力側ディスク４ｂと上記入力軸３ａとを、キャリア７ａを介して結合している。従って、上記出力側ディスク５を軸方向両側から挟む位置に設けた１対の入力側ディスク４ａ、４ｂは、上記入力軸３ａと上記キャリア７ａとを介して、同期して回転する。 The input shaft 3a is inserted inside the hollow rotary shaft 14a. One input side disk 4a (left side in FIG. 6) is supported via a ball spline 39 near the base end of the input shaft 3a, and the input side disk 4a is supported by a hydraulic pressing device 40. The output side disk 5 can be pressed freely. On the other hand, the other input side disk 4b (on the right side in FIG. 6) is rotated and axially moved by a radial needle bearing 41 around the middle tip end (right side in FIG. 6) of the hollow rotary shaft 14a. Supports displaceability. The other input side disk 4b and the input shaft 3a are coupled via a carrier 7a. Accordingly, the pair of input side disks 4a and 4b provided at the positions sandwiching the output side disk 5 from both sides in the axial direction rotate synchronously via the input shaft 3a and the carrier 7a.

上記キャリア７ａは、図７〜８に詳示する様に、断面Ｌ字形で全体を円環状とした中間支持板４２と、それぞれが円輪状に形成された第一、第二両連結板４３、４４との間に、それぞれ複数本ずつ（例えば３本ずつ）の第一、第二各遊星軸４５、４６を、上記第一、第二両連結板４３、４４同士の間に複数本（例えば３本）の第三遊星軸４７を、それぞれ掛け渡して成る。又、これら各遊星軸４５〜４７の周囲に前記各遊星歯車２５ａ、２６ａ、２５を、それぞれラジアルニードル軸受４８ａ、４８ｂ、４８ｃを介して、回転自在に支持している。そして、外径側の遊星歯車２５と内径側の各遊星歯車２５ａ、２６ａとを互いに噛合させると共に、内径側の遊星歯車２５ａ、２６ａを、上記中空回転軸１４ａの先端部（図６〜７の右端部）に固設した第一太陽歯車２８又は伝達軸２７の基端部に固設した第二太陽歯車２９に、外径側の遊星歯車２５を前記リング歯車３０ａに、それぞれ噛合させている。 As shown in detail in FIGS. 7 to 8, the carrier 7 a includes an intermediate support plate 42 having an L-shaped cross section and an annular shape as a whole, and first and second connecting plates 43 each formed in an annular shape. A plurality of (for example, three) first and second planetary shafts 45 and 46 are respectively provided between the first and second connecting plates 43 and 44 (for example, three). 3) third planetary shafts 47 are spanned over each other. The planetary gears 25a, 26a, 25 are rotatably supported around the planetary shafts 45-47 via radial needle bearings 48a, 48b, 48c, respectively. Then, the planetary gear 25 on the outer diameter side and the planetary gears 25a and 26a on the inner diameter side are meshed with each other, and the planetary gears 25a and 26a on the inner diameter side are connected to the tip of the hollow rotary shaft 14a (see FIGS. 6 to 7). The planetary gear 25 on the outer diameter side is meshed with the ring gear 30a to the first sun gear 28 fixed to the right end portion) or the second sun gear 29 fixed to the base end portion of the transmission shaft 27, respectively. .

又、上記中間支持板４２の中心に設けた円筒部４９は、上記入力軸３ａの中間部先端寄り部分にスプライン係合させ、ローディングナット５０により抑え付けている。尚、図８に示す様に、上記中間支持板４２の円輪部５１と上記第一、第二各連結板４３、４４とは、前記各遊星歯車２５ａ、２６ａ、２５から円周方向に外れた位置に設けた連結部５９、５９により、互いに連結している。図示の例の場合、上記キャリア７ａを構成する上記中間支持板４２と、第一、第二各連結板４３、４４と、上記各連結部５９、５９とを、一体に形成している。そしてこの構成により、上記キャリア７ａの、回転伝達方向の力に対する強度及び剛性を確保している。又、前記他方の入力側ディスク４ｂと上記キャリア７ａとの間での回転伝達を行なわせるべく、この他方の入力側ディスク４ｂの外側面複数個所に形成した凸部５２と、上記第一連結板４３の外周縁部に形成した切り欠き５３とを係合させている。又、運転時には、駆動軸５４により上記入力軸３ａを回転駆動する。同時に、前記押圧装置４０に油圧を導入して、各入力側ディスク４ａ、４ｂ及び出力側ディスク５の側面と各パワーローラ６、６の周面との転がり接触部（トラクション部）の面圧を確保する。 A cylindrical portion 49 provided at the center of the intermediate support plate 42 is spline-engaged with a portion closer to the front end of the intermediate portion of the input shaft 3 a and is held down by a loading nut 50. As shown in FIG. 8, the annular portion 51 of the intermediate support plate 42 and the first and second connecting plates 43, 44 are disengaged from the planetary gears 25a, 26a, 25 in the circumferential direction. They are connected to each other by connecting portions 59, 59 provided at different positions. In the case of the illustrated example, the intermediate support plate 42 constituting the carrier 7a, the first and second connecting plates 43 and 44, and the connecting portions 59 and 59 are integrally formed. And by this structure, the intensity | strength and rigidity with respect to the force of the rotation transmission direction of the said carrier 7a are ensured. Further, in order to transmit the rotation between the other input side disk 4b and the carrier 7a, convex portions 52 formed at a plurality of locations on the outer side surface of the other input side disk 4b, and the first connecting plate A notch 53 formed on the outer peripheral edge portion of 43 is engaged. Further, during operation, the input shaft 3a is rotationally driven by the drive shaft 54. At the same time, hydraulic pressure is introduced into the pressing device 40, and the surface pressure of the rolling contact portion (traction portion) between the side surfaces of the input side disks 4a, 4b and the output side disk 5 and the peripheral surfaces of the power rollers 6, 6 is adjusted. Secure.

上述の様な図６〜７に示す無段変速装置の場合、他方の入力側ディスク４ｂとキャリア７ａとの間の回転伝達を、凸部５２と切り欠き５３との凹凸係合により行なっている。又、トラクション部の面圧を確保する為に押圧装置４０の発生する推力は、入力軸３ａ及びこの入力軸３ａに固定したキャリア７ａを構成する中間支持板４２、第一連結板４３を介して、上記他方の入力側ディスク４ｂに加わる。言い換えれば、この他方の入力側ディスク４ｂの外側面（図６〜７の右側面）と第一連結板４３の片側面（図６〜８の左側面）との当接部である、これら入力側ディスク４ｂ及び第一連結板４３の径方向中間部（図７にｗで表わす部分を入力側ディスク４ｂ及び第一連結板４３の中心軸αを中心に回転させてできる円輪状部分）に、上記押圧装置４０の発生する推力に基づく力が加わる。 In the case of the continuously variable transmission shown in FIGS. 6 to 7 as described above, the rotation transmission between the other input side disk 4 b and the carrier 7 a is performed by the concave and convex engagement between the convex portion 52 and the notch 53. . Further, the thrust generated by the pressing device 40 in order to ensure the surface pressure of the traction portion is transmitted through the input shaft 3a and the intermediate support plate 42 and the first connecting plate 43 constituting the carrier 7a fixed to the input shaft 3a. To the other input side disk 4b. In other words, these inputs are the contact portions between the outer side surface of the other input side disk 4b (the right side surface in FIGS. 6 to 7) and one side surface of the first connecting plate 43 (the left side surface in FIGS. 6 to 8). In the radial intermediate portion of the side disk 4b and the first connecting plate 43 (an annular portion formed by rotating the portion represented by w in FIG. 7 around the central axis α of the input side disk 4b and the first connecting plate 43), A force based on the thrust generated by the pressing device 40 is applied.

一方、上記他方の入力側ディスク４ｂは、上記押圧装置４０の発生する推力に基づく上記パワーローラ６、６から受ける力に基づいて、図９に誇張して示す様に、この入力側ディスク４ｂの外径寄り部分が上記第一連結板４３の片側面に近付く方向（軸方向）に弾性変形する。即ち、運転時に上記推力に基づき上記他方の入力側ディスク４ｂに加わる力は、トロイダル型無段変速機の運転時に最大で５ｔ（トン）程度となり、この様な力に基づく入力側ディスク４ｂの軸方向に関する弾性変形量は、コンマ数mm（１０分の数mm）程度と無視できない量となる。そして、この様に他方の入力側ディスク４ｂが軸方向に弾性変形すると、この他方の入力側ディスク４ｂの外側面外径寄り部分と上記第一連結板４３の片側面とが断続的に繰り返し当接する事で互いに擦れ合い、当該部分でフレッチング摩耗が生じる可能性がある。特に、上記入力ディスク４ｂが弾性変形する円周方向位置は、上記各パワーローラ６、６により押し付けられる部分が変化するのに伴って常に変化する。この為、上記擦れ合いの周波数は相当に高く（例えば百数十Ｈｚに）なり、フレッチング摩耗発生の面からはかなり厳しい条件となる。この様なフレッチング摩耗は、上記キャリア７ａを所定位置から軸方向にずらせたり、剥離等の損傷の起点となる可能性がある。又、発生した摩耗粉が潤滑油（トラクションオイル）を汚染し、各部の潤滑状態を不良にする可能性もある。 On the other hand, the other input side disk 4b is formed on the input side disk 4b as shown in an exaggerated manner in FIG. 9 based on the force received from the power rollers 6 and 6 based on the thrust generated by the pressing device 40. The portion closer to the outer diameter is elastically deformed in a direction (axial direction) approaching one side surface of the first connecting plate 43. That is, the force applied to the other input side disk 4b based on the thrust during operation is about 5 t (tons) at the maximum during the operation of the toroidal continuously variable transmission, and the shaft of the input side disk 4b based on such a force. The amount of elastic deformation with respect to the direction is a comma number of mm (a few tenths of a millimeter) and cannot be ignored. When the other input side disk 4b is elastically deformed in the axial direction in this way, the outer surface of the other input side disk 4b and the one side surface of the first connecting plate 43 are repeatedly and repeatedly applied. When they come into contact with each other, they rub against each other, and there is a possibility that fretting wear will occur at those portions. In particular, the circumferential position at which the input disk 4b is elastically deformed always changes as the portions pressed by the power rollers 6 and 6 change. For this reason, the frequency of the rubbing is considerably high (for example, hundreds of tens Hz), which is a severe condition in terms of occurrence of fretting wear. Such fretting wear may cause the carrier 7a to shift in the axial direction from a predetermined position, or may be a starting point of damage such as peeling. In addition, the generated wear powder may contaminate the lubricating oil (traction oil), resulting in poor lubrication of each part.

特開平６−１７４０３３号公報JP-A-6-174033 特開２０００−２２０７１９号公報JP 2000-220719 A 特開２００２−１３９１２４号公報JP 2002-139124 A 米国特許第５６０７３７２号明細書US Pat. No. 5,607,372 米国特許第６０５９６８５号明細書US Pat. No. 6,059,658 米国特許第６０９９４３１号明細書US Pat. No. 6,099,431 米国特許第６３５８１７８号明細書US Pat. No. 6,358,178

本発明は、上述の様な事情に鑑みて、入力側ディスクの軸方向の弾性変形に基づくフレッチング摩耗を防止できる構造を実現すべく発明したものである。 The present invention was invented to realize a structure capable of preventing fretting wear based on the elastic deformation in the axial direction of the input side disk in view of the above-described circumstances.

本発明の無段変速装置は何れも、互いに同心に配置された、入力軸と、出力軸と、トロイダル型無段変速機と、遊星歯車式変速機とを備える。
そして、これらトロイダル型無段変速機と遊星歯車式変速機とは、トロイダル型無段変速機を構成する入力側ディスクと遊星歯車式変速機を構成するキャリアとを隣接させると共に、これら入力側ディスクとキャリアとが同期して回転する状態に組み合わされている。
又、上記キャリアは、上記入力軸に支持固定された支持板と、この支持板と同心に且つ軸方向に間隔をあけた状態で配置され、その側面を上記入力側ディスクの外側面に対向させた、円輪状である連結板と、この連結板と上記支持板とにそれぞれの両端部を支持された複数の遊星軸とを備えたものである。
そして、上記遊星歯車式変速機を構成する遊星歯車を、上記各遊星軸の周囲に回転自在に支持している。
特に、本発明のうちの請求項１に記載した無段変速装置に於いては、互いに対向する上記連結板の片側面と上記入力側ディスクの外側面とを、黄銅等の銅系合金製で円輪状のスペーサを介して突き当てている。
又、請求項５に記載した無段変速装置の場合には、互いに対向する上記連結板の片側面と上記入力側ディスクの外側面とを円輪状のスペーサを介して突き当てると共に、互いに当接する上記連結板の片側面とこのスペーサの片面とを、何れも表面粗さ（算術平均粗さ）がＲａ１２．５μｍ以下の平滑面としている。 Each of the continuously variable transmissions of the present invention includes an input shaft, an output shaft, a toroidal continuously variable transmission, and a planetary gear transmission that are concentrically arranged.
The toroidal type continuously variable transmission and the planetary gear type transmission include an input side disk constituting the toroidal type continuously variable transmission and a carrier constituting the planetary gear type transmission, and these input side disks. And the carrier are rotated in a synchronized manner.
The carrier is disposed with a support plate supported and fixed to the input shaft, concentric with the support plate and spaced apart in the axial direction, with the side surface facing the outer surface of the input side disk. In addition, a connecting plate having an annular shape and a plurality of planetary shafts supported at both ends by the connecting plate and the support plate are provided.
And the planetary gear which comprises the said planetary gear type transmission is rotatably supported around each said planetary shaft.
In particular, in the continuously variable transmission according to claim 1 of the present invention, the one side surface of the coupling plate and the outer side surface of the input side disk facing each other are made of a copper-based alloy such as brass. It abuts through an annular spacer.
In the case of the continuously variable transmission according to claim 5, one side surface of the connecting plate and the outer side surface of the input-side disk that are opposed to each other are abutted through an annular spacer and abut against each other. One side of the connecting plate and one side of the spacer are both smooth surfaces with a surface roughness (arithmetic average roughness) of Ra 12.5 μm or less.

上述の様に構成する本発明の無段変速装置によれば、入力側ディスクの軸方向の弾性変形に基づくフレッチング摩耗を防止できる。
即ち、本発明のうちの請求項１に記載した無段変速装置の場合には、連結板の片側面と入力側ディスクの外側面とを銅系合金製で円輪状のスペーサを介して突き当てている。黄銅等の銅系合金は、上記連結板や入力側ディスクを構成する、炭素鋼や軸受鋼等の鉄系合金と接触した状態で、優れた自己潤滑性（摺動特性）を発揮する。この為、入力側ディスクの弾性変形に伴って上記両側面同士が擦れ合った場合でも、これら両側面に著しいフレッチング摩耗が発生する事を防止できる。 According to the continuously variable transmission of the present invention configured as described above, fretting wear due to elastic deformation in the axial direction of the input side disk can be prevented.
That is, in the case of the continuously variable transmission according to claim 1 of the present invention, the one side surface of the connecting plate and the outer side surface of the input side disk are abutted via a ring-shaped spacer made of a copper alloy. ing. Copper-based alloys such as brass exhibit excellent self-lubricating properties (sliding characteristics) in contact with iron-based alloys such as carbon steel and bearing steel that constitute the connecting plate and the input side disk. For this reason, even when the both side surfaces are rubbed with each other due to the elastic deformation of the input side disk, it is possible to prevent the occurrence of significant fretting wear on both side surfaces.

又、請求項５に記載した無段変速装置の場合には、互いに当接する連結板の片側面とスペーサの片面との間に、良好な油膜を形成できる。即ち、これら両面の面粗度が不良である（表面粗さの値がＲａ１２．５μｍよりも大きい）と、当接部の面圧が局部的に過大になって当該部分で油膜切れが発生し、この部分でフレッチング摩耗を生じ易くなる。そして、フレッチング摩耗の結果、上記スペーサに割れ等の損傷が発生したり、発生した摩耗粉が潤滑油（トラクションオイル）中に混入して、上記当接部以外の、広範な部分の潤滑を不良にする可能性がある。これに対して請求項５に記載した無段変速装置の場合には、上記連結板の片側面とスペーサの片面とを、何れも表面粗さがＲａ１２．５μｍ以下の平滑面としている為、これら両面同士の間に良好な油膜を形成して、上記フレッチング摩耗に結び付く油膜切れの発生を防止できる。尚、請求項５に記載した無段変速装置装置を実施する場合に、上記スペーサの材質は、必要とする強度を得られる限り、特に問わないが、好ましくは、請求項１に記載した発明と同様に、銅系合金とする。 In the case of the continuously variable transmission according to the fifth aspect, a good oil film can be formed between one side surface of the connecting plate and one side surface of the spacer which are in contact with each other. That is, if the surface roughness of these two surfaces is poor (the value of the surface roughness is larger than Ra 12.5 μm), the surface pressure of the abutting portion becomes locally excessive and the oil film is cut off at that portion. In this part, fretting wear tends to occur. As a result of fretting wear, damage such as cracking occurs in the spacer, or the generated wear powder mixes in the lubricating oil (traction oil), resulting in poor lubrication of a wide range of parts other than the contact part. There is a possibility. On the other hand, in the case of the continuously variable transmission according to claim 5, since one side of the connecting plate and one side of the spacer are both smooth surfaces with a surface roughness of Ra 12.5 μm or less, these By forming a good oil film between both surfaces, it is possible to prevent the occurrence of oil film breakage that leads to the fretting wear. In addition, when implementing the continuously variable transmission apparatus according to claim 5, the material of the spacer is not particularly limited as long as the necessary strength can be obtained. Similarly, a copper alloy is used.

本発明のうちの請求項１に記載した発明を実施する場合に好ましくは、請求項２に記載した様に、スペーサの軸方向側面（少なくとも片側面、好ましくは両側面）に、多数の微小凹部を形成する。或は、請求項３に記載した様に、複数の放射状凹溝を形成する。或は、請求項４に記載した様に、環状凹溝を形成する。
上記スペーサの軸方向側面に上述の様な凹部若しくは凹溝を形成すれば、互いに当接するスペーサの軸方向側面と連結板の片側面又は入力側ディスクの外側面との間に潤滑剤を効果的に送り込み、これら互いに当接する側面同士の当接部で、フレッチング摩耗に結び付く油膜切れが発生する事を有効に防止できる。 When carrying out the invention described in claim 1 of the present invention, preferably, as described in claim 2, a large number of minute recesses are formed on the axial side surface (at least one side surface, preferably both side surfaces) of the spacer. Form. Alternatively, as described in claim 3, a plurality of radial concave grooves are formed. Alternatively, as described in claim 4, an annular groove is formed.
By forming the above-described recess or groove on the side surface in the axial direction of the spacer, it is effective to apply a lubricant between the side surface in the axial direction of the spacer that contacts each other and one side surface of the connecting plate or the outer side surface of the input side disk. It is possible to effectively prevent the occurrence of oil film breakage that leads to fretting wear at the contact portions of the side surfaces that are in contact with each other.

又、請求項５に記載した発明を実施する場合に好ましくは、請求項６に記載した様に、互いに当接する連結板の片側面とスペーサの片面とを、研磨加工により平滑面とする。研磨加工による平滑面同士の当接部には、良好な油膜が形成され易く、上記フレッチング摩耗の防止効果がより優れたものとなる。
又、請求項５に記載した発明を実施する場合に好ましくは、請求項７に記載した様に、互いに当接する連結板の片側面とスペーサの片面とを平滑面とする事に加えて、互いに当接する入力側ディスクの外側面とスペーサの他面とを、何れも表面粗さがＲａ１２．５μｍ以下の平滑面とする。この様に構成すれば、上記スペーサの両面と、それぞれの相手面との間に、それぞれ良好な油膜を形成して、このスペーサの耐久性をより一層向上させる事ができる。
又、本発明を実施する場合に好ましくは、請求項８に記載した様に、支持板と連結板とを一体に形成する。この様に構成すれば、キャリアの強度及び剛性を確保しつつ、部品点数の低減による製造コストの低減を図れる。
更に、本発明を実施する場合に好ましくは、請求項９に記載した様に、上記スペーサの円周方向複数個所に、それぞれがこのスペーサの径方向中間部から外周縁に迄達するスリットを形成し、このスペーサの径方向中間部乃至外周縁部を、厚さ方向に変形し易くする。この様に構成すれば、上記入力側ディスクの外側面のうちで、軸方向に関する変形量が大きくなる外径寄り部分に当接する、上記スペーサの外径寄り部分を、上記入力側ディスクの弾性変形に伴って変形し易くできる。この為、この入力側ディスクの弾性変形に伴って、上記スペーサに無理な力が加わりにくくして、このスペーサに、有害な塑性変形を生じる事を防止できる。 Further, when carrying out the invention described in claim 5, preferably, as described in claim 6, one side surface of the connecting plate and one side surface of the spacer which are in contact with each other are made smooth by polishing. A good oil film is easily formed on the contact portion between the smooth surfaces by the polishing process, and the effect of preventing the fretting wear is more excellent.
Further, when the invention described in claim 5 is carried out, preferably, as described in claim 7, in addition to making one side of the connecting plate and one side of the spacer in contact with each other smooth, Both the outer surface of the input side disk and the other surface of the spacer that are in contact with each other are smooth surfaces with a surface roughness of Ra 12.5 μm or less. If comprised in this way, a favorable oil film can be formed between the both surfaces of the said spacer and each other surface, respectively, and the durability of this spacer can be improved further.
Further, when implementing the present invention, preferably, as described in claim 8, the support plate and the connecting plate are integrally formed. If comprised in this way, the manufacturing cost can be reduced by reducing the number of parts while ensuring the strength and rigidity of the carrier.
Furthermore, when the present invention is carried out, preferably, as described in claim 9, slits are formed at a plurality of circumferential positions of the spacer so as to reach the outer peripheral edge from the radial intermediate portion of the spacer. The intermediate portion or outer peripheral portion of the spacer in the radial direction is easily deformed in the thickness direction. If comprised in this way, the outer diameter side part of the said spacer which contact | abuts the outer diameter side part where the deformation amount regarding an axial direction becomes large among the outer surfaces of the said input side disk will be elastically deformed of the said input side disk. As a result, it can be easily deformed. For this reason, with the elastic deformation of the input side disk, it is difficult to apply an excessive force to the spacer, and it is possible to prevent the spacer from causing harmful plastic deformation.

図１〜２は、本発明の実施例１を示している。尚、本実施例の特徴は、他方の入力側ディスク４ｂの外側面（図１の右側面）とキャリア７ａを構成する第一連結板４３の片側面（図１の左側面）との間に、黄銅等の銅系合金製で円輪状のスペーサ５５を挟持する事により、これら入力側ディスク４ｂの外側面と第一連結板４３の片側面とのフレッチング摩耗を防止する点にある。その他の部分の構造及び作用は、前述の図６〜８に示した先発明に係る構造と同様であるから、同等部分に関する図示並びに説明は、省略若しくは簡略にし、以下、本発明の特徴部分を中心に説明する。 1 and 2 show Embodiment 1 of the present invention. The feature of this embodiment is that it is between the outer side surface (the right side surface in FIG. 1) of the other input side disk 4b and one side surface (the left side surface in FIG. 1) of the first connecting plate 43 constituting the carrier 7a. By sandwiching an annular spacer 55 made of a copper alloy such as brass, fretting wear between the outer side surface of the input side disk 4b and one side surface of the first connecting plate 43 is prevented. Since the structure and operation of the other parts are the same as the structure according to the prior invention shown in FIGS. 6 to 8 described above, the illustration and description of the equivalent parts are omitted or simplified. Hereinafter, the characteristic parts of the present invention will be described. I will explain it mainly.

上記他方の入力側ディスク４ｂの外側面（図１の右側面）とキャリア７ａを構成する第一連結板４３の片側面（図１の左側面）との間に、黄銅等の銅系合金製で円輪状のスペーサ５５を挟持している。このスペーサ５５の軸方向側面（少なくとも片側面、好ましくは両側面）には、潤滑油（トラクションオイル）を捕集し更に保持する為の保油凹部を形成している。この様な保油凹部としては、例えば図２に示す様な構造が使用可能である。このうちの（Ａ）に示した構造は、上記軸方向片側面に多数の微小凹部５６、５６を形成したもの、（Ｂ）に示した構造は、複数の放射状凹溝５７、５７を形成したもの、（Ｃ）に示した構造は、同心円状の複数の環状凹溝５８ａ、５８ｂを形成したものである。 Between the outer side surface (right side surface in FIG. 1) of the other input side disk 4b and one side surface (left side surface in FIG. 1) of the first connecting plate 43 constituting the carrier 7a, made of a copper alloy such as brass. An annular spacer 55 is sandwiched between the two. An oil retaining recess for collecting and holding lubricating oil (traction oil) is formed on the axial side surface (at least one side surface, preferably both side surfaces) of the spacer 55. As such an oil retaining recess, for example, a structure as shown in FIG. 2 can be used. Of these, the structure shown in (A) is a structure in which a large number of minute recesses 56, 56 are formed on one side surface in the axial direction, and the structure shown in (B) is formed with a plurality of radial recess grooves 57, 57. The structure shown in FIG. 5C is a structure in which a plurality of concentric annular grooves 58a and 58b are formed.

上述の様に構成する本実施例の無段変速装置によれば、上記他方の入力側ディスク４ｂが、前述の図９に示す様に軸方向に弾性変形しても、このディスク４ｂの外側面や、上記第一連結板４３の片側面が、フレッチング摩耗する事を防止できる。
即ち、本実施例の無段変速装置の場合には、上記第一連結板４３の片側面と上記他方の入力側ディスク４ｂの外側面とを、銅系合金製で円輪状のスペーサ５５を介して突き当てている。黄銅等の銅系合金は、上記第一連結板４３や上記他方の入力側ディスク４ｂを構成する、炭素鋼や軸受鋼等の鉄系合金と接触した状態で、優れた自己潤滑性（摺動特性）を発揮する。この為、上記他方の入力側ディスク４ｂの弾性変形に伴って上記両側面同士が擦れ合った場合でも、これら両側面に著しいフレッチング摩耗が発生する事を防止できる。 According to the continuously variable transmission of this embodiment configured as described above, even if the other input side disk 4b is elastically deformed in the axial direction as shown in FIG. 9, the outer surface of the disk 4b. In addition, fretting wear on one side surface of the first connecting plate 43 can be prevented.
That is, in the case of the continuously variable transmission according to the present embodiment, one side surface of the first connecting plate 43 and the outer side surface of the other input side disk 4b are connected via an annular spacer 55 made of a copper alloy. I bumped. Copper-based alloys such as brass have excellent self-lubricating properties (sliding) in contact with iron-based alloys such as carbon steel and bearing steel constituting the first connecting plate 43 and the other input side disk 4b. Characteristics). For this reason, even when the both side surfaces rub against each other with the elastic deformation of the other input side disk 4b, it is possible to prevent the occurrence of significant fretting wear on both side surfaces.

更に、本実施例の場合には、上記スペーサ５５の軸方向側面に上述の様な微小凹部５６、５６、放射状凹溝５７、５７、環状凹溝５８ａ、５８ｂ等の保油凹部を形成しているので、互いに当接する上記スペーサ５５の軸方向側面と、上記第一連結板４３の片側面又は上記他方の入力側ディスク４ｂの外側面との間に潤滑剤を効果的に送り込める。即ち、トロイダル型無段変速機を備えた無段変速装置の運転時に、ハウジング３３（図６参照）内には、潤滑剤としての役目も備えたトラクションオイルの飛沫が無数に浮遊している。この様なトラクションオイルの飛沫は、上記スペーサ５５の軸方向側面と、上記第一連結板４３の片側面又は上記他方の入力側ディスク４ｂの外側面との間に入り込み、上記保油凹部に捕集される。そして、この様な保油凹部内に捕集されたトラクションオイルは、上記スペーサ５５の側面と、第一連結板４３の片側面又は上記他方の入力側ディスク４ｂの外側面との微小変位に伴って、これら互いに当接する側面同士の間に染み出す。この結果、これら互いに当接する側面同士の当接部で、フレッチング摩耗に結び付く油膜切れが発生する事を有効に防止できる。 Further, in the case of this embodiment, oil retaining recesses such as the minute recesses 56 and 56, the radial recess grooves 57 and 57, and the annular recess grooves 58a and 58b as described above are formed on the side surface in the axial direction of the spacer 55. Therefore, the lubricant can be effectively fed between the side surface in the axial direction of the spacer 55 that contacts each other and the outer surface of the one side surface of the first connecting plate 43 or the other input side disk 4b. That is, when the continuously variable transmission including the toroidal continuously variable transmission is operated, countless splashes of traction oil that also serves as a lubricant are floating in the housing 33 (see FIG. 6). Such splash of traction oil enters between the axial side surface of the spacer 55 and the one side surface of the first connecting plate 43 or the outer side surface of the other input side disk 4b, and is trapped in the oil retaining recess. Be collected. The traction oil collected in such an oil retaining recess is accompanied by a minute displacement between the side surface of the spacer 55 and one side surface of the first connecting plate 43 or the outer side surface of the other input side disk 4b. And ooze out between the side surfaces that are in contact with each other. As a result, it is possible to effectively prevent the occurrence of oil film breakage associated with fretting wear at the abutting portions between the side surfaces that abut each other.

尚、上記フレッチング摩耗に結び付く油膜切れをより有効に防止する為には、上記スペーサ５５の軸方向片側面と上記第一連結板４３の片側面とを、何れも表面粗さがＲａ１２．５μｍ以下の平滑面とする。更に好ましくは、上記スペーサ５５の軸方向他側面と上記入力側ディスク４ｂの外側面とも、何れも表面粗さがＲａ１２．５μｍ以下の平滑面とする。この場合に平滑面とする部分は、図２に示した微小凹部５６、５６、放射状凹溝５７、５７、環状凹溝５８ａ、５８ｂから外れた平坦部分とする。これら微小凹部５６、５６、放射状凹溝５７、５７、環状凹溝５８ａ、５８ｂの内面部分は、相手面と擦れ合う事はないので、平滑面とする必要はない。上記表面粗さの値（Ｒａ１２．５μｍ以下）が、上記微小凹部５６、５６、放射状凹溝５７、５７、環状凹溝５８ａ、５８ｂ部分の深さを除いたものである事は勿論である。又、上記各面を、Ｒａ１２．５μｍ以下の平滑面とすれば、特に使用条件が厳しくなければ、上記微小凹部５６、５６、放射状凹溝５７、５７、環状凹溝５８ａ、５８ｂを省略しても、実用上十分な耐久性を得られる。 In addition, in order to more effectively prevent the oil film breakage that leads to the fretting wear, the surface roughness of the one side surface in the axial direction of the spacer 55 and the one side surface of the first connecting plate 43 is Ra 12.5 μm or less. The smooth surface. More preferably, both the other axial side surface of the spacer 55 and the outer surface of the input side disk 4b are smooth surfaces with a surface roughness Ra of 12.5 μm or less. In this case, the smooth surface is a flat portion that is out of the minute recesses 56 and 56, the radial recesses 57 and 57, and the annular recesses 58a and 58b shown in FIG. The inner surface portions of the minute recesses 56 and 56, the radial recess grooves 57 and 57, and the annular recess grooves 58a and 58b do not rub against the mating surface, and need not be smooth surfaces. Of course, the value of the surface roughness (Ra 12.5 μm or less) is obtained by excluding the depths of the minute concave portions 56 and 56, the radial concave grooves 57 and 57, and the annular concave grooves 58a and 58b. Further, if each surface is a smooth surface of Ra 12.5 μm or less, the micro concave portions 56 and 56, the radial concave grooves 57 and 57, and the annular concave grooves 58a and 58b are omitted unless the usage conditions are particularly severe. However, sufficient practical durability can be obtained.

図３は、請求項１、９に対応する、本発明の実施例２を示している。本実施例の場合には、銅系合金製で円輪状のスペーサ５５ａの円周方向複数個所（図示の例では８個所）に、それぞれがこのスペーサ５５ａの径方向中間部から外周縁に迄達するスリット６０、６０を、放射状に形成している。本実施例の場合には、この様にして上記スペーサ５５ａの径方向中間部乃至外径寄り部分を、円周方向に関して分割する事により、このスペーサ５５ａの径方向中間部乃至外周縁部を、厚さ方向に変形し易くしている。 FIG. 3 shows a second embodiment of the present invention corresponding to claims 1 and 9. In the case of the present embodiment, the annular spacer 55a made of a copper alloy reaches a plurality of circumferential positions (eight positions in the illustrated example) from the intermediate portion in the radial direction of the spacer 55a to the outer peripheral edge. The slits 60, 60 are formed radially. In the case of the present embodiment, the radial intermediate portion or outer peripheral portion of the spacer 55a is thus divided in the circumferential direction so that the radial intermediate portion or outer peripheral portion of the spacer 55a is divided. It is easy to deform in the thickness direction.

本実施例の場合には、上述の様な構成を採用する事により、上記スペーサ５５ａが隣接する入力側ディスク４ｂが、前述の図９に示す様に弾性変形した場合でも、このスペーサ５５ａに有害な塑性変形が生じにくくしている。即ち、本実施例の場合には、上記入力側ディスク４ｂの外側面のうち外径寄り部分が軸方向に関して比較的大きく弾性変形し、この部分に当接した上記スペーサ５５ａが軸方向に押圧されると、この押圧された部分及びその近傍部分のみが軸方向（厚さ方向）に変位する。つまり、上記各スリット６０、６０の存在に基づき、上記スペーサ５５ａの一部が押されても、このスペーサ５５ａに円周方向に関して大きな引っ張り応力が発生する事はない。この為、このスペーサ５５ａに、有害な塑性変形、即ち、外径寄り部分が引っ張り延ばされる様な塑性変形を生じる事を防止できる。 In the case of the present embodiment, by adopting the above-described configuration, even if the input side disk 4b adjacent to the spacer 55a is elastically deformed as shown in FIG. 9, it is harmful to the spacer 55a. This makes it difficult for plastic deformation to occur. That is, in the case of the present embodiment, a portion near the outer diameter of the outer side surface of the input side disk 4b undergoes a relatively large elastic deformation in the axial direction, and the spacer 55a in contact with this portion is pressed in the axial direction. Then, only the pressed portion and the vicinity thereof are displaced in the axial direction (thickness direction). In other words, even if a part of the spacer 55a is pushed due to the presence of the slits 60, 60, a large tensile stress is not generated in the spacer 55a in the circumferential direction. For this reason, it is possible to prevent the spacer 55a from causing harmful plastic deformation, that is, plastic deformation such that a portion near the outer diameter is stretched.

図示の例は、本発明を構成するトロイダル型無段変速機としてハーフトロイダル型のものを使用した場合に就いて説明したが、本発明は、何れの請求項に記載した発明の場合でも、ハーフトロイダル型に限らず、フルトロイダル型のトロイダル型無段変速機でも実施可能である。 The illustrated example has been described for the case where a half toroidal type continuously variable transmission constituting the present invention is used. However, the present invention is not limited to a half toroidal type continuously variable transmission. Not only the toroidal type but also a full toroidal type toroidal continuously variable transmission can be implemented.

本発明の実施例１を、組み立て前の状態で示す、図６のＡ部に相当する拡大断面図。The expanded sectional view equivalent to the A section of FIG. 6 which shows Example 1 of this invention in the state before an assembly. 実施例１に組み込むスペーサの形状の３例を示す斜視図。3 is a perspective view showing three examples of the shape of a spacer incorporated in Example 1. FIG. 実施例２に組み込むスペーサの斜視図。FIG. 6 is a perspective view of a spacer incorporated in Example 2. 従来から知られている無段変速装置の１例を示す略断面図。FIG. 6 is a schematic cross-sectional view showing an example of a conventionally known continuously variable transmission. 先発明に係る無段変速装置の１例を示す略断面図。1 is a schematic cross-sectional view showing an example of a continuously variable transmission according to a prior invention. 先に考えた具体的構造の１例を示す断面図。Sectional drawing which shows an example of the concrete structure considered previously. 図６のＢ部に相当する拡大断面図。The expanded sectional view equivalent to the B section of FIG. キャリアを取り出して示す斜視図。The perspective view which takes out and shows a carrier. 入力側ディスクの弾性変形を誇張して示す断面図。A sectional view exaggeratingly showing elastic deformation of an input side disk.

Explanation of symbols

１トロイダル型無段変速機
２、２ａ、２ｂ遊星歯車式変速機
３、３ａ入力軸
４、４ａ、４ｂ入力側ディスク
５出力側ディスク
６パワーローラ
７、７ａキャリア
８遊星歯車
９遊星歯車
１０第一伝達軸
１１太陽歯車
１２太陽歯車
１３第二伝達軸
１４、１４ａ中空回転軸
１５太陽歯車
１６遊星歯車
１７リング歯車
１８、１８ａ第二キャリア
１９遊星歯車
２０遊星歯車
２１、２１ａ出力軸
２２、２２ａ第二リング歯車
２３、２３ａ低速用クラッチ
２４、２４ａ高速用クラッチ
２５、２５ａ、２５ｂ遊星歯車
２６ａ、２６ｂ遊星歯車
２７伝達軸
２８第一太陽歯車
２９第二太陽歯車
３０、３０ａリング歯車
３１第三太陽歯車
３２ａ、３２ｂ遊星歯車
３３ハウジング
３４支柱
３５連結板
３６バルブボディー
３７支持板
３８転がり軸受
３９ボールスプライン
４０押圧装置
４１ラジアルニードル軸受
４２中間支持板
４３第一連結板
４４第二連結板
４５第一遊星軸
４６第二遊星軸
４７第三遊星軸
４８ａ、４８ｂ、４８ｃラジアルニードル軸受
４９円筒部
５０ローディングナット
５１円輪部
５２凸部
５３切り欠き
５４駆動軸
５５、５５ａスペーサ
５６微小凹部
５７放射状凹溝
５８ａ、５８ｂ環状凹溝
５９連結部
６０スリット
DESCRIPTION OF SYMBOLS 1 Toroidal type continuously variable transmission 2, 2a, 2b Planetary gear type transmission 3, 3a Input shaft 4, 4a, 4b Input side disk 5 Output side disk 6 Power roller 7, 7a Carrier 8 Planetary gear 9 Planetary gear 10 First Transmission shaft 11 Sun gear 12 Sun gear 13 Second transmission shaft 14, 14a Hollow rotating shaft 15 Sun gear 16 Planet gear 17 Ring gear 18, 18a Second carrier 19 Planet gear 20 Planet gear 21, 21a Output shaft 22, 22a Second Ring gear 23, 23a Low speed clutch 24, 24a High speed clutch 25, 25a, 25b Planetary gear 26a, 26b Planetary gear 27 Transmission shaft 28 First sun gear 29 Second sun gear 30, 30a Ring gear 31 Third sun gear 32a 32b Planetary gear 33 Housing 34 Prop 35 Connecting plate 36 Valve body 37 Support plate 38 Ball bearing 39 Ball spline 40 Press device 41 Radial needle bearing 42 Intermediate support plate 43 First connecting plate 44 Second connecting plate 45 First planetary shaft 46 Second planetary shaft 47 Third planetary shafts 48a, 48b, 48c Radial needle bearing 49 Cylindrical part 50 Loading nut 51 Annular part 52 Convex part 53 Notch 54 Drive shaft 55, 55a Spacer 56 Micro concave part 57 Radial concave groove 58a, 58b Annular concave groove 59 Connecting part 60 Slit

Claims

An input shaft, an output shaft, a toroidal type continuously variable transmission, and a planetary gear type transmission, which are arranged concentrically with each other, are provided with a toroidal type continuously variable transmission and a planetary gear type transmission. The input side disk constituting the continuously variable transmission and the carrier constituting the planetary gear type transmission are adjacent to each other, and the input side disk and the carrier are combined in a state of rotating synchronously. A support plate supported and fixed to the input shaft, and an annular shape arranged concentrically with the support plate and spaced apart in the axial direction, with one side surface facing the outer surface of the input side disk. A connecting plate, and a plurality of planetary shafts supported at both ends by the connecting plate and the support plate, and the planetary gears constituting the planetary gear type transmission are connected to each planetary shaft. Rotate around In the continuously variable transmission supported on the side, the one side surface of the coupling plate and the outer side surface of the input side disk facing each other are abutted through a ring-shaped spacer made of a copper alloy. A continuously variable transmission.

The continuously variable transmission according to claim 1, wherein a number of minute recesses are formed on the side surface in the axial direction of the spacer.

The continuously variable transmission according to claim 1, wherein a plurality of radial grooves are formed on an axial side surface of the spacer.

The continuously variable transmission according to claim 1, wherein an annular groove is formed on an axial side surface of the spacer.

An input shaft, an output shaft, a toroidal type continuously variable transmission, and a planetary gear type transmission, which are arranged concentrically with each other, are provided with a toroidal type continuously variable transmission and a planetary gear type transmission. The input side disk constituting the continuously variable transmission and the carrier constituting the planetary gear type transmission are adjacent to each other, and the input side disk and the carrier are combined in a state of rotating synchronously. A support plate supported and fixed to the input shaft, and an annular shape arranged concentrically with the support plate and spaced apart in the axial direction, with one side surface facing the outer surface of the input side disk. A connecting plate, and a plurality of planetary shafts supported at both ends by the connecting plate and the support plate, and the planetary gears constituting the planetary gear type transmission are connected to each planetary shaft. Rotate around In the continuously variable transmission supported on the one side surface, the one side surface of the coupling plate that abuts the one side surface of the coupling plate facing each other and the outer side surface of the input side disk via a ring-shaped spacer. A continuously variable transmission having a smooth surface with a surface roughness of Ra 12.5 [mu] m or less.

The continuously variable transmission according to claim 5, wherein one side surface of the connecting plate and the one side surface of the spacer that are in contact with each other are smoothened by polishing.

In addition to making one side of the connecting plate that contacts each other and one side of the spacer a smooth surface, the outer surface of the input disk that contacts each other and the other surface of the spacer both have a surface roughness of Ra 12.5 μm or less. The continuously variable transmission according to any one of claims 5 to 6, wherein the continuously variable transmission surface is a smooth surface.

The continuously variable transmission according to any one of claims 1 to 7, wherein a support plate and a connecting plate constituting the carrier are integrally formed.

A plurality of slits extending from the radial intermediate portion of the spacer to the outer peripheral edge are formed at a plurality of locations in the circumferential direction of the spacer so that the radial intermediate portion to the outer peripheral edge of the spacer can be easily deformed in the thickness direction. The continuously variable transmission according to any one of claims 1 to 8.