JP3468060B2 - Transmission ratio infinitely variable transmission - Google Patents
Transmission ratio infinitely variable transmissionInfo
- Publication number
- JP3468060B2 JP3468060B2 JP30317897A JP30317897A JP3468060B2 JP 3468060 B2 JP3468060 B2 JP 3468060B2 JP 30317897 A JP30317897 A JP 30317897A JP 30317897 A JP30317897 A JP 30317897A JP 3468060 B2 JP3468060 B2 JP 3468060B2
- Authority
- JP
- Japan
- Prior art keywords
- variable transmission
- continuously variable
- transmission
- gear ratio
- gear
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Description
【０００１】[0001]
【発明の属する技術分野】本発明は、車両などに採用さ
れる無段変速機、特に変速比無限大無段変速機の改良に
関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a continuously variable transmission adopted in a vehicle or the like, and particularly to an continuously variable transmission having an infinite transmission ratio.
【０００２】[0002]
【従来の技術】従来から連続的に変速比を設定可能な車
両の変速機としては、ベルト式やトロイダル型の無段変
速機が知られており、このような無段変速機の変速領域
をさらに拡大するために、無段変速機と一定変速機等を
並列的に配設するとともに、これらの出力軸を遊星歯車
機構へ入力して変速比を無限大まで制御可能とする変速
比無限大無段変速機が知られており、例えば、本願出願
人が提案した特願平８−１５５４４０号や特願平７−２
４１８９０号などがある。2. Description of the Related Art Conventionally, a belt type or toroidal type continuously variable transmission has been known as a transmission for a vehicle in which a gear ratio can be continuously set. For further expansion, a continuously variable transmission and a constant transmission are arranged in parallel, and these output shafts are input to the planetary gear mechanism so that the gear ratio can be controlled to infinity. A continuously variable transmission is known, and for example, Japanese Patent Application No. 8-155440 and Japanese Patent Application No. 7-2 proposed by the applicant of the present application.
41890 and the like.
【０００３】これは、図９に示すように、エンジンに結
合される変速比無限大無段変速機のユニット入力軸１に
変速比を連続的に変更可能な無段変速機２と、ユニット
入力軸１に設けたギヤ３ａ及び遊星歯車機構５と選択的
に締結されるギヤ３ｂから構成される一定の変速比を備
えた一定変速機３（または、一定減速機）を並列的に連
結するとともに、これらの出力軸４及び３ｃを遊星歯車
機構５で結合したもので、無段変速機２の出力は無段変
速機出力ギヤ列４０（無段変速機出力ギヤ２ａ、カウン
タギヤ４０ａ、ギヤ４ａ）を介して出力軸４に連結さ
れ、出力軸４は遊星歯車機構５のサンギヤ５ａに連結さ
れ、一定変速機３の出力軸３ｃは遊星歯車機構５のキャ
リア５ｂへ選択的に締結される一方、遊星歯車機構５の
リングギヤ５ｃはユニット出力軸６に結合される。As shown in FIG. 9, this is because a continuously variable transmission 2 capable of continuously changing the gear ratio is connected to a unit input shaft 1 of an infinitely variable transmission continuously variable transmission coupled to an engine, and a unit input. A constant transmission 3 (or a constant speed reducer) having a constant speed ratio, which is composed of a gear 3a provided on the shaft 1 and a gear 3b selectively engaged with the planetary gear mechanism 5, is connected in parallel. , The output shafts 4 and 3c are connected by a planetary gear mechanism 5, and the output of the continuously variable transmission 2 is the continuously variable transmission output gear train 40 (the continuously variable transmission output gear 2a, the counter gear 40a, the gear 4a). ) Is connected to the output shaft 4, the output shaft 4 is connected to the sun gear 5a of the planetary gear mechanism 5, and the output shaft 3c of the constant transmission 3 is selectively fastened to the carrier 5b of the planetary gear mechanism 5. , The ring gear 5c of the planetary gear mechanism 5 is It is coupled to Tsu preparative output shaft 6.
【０００４】無段変速機２は、２組の入力ディスク２１
と出力ディスク２２の間にそれぞれ扶持された一対のパ
ワーローラ２０の傾転角に応じて変速比を連続的に変更
するトロイダル型無段変速機で構成されており、ユニッ
ト入力軸１から遊星歯車機構５のキャリア５ｂへの伝達
経路の途中には、動力循環モードクラッチ９が介装さ
れ、無段変速機の出力軸４からユニット出力軸６の伝達
経路の途中には、直結モードクラッチ１０が介装され
る。なお、直結モードクラッチ１０は、遊星歯車機構５
のうち、相互に歯合する回転要素（サンギヤ、キャリ
ア、リングギア）のうちの２つを固定するものであって
も良い。The continuously variable transmission 2 has two sets of input disks 21.
And a pair of power rollers 20 held between the output disk 22 and the output disk 22 respectively. The toroidal type continuously variable transmission continuously changes the gear ratio according to the tilt angle of the pair of power rollers. A power circulation mode clutch 9 is provided in the transmission path of the mechanism 5 to the carrier 5b, and a direct coupling mode clutch 10 is provided in the transmission path of the continuously variable transmission from the output shaft 4 to the unit output shaft 6. Intervened. The direct coupling mode clutch 10 is used for the planetary gear mechanism 5.
Of these, two of the rotating elements (sun gear, carrier, ring gear) that mesh with each other may be fixed.
【０００５】ユニット出力軸６には変速機出力ギヤ７が
設けられ、この変速機出力ギヤ７は差動ギヤ８のファイ
ナルギヤ１２ａと歯合し、所定の総減速比で差動ギヤ８
と結合した駆動軸１１ａ、１１ｂに駆動力が伝達され
る。A transmission output gear 7 is provided on the unit output shaft 6, and the transmission output gear 7 meshes with a final gear 12a of a differential gear 8 so that the differential gear 8 has a predetermined total reduction ratio.
The driving force is transmitted to the drive shafts 11a and 11b coupled with the drive shafts.
【０００６】このような変速比無限大無段変速機では、
動力循環モードクラッチ９を接続する一方、直結モード
クラッチ１０を解放することにより、無段変速機２と一
定変速機３の変速比に応じて、ユニット変速比（総変速
比）Ｉｖを負の値から正の値まで無限大を含んでほぼ連
続的に制御を行う動力循環モードと、動力循環モードク
ラッチ９を解放する一方、直結モードクラッチ１０を接
続して無段変速機２の変速比と無段変速機出力ギヤ列４
０の変速比の積に応じた変速比となる無段変速機直結モ
ードを選択的に使用することができる。In such a continuously variable transmission having an infinite transmission ratio,
By connecting the power circulation mode clutch 9 and releasing the direct connection mode clutch 10, the unit gear ratio (total gear ratio) Iv is set to a negative value in accordance with the gear ratio between the continuously variable transmission 2 and the constant transmission 3. To a positive value, the power circulation mode in which the control is performed substantially continuously including infinity, and the power circulation mode clutch 9 is released, while the direct coupling mode clutch 10 is connected, and the gear ratio of the continuously variable transmission 2 and Gearbox output gear train 4
It is possible to selectively use the continuously variable transmission direct-coupling mode in which the gear ratio corresponds to the product of the gear ratio of 0.
【０００７】ここで、一定変速機３の減速比Ｉｇは、無
段変速機出力ギヤ列４０の変速比Ｉｄと無段変速機で設
定可能な最大（最ロー）変速比ＩｃLOWの積に等しい
か、または、これらの積以下で、かつ、可能な限り大き
く設定されており、総変速比に段差のない円滑なモード
切り換えを行うことができる。Here, is the reduction gear ratio Ig of the constant transmission 3 equal to the product of the gear ratio Id of the continuously variable transmission output gear train 40 and the maximum (lowest) gear ratio IcLOW that can be set in the continuously variable transmission? Alternatively, the product is set to be less than or equal to the product of these and set as large as possible, and smooth mode switching can be performed without a step in the total speed ratio.
【０００８】ところで、上記のような変速比無限大無段
変速機では、無段変速機直結モードにおける総変速比Ｉ
ｖは、無段変速機２の変速比Ｉｃと無段変速機出力ギヤ
列４０の変速比Ｉｄと、ファイナルギヤ列１２の減速比
Ｉｆの積に等しい、すなわち、
Ｉｖ＝（−Ｉｃ・Ｉｄ）（−Ｉｆ）＝Ｉｃ・Ｉｄ・Ｉｆ ………（１）
で表される。By the way, in the continuously variable transmission having an infinite transmission ratio as described above, the total transmission ratio I in the direct connection mode of the continuously variable transmission is set.
v is equal to the product of the gear ratio Ic of the continuously variable transmission 2, the gear ratio Id of the continuously variable transmission output gear train 40, and the speed reduction ratio If of the final gear train 12, that is, Iv = (-Ic · Id) (-If) = Ic · Id · If ... (1)
【０００９】また、動力循環モードにおける総変速比Ｉ
ｖは、無段変速機２の変速比Ｉｃと、無段変速機出力ギ
ヤ列の変速比Ｉｄと、一定変速機３の変速比Ｉｇと、遊
星歯車機構５のギヤ比α（＝サンギヤ５ａの歯数／リン
グギヤ５ｃの歯数）と、ファイナルギヤ列１２の減速比
Ｉｆから設定される。すなわち、Further, the total gear ratio I in the power circulation mode
v is the gear ratio Ic of the continuously variable transmission 2, the gear ratio Id of the continuously variable transmission output gear train, the gear ratio Ig of the constant transmission 3, and the gear ratio α (= sun gear 5a of the planetary gear mechanism 5). The number of teeth / the number of teeth of the ring gear 5c) and the reduction ratio If of the final gear train 12 are set. That is,
【００１０】[0010]
【数５】 [Equation 5]
【００１１】で表される。It is represented by
【００１２】したがって、総変速比Ｉｖの範囲は、無段
変速機２の変速比幅λ（最大変速比／最小変速比）と、
無段変速機出力ギヤ列４０の変速比Ｉｄと、一定変速機
３の変速比Ｉｇと、遊星歯車機構５のギヤ比αと、ファ
イナルギヤ列１２の減速比Ｉｆによって決まる。Therefore, the range of the total gear ratio Iv is the gear ratio width λ (maximum gear ratio / minimum gear ratio) of the continuously variable transmission 2,
It is determined by the gear ratio Id of the continuously variable transmission output gear train 40, the gear ratio Ig of the constant transmission 3, the gear ratio α of the planetary gear mechanism 5, and the reduction gear ratio If of the final gear train 12.
【００１３】[0013]
【発明が解決しようとする課題】しかしながら、上記従
来の変速比無限大無段変速機では、遊星歯車機構５のギ
ヤ比αと無段変速機２の変速比幅λの間に関連性が規定
されていないため、変速比無限大無段変速機に必要とさ
れる前進側最ハイ変速比ＩｖHiと、必要とされる後退側
最ハイ変速比ＩｖRevが与えられた場合、遊星歯車機構
５のギヤ比αによっては、無段変速機２の変速比範囲
（すなわち変速比幅λ）を有効に利用することができな
い場合があり、必要とされる変速比の条件を満たそうと
すると無段変速機２が大型化するという問題があった。However, in the above-mentioned conventional infinitely variable transmission continuously variable transmission, a relationship is defined between the gear ratio α of the planetary gear mechanism 5 and the transmission ratio width λ of the continuously variable transmission 2. Therefore, when the maximum forward gear ratio IvHi required for the infinitely variable transmission and the required maximum backward gear ratio IvRev are provided, the gears of the planetary gear mechanism 5 are not provided. Depending on the ratio α, there is a case where the gear ratio range of the continuously variable transmission 2 (that is, the gear ratio width λ) cannot be effectively utilized, and if the condition of the required gear ratio is attempted to be satisfied, the continuously variable transmission will There was a problem that 2 became large.
【００１４】すなわち、前記従来例と同様に、変速比無
限大無段変速機の諸元設定を、
無段変速機出力ギヤ列４０の変速比Ｉｄ＝１．０
一定変速機３の変速比Ｉｇ＝２．０
ファイナルギヤ列１２の減速比Ｉｆ＝３．５
遊星歯車機構５のギヤ比α＝３６／６７
とし、必要とされる前進側最ハイ変速比ＩｖHiと、必要
とされる後退側最ハイ変速比ＩｖRevを、
ＩｖHi＝２
ＩｖRev＝−７．５
とした場合には、無段変速機２の変速比Ｉｃと総変速比
Ｉｖの逆数１／Ｉｖの関係は、図１０に示すようにな
る。That is, similarly to the conventional example, the specifications of the continuously variable transmission having an infinite transmission ratio are set such that the gear ratio Id of the continuously variable transmission output gear train 40 is 1.0 and the gear ratio Ig of the constant transmission 3 is constant. = 2.0 Reduction ratio If of final gear train 12 = 3.5 Gear ratio α of planetary gear mechanism 5 = 36/67, required forward maximum gear ratio IvHi and required reverse maximum gear ratio When the high gear ratio IvRev is set to IvHi = 2 IvRev = -7.5, the relationship between the gear ratio Ic of the continuously variable transmission 2 and the reciprocal 1 / Iv of the total gear ratio Iv is as shown in FIG. Become.
【００１５】すなわち、変速比無限大無段変速機の総変
速比Ｉｖが必要とする前進側最ハイ変速比ＩｖHiとなる
無段変速機２の変速比ＩｃHi、及び必要とする後退側最
ハイ変速比ＩｃRevとなる無段変速機２の変速比ＩｃRev
は、That is, the gear ratio IcHi of the continuously variable transmission 2 at which the total gear ratio Iv of the continuously variable transmission with infinite gear ratio becomes the required highest forward gear ratio IvHi, and the required highest gear ratio of the backward gear IvHi. The gear ratio IcRev of the continuously variable transmission 2 with the ratio IcRev
Is
【００１６】[0016]
【数６】 [Equation 6]
【００１７】となる。[0017]
【００１８】無段変速機２の変速比範囲、すなわち、変
速比幅λは、図１０のように、前進側では余裕を生ずる
が、後退側では不足する。このため、変速比範囲を有効
に利用することができないばかりか、後退側での不足を
補うためには、無段変速機２の変速比範囲を拡大するこ
とにより無段変速機２が大型化するという問題があっ
た。As shown in FIG. 10, the gear ratio range of the continuously variable transmission 2, that is, the gear ratio width λ, has a margin on the forward side but is insufficient on the reverse side. For this reason, not only can the gear ratio range not be effectively utilized, but in order to compensate for the shortage on the reverse side, the gear ratio range of the continuously variable transmission 2 is expanded to increase the size of the continuously variable transmission 2. There was a problem of doing.
【００１９】そこで本発明は、上記間題点に鑑みてなさ
れたもので、遊星歯車機構のギヤ比αと無段変速機の変
速比幅λの間に所定の関係を設定し、無段変速機の変速
比範囲を有効に利用し、変速比無限大無段変速機の小型
軽量化を可能にすることを目的とする。Therefore, the present invention has been made in view of the above-mentioned problem, and a predetermined relationship is set between the gear ratio α of the planetary gear mechanism and the speed ratio width λ of the continuously variable transmission to continuously change the speed. It is an object of the present invention to effectively utilize the gear ratio range of a machine and to reduce the size and weight of a continuously variable transmission with an infinite gear ratio.
【００２０】[0020]
【課題を解決するための手段】第１の発明は、ユニット
入力軸にそれぞれ接続された無段変速機及び一定変速機
と、無段変速機の出力軸に連結したサンギヤ、シングル
ピニオンで構成されて一定変速機の出力軸に連結したキ
ャリア及びユニット出力軸に連結したリングギヤとから
なる遊星歯車機構と、前記ユニット入力軸から遊星歯車
機構のキャリアへの動力伝達経路の途中に介装された動
力循環モードクラッチと、前記無段変速機の出力軸から
ユニット出力軸の動力伝達経路の途中に介装されて無段
変速機の出力軸とユニット出力軸を選択的に締結または
遊星歯車機構の相互に歯合する前記回転要素を選択的に
固定する直結モードクラッチとを備えて、前記動力循環
モードクラッチと直結モードクラッチとを選択的に締
結、解除可能な変速比無限大無段変速機において、変速
比無限大無段変速機の前進側最ハイ変速比をＩｖHiと
し、同じく後退側最ハイ変速比をＩｖRevとするととも
に、前記無段変速機の変速比幅をλとすると、前記遊星
歯車機構のサンギヤの歯数／リングギヤの歯数で表され
るギヤ比αは、A first aspect of the present invention comprises a continuously variable transmission and a constant transmission, each connected to a unit input shaft, a sun gear and a single pinion connected to an output shaft of the continuously variable transmission. A planetary gear mechanism consisting of a carrier connected to the output shaft of a constant transmission and a ring gear connected to the unit output shaft, and a power interposed in the power transmission path from the unit input shaft to the carrier of the planetary gear mechanism. The circulation mode clutch and the output shaft of the continuously variable transmission are interposed between the output shaft of the continuously variable transmission and the unit output shaft so that the output shaft of the continuously variable transmission and the unit output shaft are selectively engaged or interlocked with each other by the planetary gear mechanism. A direct coupling mode clutch that selectively fixes the rotary element that meshes with the power circulation mode clutch and the direct coupling mode clutch. In the infinite continuously variable transmission, the forward maximum speed ratio of the infinite continuously variable transmission is set to IvHi, the reverse maximum speed ratio is set to IvRev, and the speed ratio range of the continuously variable transmission is set. If λ, the gear ratio α represented by the number of teeth of the sun gear of the planetary gear mechanism / the number of teeth of the ring gear is
【００２１】[0021]
【数７】 [Equation 7]
【００２２】に設定される。Is set to
【００２３】また、第２の発明は、ユニット入力軸にそ
れぞれ接続された無段変速機及び一定変速機と、無段変
速機の出力軸に連結したリングギヤ、シングルピニオン
で構成されて一定変速機の出力軸に連結したキャリア及
びユニット出力軸に連結したサンギヤとからなる遊星歯
車機構と、前記ユニット入力軸から遊星歯車機構のキャ
リアへの動力伝達経路の途中に介装された動力循環モー
ドクラッチと、前記無段変速機の出力軸からユニット出
力軸の動力伝達経路の途中に介装されて無段変速機の出
力軸とユニット出力軸を選択的に締結または遊星歯車機
構の相互に歯合する前記回転要素を選択的に固定する直
結モードクラッチとを備えて、前記動力循環モードクラ
ッチと直結モードクラッチとを選択的に締結、解除可能
な変速比無限大無段変速機において、変速比無限大無段
変速機の前進側最ハイ変速比をＩｖHiとし、同じく後退
側最ハイ変速比をＩｖRevとするとともに、前記無段変
速機の変速比幅をλとすると、前記遊星歯車機構のサン
ギヤの歯数／リングギヤの歯数で表されるギヤ比αは、A second aspect of the present invention is a constant transmission that is composed of a continuously variable transmission and a constant transmission that are respectively connected to a unit input shaft, a ring gear that is connected to an output shaft of the continuously variable transmission, and a single pinion. A planetary gear mechanism consisting of a carrier connected to the output shaft of the above and a sun gear connected to the unit output shaft, and a power circulation mode clutch interposed in the middle of the power transmission path from the unit input shaft to the carrier of the planetary gear mechanism. An output shaft of the continuously variable transmission, which is interposed in the power transmission path of the unit output shaft, selectively engages the output shaft of the continuously variable transmission with the unit output shaft or meshes with the planetary gear mechanism. A direct coupling mode clutch for selectively fixing the rotating element, and a gear ratio infinity capable of selectively engaging and releasing the power circulation mode clutch and the direct coupling mode clutch. In the transmission, if the forward-side highest gear ratio of the continuously variable transmission with infinite gear ratio is IvHi, the backward-side highest gear ratio is IvRev, and the gear ratio width of the continuously variable transmission is λ, The gear ratio α represented by the number of teeth of the sun gear of the planetary gear mechanism / the number of teeth of the ring gear is
【００２４】[0024]
【数８】 [Equation 8]
【００２５】に設定される。Is set to
【００２６】また、第３の発明は、ユニット入力軸にそ
れぞれ連結された無段変速機及び一定変速機と、無段変
速機の出力軸に連結したサンギヤ、一定変速機の出力軸
に連結したリングギヤ及びダブルピニオンで構成されて
ユニット出力軸に連結したキャリアとからなる遊星歯車
機構と、前記ユニット入力軸から遊星歯車機構のリング
ギヤへの動力伝達経路の途中に介装された動力循環モー
ドクラッチと、前記無段変速機の出力軸からユニット出
力軸の動力伝達経路の途中に介装されて無段変速機の出
力軸とユニット出力軸を選択的に締結または遊星歯車機
構の相互に歯合する前記回転要素を選択的に固定する直
結モードクラッチとを備えて、前記動力循環モードクラ
ッチと直結モードクラッチとを選択的に締結、解除可能
な変速比無限大無段変速機において、変速比無限大無段
変速機の前進側最ハイ変速比をＩｖHiとし、同じく後退
側最ハイ変速比をＩｖRevとするとともに、前記無段変
速機の変速比幅をλとすると、前記遊星歯車機構のサン
ギヤの歯数／リングギヤの歯数で表されるギヤ比αは、In the third aspect of the invention, a continuously variable transmission and a constant transmission, each connected to the unit input shaft, a sun gear connected to the output shaft of the continuously variable transmission, and an output shaft of the constant transmission are connected. A planetary gear mechanism including a ring gear and a carrier that is composed of a double pinion and connected to a unit output shaft, and a power circulation mode clutch that is interposed in the power transmission path from the unit input shaft to the ring gear of the planetary gear mechanism. An output shaft of the continuously variable transmission, which is interposed in the power transmission path of the unit output shaft, selectively engages the output shaft of the continuously variable transmission with the unit output shaft or meshes with the planetary gear mechanism. A direct coupling mode clutch for selectively fixing the rotating element, and a gear ratio infinity capable of selectively engaging and releasing the power circulation mode clutch and the direct coupling mode clutch. In the transmission, if the forward-side highest gear ratio of the continuously variable transmission with infinite gear ratio is IvHi, the backward-side highest gear ratio is IvRev, and the gear ratio width of the continuously variable transmission is λ, The gear ratio α represented by the number of teeth of the sun gear of the planetary gear mechanism / the number of teeth of the ring gear is
【００２７】[0027]
【数９】 [Equation 9]
【００２８】に設定される。Is set to
【００２９】また、第４の発明は、ユニット入力軸にそ
れぞれ連結された無段変速機及び一定変速機と、ダブル
ピニオンで構成されて無段変速機の出力軸に連結したキ
ャリア、一定変速機の出力軸に連結したリングギヤ及び
ユニット出力軸に連結したサンギヤとからなる遊星歯車
機構と、前記ユニット入力軸から遊星歯車機構のリング
ギヤへの動力伝達経路の途中に介装された動力循環モー
ドクラッチと、前記無段変速機の出力軸からユニット出
力軸の動力伝達経路の途中に介装されて無段変速機の出
力軸とユニット出力軸を選択的に締結または遊星歯車機
構の相互に歯合する前記回転要素を選択的に固定する直
結モードクラッチとを備えて、前記動力循環モードクラ
ッチと直結モードクラッチとを選択的に締結、解除可能
な変速比無限大無段変速機において、変速比無限大無段
変速機の前進側最ハイ変速比をＩｖHiとし、同じく後退
側最ハイ変速比をＩｖRevとするとともに、前記無段変
速機の変速比幅をλとすると、前記遊星歯車機構のサン
ギヤの歯数／リングギヤの歯数で表されるギヤ比αは、A fourth aspect of the invention is a continuously variable transmission and a constant transmission, each of which is connected to a unit input shaft, and a carrier and a constant transmission, which are composed of a double pinion and are connected to an output shaft of the continuously variable transmission. A planetary gear mechanism consisting of a ring gear connected to the output shaft of the above and a sun gear connected to the unit output shaft, and a power circulation mode clutch interposed in the middle of the power transmission path from the unit input shaft to the ring gear of the planetary gear mechanism. An output shaft of the continuously variable transmission, which is interposed in the power transmission path of the unit output shaft, selectively engages the output shaft of the continuously variable transmission with the unit output shaft or meshes with the planetary gear mechanism. A direct coupling mode clutch for selectively fixing the rotating element, and a gear ratio infinity capable of selectively engaging and releasing the power circulation mode clutch and the direct coupling mode clutch. In the transmission, if the forward-side highest gear ratio of the continuously variable transmission with infinite gear ratio is IvHi, the backward-side highest gear ratio is IvRev, and the gear ratio width of the continuously variable transmission is λ, The gear ratio α represented by the number of teeth of the sun gear of the planetary gear mechanism / the number of teeth of the ring gear is
【００３０】[0030]
【数１０】 [Equation 10]
【００３１】に設定される。Is set to
【００３２】[0032]
【発明の効果】第１の発明は、無段変速機の出力軸に連
結したサンギヤ、シングルピニオンで構成されて一定変
速機の出力軸に連結したキャリア及びユニット出力軸に
連結したリングギヤとからなる遊星歯車機構のギヤ比α
と無段変速機の変速比幅λの関係を、上記（Ａ）式に等
しいか、またはほぼ等しい値に設定する構成としたた
め、無段変速機の最小（最ハイ）変速比ＩｃHiにおい
て、変速比無限大無段変速機の総変速比Ｉｖを、動力循
環モードのときには必要とされる後退側の最ハイ変速比
ＩｖRevに、無段変速機直結モードのときには必要とさ
れる前進側の最ハイ変速比ＩｖHiにすることが可能とな
って、無段変速機の変速比範囲を有効に活用できるた
め、前記従来例のように無段変速機を大型化する必要が
なくなって、変速比無限大無段変速機の小型軽量化を推
進できる。The first invention comprises a sun gear connected to the output shaft of a continuously variable transmission, a carrier composed of a single pinion and connected to the output shaft of a constant transmission, and a ring gear connected to the unit output shaft. Gear ratio α of planetary gear mechanism
And the gear ratio width λ of the continuously variable transmission are set to a value equal to or substantially equal to the expression (A), the gear ratio is changed at the minimum (highest) gear ratio IcHi of the continuously variable transmission. The total gear ratio Iv of the infinite ratio continuously variable transmission is set to the highest reverse gear ratio IvRev required in the power circulation mode, and the highest forward gear ratio required in the continuously variable transmission direct connection mode. Since the gear ratio can be set to IvHi and the gear ratio range of the continuously variable transmission can be effectively utilized, it is not necessary to increase the size of the continuously variable transmission as in the conventional example described above. The size and weight of the continuously variable transmission can be promoted.
【００３３】また、第２の発明は、無段変速機の出力軸
に連結したリングギヤ、シングルピニオンで構成されて
一定変速機の出力軸に連結したキャリア及びユニット出
力軸に連結したサンギヤとからなる遊星歯車機構のギヤ
比αと無段変速機の変速比幅λの関係を、上記（Ｂ）式
に等しいか、またはほぼ等しい値に設定する構成とした
ため、無段変速機の最小（最ハイ）変速比ＩｃHiにおい
て、変速比無限大無段変速機の総変速比Ｉｖを、動力循
環モードのときには必要とされる後退側の最ハイ変速比
ＩｖRevに、無段変速機直結モードのときには必要とさ
れる前進側の最ハイ変速比ＩｖHiにすることが可能とな
って、無段変速機の変速比範囲を有効に活用できるた
め、前記従来例のように無段変速機を大型化する必要が
なくなって、変速比無限大無段変速機の小型軽量化を推
進できる。The second invention comprises a ring gear connected to the output shaft of the continuously variable transmission, a carrier composed of a single pinion and connected to the output shaft of the constant transmission, and a sun gear connected to the unit output shaft. Since the relationship between the gear ratio α of the planetary gear mechanism and the gear ratio width λ of the continuously variable transmission is set to a value equal to or substantially equal to the above equation (B), the minimum (maximum high speed of the continuously variable transmission is ) In the gear ratio IcHi, the total gear ratio Iv of the continuously variable transmission with infinite gear ratio is set to the highest gear ratio IvRev on the reverse side which is required in the power circulation mode, and is required in the continuously variable transmission direct connection mode. The maximum gear ratio IvHi on the forward side can be set, and the gear ratio range of the continuously variable transmission can be effectively utilized. Therefore, it is necessary to increase the size of the continuously variable transmission as in the conventional example. Gone, infinite gear ratio It can promote the size and weight of the continuously variable transmission.
【００３４】また、第３の発明は、無段変速機の出力軸
に連結したサンギヤ、一定変速機の出力軸に連結したリ
ングギヤ及びダブルピニオンで構成されてユニット出力
軸に連結したキャリアとからなる遊星歯車機構のギヤ比
αと無段変速機の変速比幅λの関係を、上記（Ｃ）式に
等しいか、またはほぼ等しい値に設定する構成としたた
め、無段変速機の最小（最ハイ）変速比ＩｃHiにおい
て、変速比無限大無段変速機の総変速比Ｉｖを、動力循
環モードのときには必要とされる後退側の最ハイ変速比
ＩｖRevに、無段変速機直結モードのときには必要とさ
れる前進側の最ハイ変速比ＩｖHiにすることが可能とな
って、無段変速機の変速比範囲を有効に活用できるた
め、前記従来例のように無段変速機を大型化する必要が
なくなって、変速比無限大無段変速機の小型軽量化を推
進できる。The third invention comprises a sun gear connected to the output shaft of the continuously variable transmission, a ring gear connected to the output shaft of the constant transmission, and a carrier composed of a double pinion and connected to the unit output shaft. Since the relationship between the gear ratio α of the planetary gear mechanism and the gear ratio width λ of the continuously variable transmission is set to a value equal to or substantially equal to the above formula (C), the minimum (highest maximum ) In the gear ratio IcHi, the total gear ratio Iv of the continuously variable transmission with infinite gear ratio is set to the highest gear ratio IvRev on the reverse side which is required in the power circulation mode, and is required in the continuously variable transmission direct connection mode. The maximum gear ratio IvHi on the forward side can be set, and the gear ratio range of the continuously variable transmission can be effectively utilized. Therefore, it is necessary to increase the size of the continuously variable transmission as in the conventional example. Gone, infinite gear ratio It can promote the size and weight of the variable transmission.
【００３５】また、第４の発明は、ダブルピニオンで構
成されて無段変速機の出力軸に連結したキャリア、一定
変速機の出力軸に連結したリングギヤ及びユニット出力
軸に連結したサンギヤとからなる遊星歯車機構のギヤ比
αと無段変速機の変速比幅λの関係を、上記（Ｄ）式に
等しいか、またはほぼ等しい値に設定する構成としたた
め、無段変速機の最小（最ハイ）変速比ＩｃHiにおい
て、変速比無限大無段変速機の総変速比Ｉｖを、動力循
環モードのときには必要とされる後退側の最ハイ変速比
ＩｖRevに、無段変速機直結モードのときには必要とさ
れる前進側の最ハイ変速比ＩｖHiにすることが可能とな
って、無段変速機の変速比範囲を有効に活用できるた
め、前記従来例のように無段変速機を大型化する必要が
なくなって、変速比無限大無段変速機の小型軽量化を推
進できる。The fourth aspect of the invention comprises a carrier which is composed of a double pinion and is connected to the output shaft of the continuously variable transmission, a ring gear which is connected to the output shaft of the constant transmission, and a sun gear which is connected to the unit output shaft. Since the relationship between the gear ratio α of the planetary gear mechanism and the speed ratio width λ of the continuously variable transmission is set to a value equal to or substantially equal to the above equation (D), the minimum (highest maximum ) In the gear ratio IcHi, the total gear ratio Iv of the continuously variable transmission with infinite gear ratio is set to the highest gear ratio IvRev on the reverse side which is required in the power circulation mode, and is required in the continuously variable transmission direct connection mode. The maximum gear ratio IvHi on the forward side can be set, and the gear ratio range of the continuously variable transmission can be effectively utilized. Therefore, it is necessary to increase the size of the continuously variable transmission as in the conventional example. Gone, infinite gear ratio It can promote the size and weight of the variable transmission.
【００３６】[0036]
【発明の実施の形態】以下、本発明の一実施形態を添付
図面に基づいて説明する。BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below with reference to the accompanying drawings.
【００３７】図１は、前記従来例の図９に示したトロイ
ダル型無段変速機を用いて、変速比無限大無段変速機を
構成した一例を示しており、前記従来例の遊星歯車機構
５を、無段変速機２の変速比幅λに対応したギヤ比αを
備える遊星歯車機構１０５に代えたもので、その他は前
記従来例と同様に構成されており、同一のものに同一の
符号を付して重複説明を省略する。FIG. 1 shows an example in which a continuously variable transmission having an infinite transmission ratio is constructed by using the toroidal type continuously variable transmission shown in FIG. 9 of the conventional example, and the planetary gear mechanism of the conventional example is shown. 5 is replaced with a planetary gear mechanism 105 having a gear ratio α corresponding to the gear ratio width λ of the continuously variable transmission 2, and the other components are configured in the same manner as the above-mentioned conventional example, and are the same as the same components. The same reference numerals are given and duplicate explanations are omitted.
【００３８】遊星歯車機構１０５は、無段変速機２の出
力を受ける無段変速機出力ギヤ列４０（２ａ、４０ａ、
４ａ）の出力軸４に連結されたサンギヤ１０５ａと、動
力循環モードクラッチ９を介して一定変速機３のギヤ３
ｂへ選択的に締結される出力軸３ｃに連結されたキャリ
ア１０５ｂと、ユニット出力軸６に結合されたリングギ
ヤ１０５ｃから構成され、前記従来例と異なる点は、遊
星歯車機構１０５のギヤ比α（＝サンギヤ１０５ａの歯
数／リングギヤ１０５ｃの歯数）が、無段変速機２の変
速比幅λに応じて次式のように設定される。The planetary gear mechanism 105 receives the output of the continuously variable transmission 2 and continuously variable transmission output gear train 40 (2a, 40a,
4a) the sun gear 105a connected to the output shaft 4 and the gear 3 of the constant transmission 3 via the power circulation mode clutch 9.
It is composed of a carrier 105b connected to the output shaft 3c that is selectively fastened to b, and a ring gear 105c connected to the unit output shaft 6. The difference from the conventional example is that the gear ratio α of the planetary gear mechanism 105 ( = The number of teeth of the sun gear 105a / the number of teeth of the ring gear 105c) is set according to the gear ratio width λ of the continuously variable transmission 2 according to the following equation.
【００３９】[0039]
【数１１】 [Equation 11]
【００４０】ここで、λは無段変速機２の変速比幅であ
り、無段変速機２の変速比Ｉｃの範囲は、Here, λ is the speed ratio width of the continuously variable transmission 2, and the range of the speed ratio Ic of the continuously variable transmission 2 is
【００４１】[0041]
【数１２】 [Equation 12]
【００４２】のように表される。It is expressed as follows.
【００４３】すなわち、無段変速機２の最大（最ロー）
変速比ＩｃLOWと、無段変速機２の最小（最ハイ）変速
比ＩｃHiは、That is, the maximum (lowest) of the continuously variable transmission 2
The gear ratio IcLOW and the minimum (highest) gear ratio IcHi of the continuously variable transmission 2 are
【００４４】[0044]
【数１３】 [Equation 13]
【００４５】で、それぞれ表される。Are respectively represented by
【００４６】また、ＩｖHiは変速比無限大無段変速機に
必要とされる前進側最ハイ変速比、ＩｖRevは、変速比
無限大無段変速機に必要とされる後退側最ハイ変速比で
ある。Further, IvHi is the forward maximum gear ratio required for the infinitely variable transmission continuously variable transmission, and IvRev is the backward maximum gear ratio required for the infinitely variable transmission continuously variable transmission. is there.
【００４７】なお、前記従来例と同様に、動力循環モー
ドと無段変速機直結モードとの切り換えを段差なく滑ら
かに行うことができるよう、一定変速機３の変速比Ｉｇ
は、無段変速機出力ギヤ列４０の変速比Ｉｄを用いて次
式を満たすよう設定されている。As in the case of the conventional example, the gear ratio Ig of the constant transmission 3 is set so that the power circulation mode and the continuously variable transmission direct connection mode can be smoothly switched without a step.
Is set to satisfy the following equation using the gear ratio Id of the continuously variable transmission output gear train 40.
【００４８】[0048]
【数１４】 [Equation 14]
【００４９】以上のように構成され、次に作用について
説明する。With the above construction, the operation will be described.
【００５０】無段変速機２の最小変速比ＩｃHiのときに
無段変速機直結モードにおいて、変速比無限大無段変速
機の総変速比Ｉｖが必要とされる前進側最ハイ変速比Ｉ
ｖHiとなるとすれば、上記（１）式から無段変速機出力
ギヤ列４０の変速比Ｉｄは、When the minimum speed ratio IcHi of the continuously variable transmission 2 is set, in the continuously variable transmission direct connection mode, the total speed ratio Iv of the continuously variable transmission having an infinite speed ratio is required.
Assuming vHi, the gear ratio Id of the continuously variable transmission output gear train 40 can be calculated from the equation (1) above.
【００５１】[0051]
【数１５】 [Equation 15]
【００５２】で表される。It is represented by
【００５３】また、動力循環モードにおいて、変速比無
限大無段変速機の総変速比Ｉｖが必要とされる後退側最
ハイ変速比ＩｖRevとなる無段変速機２の変速比ＩｃRev
は、Further, in the power circulation mode, the gear ratio IcRev of the continuously variable transmission 2 at which the total gear ratio Iv of the infinite gear ratio continuously variable transmission becomes the required backward maximum gear ratio IvRev
Is
【００５４】[0054]
【数１６】 [Equation 16]
【００５５】となるから、ＩｃRevは、次の関係式を満
たす。Therefore, IcRev satisfies the following relational expression.
【００５６】[0056]
【数１７】 [Equation 17]
【００５７】ここで、遊星歯車機構１０５のギヤ比α
は、上記（５）式のように設定されているので、上記
（１２）式は、Here, the gear ratio α of the planetary gear mechanism 105
Is set as in the above equation (5), the above equation (12) is
【００５８】[0058]
【数１８】 [Equation 18]
【００５９】となり、無段変速機２の最小（最ハイ）変
速比ＩｃHi＝１／λ1/2において、変速比無限大無段変
速機の総減速比Ｉｖは、無段変速機直結モードのとき
は、必要とされる前進側最ハイ変速比となり、動力循環
モードのときは、必要とされる後退側最ハイ変速比とな
ることがわかる。Therefore, at the minimum (highest) gear ratio IcHi = 1 / λ 1/2 of the continuously variable transmission 2 , the total speed reduction ratio Iv of the continuously variable transmission having an infinite gear ratio is equal to that of the continuously variable transmission direct connection mode. It can be seen that the maximum forward gear ratio is required at this time, and the required maximum reverse gear ratio at the time of power circulation mode.
【００６０】実際に数値をあてはめて、計算してみる。
無段変速機の変速比幅λと、ファイナルギヤ列減速比Ｉ
ｆを、
λ＝４
Ｉｆ＝３
に設定し、変速比無限大無段変速機に必要とされる前進
側最ハイ変速比ＩｖHiと必要とされる後退側最ハイ変速
比ＩｖRevを、
ＩｖHi＝1.2
IvRev＝−7.5
にそれぞれ設定すると、変速比無限大無段変速機の諸元
設定は、上記式より、Apply numerical values and calculate.
The gear ratio width λ of the continuously variable transmission and the final gear train reduction ratio I
f is set to λ = 4 If = 3, and the forward-side maximum gear ratio IvHi required for the infinite gear ratio continuously variable transmission and the required reverse-side maximum gear ratio IvRev are set to IvHi = 1.2. When IvRev = -7.5 is set, the specifications of the continuously variable transmission with infinite transmission ratio are
【００６１】[0061]
【数１９】 [Formula 19]
【００６２】のようになる。It becomes as follows.
【００６３】したがって、遊星歯車機構１０５のギヤ比
αは、上記（５）式より、Therefore, the gear ratio α of the planetary gear mechanism 105 is calculated from the above equation (5) as follows:
【００６４】[0064]
【数２０】 [Equation 20]
【００６５】となる。It becomes
【００６６】この場合の無段変速機の変速比Ｉｃと変速
比無限大無段変速機の総変速比Ｉｖの逆数の関係は図２
に示すようになる。In this case, the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the total gear ratio Iv of the infinitely variable transmission is shown in FIG.
As shown in.
【００６７】したがって、無段変速機２の最小変速比
（最ハイ）ＩｃHiにおいて、変速比無限大無段変速機の
総変速比Ｉｖは、動力循環モードのときに必要とされる
後退側最ハイ変速比ＩｖRevとなる一方、無段変速機直
結モードのときには、必要とされる前進側最ハイ変速比
ＩｖHiとなるため、無段変速機２の変速比範囲を有効に
活用できる。Therefore, at the minimum speed ratio (highest) IcHi of the continuously variable transmission 2, the total speed ratio Iv of the continuously variable transmission having an infinite speed ratio is the highest speed on the reverse side required in the power circulation mode. While the gear ratio becomes IvRev, in the continuously variable transmission direct-coupling mode, the required forward-side highest gear ratio IvHi is obtained, so that the gear ratio range of the continuously variable transmission 2 can be effectively utilized.
【００６８】こうして、遊星歯車機構１０５のギヤ比α
と無段変速機２の変速比幅λの関係を、上記（５）式も
しくは、それにほぼ等しい値に設定する構成としたた
め、無段変速機２の最小（最ハイ）変速比ＩｃHiにおい
て、変速比無限大無段変速機の総変速比Ｉｖを、動力循
環モードのときには必要とされる後退側最ハイ変速比Ｉ
ｖRev、無段変速機直結モードのときには必要とされる
前進側最ハイ変速比ＩｖHiにすることができ、無段変速
機の変速比範囲を有効に活用できるため、前記従来例の
ように無段変速機を大型化する必要がなくなって、変速
比無限大無段変速機の小型軽量化を可能にすることがで
きる。Thus, the gear ratio α of the planetary gear mechanism 105 is
Since the relationship between the gear ratio width λ of the continuously variable transmission 2 and the gear ratio width λ of the continuously variable transmission 2 is set to the above expression (5) or a value substantially equal thereto, the gear change is performed at the minimum (highest) gear ratio IcHi of the continuously variable transmission 2. The total gear ratio Iv of the infinite ratio continuously variable transmission is set to the reverse side highest gear ratio I required in the power circulation mode.
In the vRev and continuously variable transmission direct connection modes, the required forward maximum gear ratio IvHi can be achieved, and the gear ratio range of the continuously variable transmission can be effectively utilized. Since it is not necessary to increase the size of the transmission, it is possible to reduce the size and weight of the continuously variable transmission with an infinite transmission ratio.
【００６９】図３は、第２の実施形態を示し、前記第１
実施形態の変速比無限大無段変速機における遊星歯車機
構１０５を遊星歯車機構２０５に変更したもので、その
他の構成は、前記第１実施形態と同様である。FIG. 3 shows a second embodiment, in which the first
The planetary gear mechanism 105 in the infinitely variable transmission continuously variable transmission according to the embodiment is replaced with the planetary gear mechanism 205, and the other configurations are the same as those in the first embodiment.
【００７０】遊星歯車機構２０５は、シングルピニオン
のキャリア２０５ｂを備え、このキャリア２０５ｂを一
定変速機３の出力軸３ｃに結合し、サンギヤ２０５ａを
ユニット出力軸６に、リングギヤ２０５ｃを無段変速機
２と連結された出力軸４にそれぞれ結合したものであ
る。The planetary gear mechanism 205 comprises a single pinion carrier 205b, which is connected to the output shaft 3c of the constant transmission 3, the sun gear 205a being the unit output shaft 6, and the ring gear 205c being the continuously variable transmission 2. Are connected to the output shafts 4 which are respectively connected to.
【００７１】遊星歯車機構２０５のギヤ比α（＝サンギ
ヤ２０５ａの歯数／リングギヤ２０５ｃの歯数）は、次
式のように設定されている。The gear ratio α of the planetary gear mechanism 205 (= the number of teeth of the sun gear 205a / the number of teeth of the ring gear 205c) is set by the following equation.
【００７２】[0072]
【数２１】 [Equation 21]
【００７３】ここで、λは無段変速機２の変速比幅であ
り、変速比Ｉｃの範囲は、上記（６）式と同様である。Here, λ is the speed ratio width of the continuously variable transmission 2, and the range of the speed ratio Ic is the same as that of the above equation (6).
【００７４】すなわち、無段変速機２の最大（最ロー）
変速比ＩｃLOWは、上記（７）式と同様に、無段変速機
２の最小（最ハイ）変速比ＩｃHiは、上記（８）式と同
様に、それぞれ表される。That is, the maximum (lowest) of the continuously variable transmission 2
The gear ratio IcLOW is expressed in the same manner as in the expression (7), and the minimum (highest) gear ratio IcHi in the continuously variable transmission 2 is expressed in the same manner as in the expression (8).
【００７５】また、ＩｖHiは変速比無限大無段変速機に
必要とされる前進側最ハイ変速比、ＩｖRevは、変速比
無限大無段変速機に必要とされる後退側最ハイ変速比で
ある。IvHi is the maximum forward gear ratio required for an infinitely variable transmission continuously variable transmission, and IvRev is the maximum backward gear ratio required for an infinitely variable transmission continuously variable transmission. is there.
【００７６】なお、前記従来例と同様に、動力循環モー
ドと無段変速機直結モードとの切り換えを段差なく滑ら
かに行うことができるよう、一定変速機３の変速比Ｉｇ
は、無段変速機出力ギヤ列４０の変速比Ｉｄを用いて上
記（９）式の関係を満たすよう設定されている。As in the conventional example, the gear ratio Ig of the constant transmission 3 is set so that the power circulation mode and the continuously variable transmission direct coupling mode can be smoothly switched without any step.
Is set so as to satisfy the relationship of the above expression (9) by using the gear ratio Id of the continuously variable transmission output gear train 40.
【００７７】無段変速機直結モードにおいて、無段変速
機２が最小（最ハイ）変速比ＩｃHiのときに、変速比無
限大無段変速機の総変速比Ｉｖが必要とされる前進側最
ハイ変速比ＩｖHiとなるとすれば、無段変速機出力ギヤ
列４０の変速比Ｉｄは、上記と同様に（１）式から（１
０）式で表される。In the continuously variable transmission direct connection mode, when the continuously variable transmission 2 has the minimum (highest) gear ratio IcHi, the total gear ratio Iv of the continuously variable continuously variable transmission is required. Assuming that the high gear ratio IvHi is obtained, the gear ratio Id of the continuously variable transmission output gear train 40 can be calculated from the equation (1) by
It is represented by the formula 0).
【００７８】また、動力循環モードにおいて、変速比無
限大無段変速機の総変速比Ｉｖが必要とされる後退側最
ハイ変速比ＩｖRevとなる無段変速機２の変速比ＩｃRev
は、Further, in the power circulation mode, the gear ratio IcRev of the continuously variable transmission 2 at which the total gear ratio Iv of the infinite gear ratio continuously variable transmission becomes the required backward maximum gear ratio IvRev
Is
【００７９】[0079]
【数２２】 [Equation 22]
【００８０】となるから、ＩｃRevは、次の関係式を満
たす。Therefore, IcRev satisfies the following relational expression.
【００８１】[0081]
【数２３】 [Equation 23]
【００８２】ここで、遊星歯車機構２０５のギヤ比α
は、上記（１６）式のように設定されているので、この
（１８）式は、Here, the gear ratio α of the planetary gear mechanism 205
Is set as in the above equation (16), the equation (18) is
【００８３】[0083]
【数２４】 [Equation 24]
【００８４】となり、無段変速機２の最小（最ハイ）変
速比ＩｃHi＝１／λ1/2において、変速比無限大無段変
速機の総減速比Ｉｖは、無段変速機直結モードのとき
は、必要とされる前進側最ハイ変速比となり、動力循環
モードのときは、必要とされる後退側最ハイ変速比とな
ることがわかる。Therefore, at the minimum (highest) gear ratio IcHi = 1 / λ 1/2 of the continuously variable transmission 2 , the total reduction ratio Iv of the continuously variable transmission having an infinite gear ratio is equal to that of the continuously variable transmission direct coupling mode. It can be seen that the maximum forward gear ratio is required at this time, and the required maximum reverse gear ratio at the time of power circulation mode.
【００８５】実際に数値をあてはめて、計算してみる。
無段変速機の変速比幅λと、ファイナルギヤ列減速比Ｉ
ｆを、
λ＝２
Ｉｆ＝３
に設定し、変速比無限大無段変速機に必要とされる前進
側最ハイ変速比ＩｖHiと必要とされる後退側最ハイ変速
比ＩｖRevを、
ＩｖHi＝1.2
ＩｖRev＝−7.5
にそれぞれ設定すると、変速比無限大無段変速機の諸元
設定は、上記式より、Actually apply numerical values and calculate.
The gear ratio width λ of the continuously variable transmission and the final gear train reduction ratio I
f is set to λ = 2 If = 3, and the forward-side maximum gear ratio IvHi required for the infinite gear ratio continuously variable transmission and the required reverse-side maximum gear ratio IvRev are set to IvHi = 1.2. When IvRev = −7.5 is set, the specifications of the continuously variable transmission with infinite gear ratio are
【００８６】[0086]
【数２５】 [Equation 25]
【００８７】この場合、遊星歯車機構２０５のギヤ比α
は、上記（１６）式よりIn this case, the gear ratio α of the planetary gear mechanism 205
Is from the above equation (16)
【００８８】[0088]
【数２６】 [Equation 26]
【００８９】となる。この場合の無段変速機の変速比Ｉ
ｃと変速比無限大無段変速機の総変速比Ｉｖの逆数の関
係は図４に示すようになる。It becomes The gear ratio I of the continuously variable transmission in this case
The relationship between c and the reciprocal of the total gear ratio Iv of the continuously variable transmission with infinite gear ratio is shown in FIG.
【００９０】したがって、無段変速機２の最小（最ハ
イ）変速比ＩｃHiにおいて、変速比無限大無段変速機の
総変速比Ｉｖは、動力循環モードのときに必要とされる
後退側最ハイ変速比ＩｖRevに設定される一方、無段変
速機直結モードのときには、必要とされる前進側最ハイ
変速比ＩｖHiとなるため、無段変速機２の変速比範囲を
有効に活用できる。Therefore, at the minimum (highest) gear ratio IcHi of the continuously variable transmission 2, the total gear ratio Iv of the continuously variable transmission having an infinite gear ratio is the highest gear on the reverse side required in the power circulation mode. While the gear ratio is set to IvRev, in the continuously variable transmission direct-coupling mode, the required forward-side highest gear ratio IvHi is obtained, so that the gear ratio range of the continuously variable transmission 2 can be effectively utilized.
【００９１】こうして、遊星歯車機構２０５のギヤ比α
と無段変速機２の変速比幅λの関係を、上記（１６）式
もしくは、それにほぼ等しい値に設定する構成としたた
め、無段変速機２の最小（最ハイ）変速比ＩｃHiにおい
て、変速比無限大無段変速機の総変速比Ｉｖを、動力循
環モードのときには必要とされる後退側最ハイ変速比Ｉ
ｖRev、無段変速機直結モードのときには必要とされる
前進側最ハイ変速比ＩｖHiに設定することができ、無段
変速機２の変速比範囲を有効に活用できるため、前記従
来例のように無段変速機を大型化する必要がなく、変速
比無限大無段変速機の小型軽量化を可能にすることがで
きる。Thus, the gear ratio α of the planetary gear mechanism 205 is
And the gear ratio width λ of the continuously variable transmission 2 are set to the above formula (16) or a value substantially equal to the formula (16), the gear ratio is changed at the minimum (highest) gear ratio IcHi of the continuously variable transmission 2. The total gear ratio Iv of the infinite ratio continuously variable transmission is set to the reverse side highest gear ratio I required in the power circulation mode.
In the vRev and continuously variable transmission direct-coupling modes, it is possible to set the forward side highest gear ratio IvHi required, and the gear ratio range of the continuously variable transmission 2 can be effectively utilized. It is not necessary to upsize the continuously variable transmission, and it is possible to reduce the size and weight of the infinitely variable transmission.
【００９２】図５は第３の実施形態を示し、前記第１実
施形態に示した遊星歯車機構１０５を、入出力の関係を
変更した遊星歯車機構３０５に置き換えたもので、その
他の構成は、前記第１実施形態と同様である。FIG. 5 shows a third embodiment, in which the planetary gear mechanism 105 shown in the first embodiment is replaced with a planetary gear mechanism 305 having a changed input / output relationship, and other configurations are as follows. This is the same as the first embodiment.
【００９３】遊星歯車機構３０５は、ダブルピニオンで
構成されたキャリア３０５ｂを備え、このキャリア３０
５ｂをユニット出力軸６に結合し、一定変速機３の出力
軸３ｃをリングギヤ３０５ｃに、無段変速機２と連結し
た出力軸４をサンギヤ３０５ａにそれぞれ結合したもの
である。The planetary gear mechanism 305 has a carrier 305b composed of a double pinion.
5b is connected to the unit output shaft 6, the output shaft 3c of the constant transmission 3 is connected to the ring gear 305c, and the output shaft 4 connected to the continuously variable transmission 2 is connected to the sun gear 305a.
【００９４】ダブルピニオン型のキャリア３０５ｂを備
えた遊星歯車機構３０５は、そのギヤ比α（＝サンギヤ
３０５ａの歯数／リングギヤ３０５ｃの歯数）が、次の
ように設定されている。The planetary gear mechanism 305 provided with the double pinion type carrier 305b has its gear ratio α (= the number of teeth of the sun gear 305a / the number of teeth of the ring gear 305c) set as follows.
【００９５】[0095]
【数２７】 [Equation 27]
【００９６】ここで、λは無段変速機２の変速比幅であ
り、変速比Ｉｃの範囲は、上記と同様であり、上記
（６）式で表される。Here, λ is the speed ratio width of the continuously variable transmission 2, the range of the speed ratio Ic is the same as above, and is represented by the above equation (6).
【００９７】すなわち、無段変速機２の最大（最ロー）
変速比ＩｃLOW及び最小（最ハイ）変速比ＩｃHiは、上
記（７）、（８）式で、それぞれ表される。That is, the maximum (lowest) of the continuously variable transmission 2
The gear ratio IcLOW and the minimum (highest) gear ratio IcHi are expressed by the above equations (7) and (8), respectively.
【００９８】また、ＩｖHiは変速比無限大無段変速機に
必要とされる前進側最ハイ変速比、ＩｖRevは、変速比
無限大無段変速機に必要とされる後退側最ハイ変速比で
ある。In addition, IvHi is the forward maximum gear ratio required for the infinitely variable transmission continuously variable transmission, and IvRev is the backward maximum gear ratio required for the infinitely variable transmission continuously variable transmission. is there.
【００９９】なお、上記と同様に、動力循環モードと無
段変速機直結モードとの切り換えを段差なく滑らかに行
うことができるよう、一定変速機３の変速比Ｉｇは、無
段変速機出力ギヤ列４０の変速比Ｉｄを用いて、上記
（９）式の関係を満たすよう設定されている。In the same manner as above, the gear ratio Ig of the constant transmission 3 is set so that the power circulation mode and the continuously variable transmission direct coupling mode can be smoothly switched without any step. The gear ratio Id of the row 40 is used to satisfy the relationship of the above equation (9).
【０１００】無段変速機２の最小（最ハイ）変速比Ｉｃ
Hiのときに無段変速機直結モードにおいて、変速比無限
大無段変速機の総変速比Ｉｖが必要とされる前進側最ハ
イ変速比ＩｖHiとなるとすれば、無段変速機出力ギヤ列
４０の変速比Ｉｄは、上記（１）式から（１０）式で表
される。Minimum (highest) gear ratio Ic of continuously variable transmission 2
If the total gear ratio Iv of the continuously variable transmission with infinite gear ratio becomes the required forward-side highest gear ratio IvHi in Hi direct mode, the continuously variable output gear train 40 The gear ratio Id is expressed by the above equations (1) to (10).
【０１０１】また、動力循環モードにおいて、変速比無
限大無段変速機の総変速比Ｉｖが、必要とされる後退側
最ハイ変速比ＩｖRevとなる無段変速機２の変速比ＩｃR
evは、Further, in the power circulation mode, the gear ratio IcR of the continuously variable transmission 2 becomes such that the total gear ratio Iv of the continuously variable transmission with infinite gear ratio becomes the required reverse side maximum gear ratio IvRev.
ev is
【０１０２】[0102]
【数２８】 [Equation 28]
【０１０３】となるから、ＩｃRevは次の関係式を満た
す。Therefore, IcRev satisfies the following relational expression.
【０１０４】[0104]
【数２９】 [Equation 29]
【０１０５】ここで、遊星歯車機構３０５のギヤ比α
は、上記（２０）式を満たすように設定されているので
上記（２２）式は、Here, the gear ratio α of the planetary gear mechanism 305
Is set to satisfy the above equation (20), the above equation (22) is
【０１０６】[0106]
【数３０】 [Equation 30]
【０１０７】となり、無段変速機２の最小（最ハイ）変
速比ＩｃHi＝１／λ1/2において、変速比無限大無段変
速機の総減速比Ｉｖは、無段変速機直結モードのとき
は、必要とされる前進側最ハイ変速比となり、動力循環
モードのときは、必要とされる後退側最ハイ変速比とな
ることがわかる。Therefore, at the minimum (highest) gear ratio IcHi = 1 / λ 1/2 of the continuously variable transmission 2 , the total reduction ratio Iv of the continuously variable transmission having an infinite gear ratio is equal to that of the continuously variable transmission direct coupling mode. It can be seen that the maximum forward gear ratio is required at this time, and the required maximum reverse gear ratio at the time of power circulation mode.
【０１０８】実際に数値をあてはめて、計算してみる。
無段変速機の変速比幅λと、ファイナルギヤ列減速比Ｉ
ｆを、
λ＝２
Ｉｆ＝３
に設定し、変速比無限大無段変速機に必要とされる前進
側最ハイ変速比ＩｖHiと必要とされる後退側最ハイ変速
比ＩｖRevを、
ＩｖHi＝1.2
ＩｖRev＝−7.5
にそれぞれ設定すると、変速比無限大無段変速機の諸元
設定は、上記式より、Apply numerical values and calculate.
The gear ratio width λ of the continuously variable transmission and the final gear train reduction ratio I
f is set to λ = 2 If = 3, and the forward-side maximum gear ratio IvHi required for the infinite gear ratio continuously variable transmission and the required reverse-side maximum gear ratio IvRev are set to IvHi = 1.2. When IvRev = −7.5 is set, the specifications of the continuously variable transmission with infinite gear ratio are
【０１０９】[0109]
【数３１】 [Equation 31]
【０１１０】この場合、遊星歯車機構３０５のギヤ比α
は、上記（２０）式よりIn this case, the gear ratio α of the planetary gear mechanism 305
Is from the above equation (20)
【０１１１】[0111]
【数３２】 [Equation 32]
【０１１２】となる。この場合の無段変速機の変速比Ｉ
ｃと変速比無限大無段変速機の総変速比Ｉｖの逆数の関
係は図６に示すようになる。[0112] The gear ratio I of the continuously variable transmission in this case
The relationship between c and the reciprocal of the total gear ratio Iv of the continuously variable transmission with infinite gear ratio is shown in FIG.
【０１１３】したがって、無段変速機２の最小（最ハ
イ）変速比ＩｃHiにおいて、変速比無限大無段変速機の
総変速比Ｉｖは、動力循環モードのとき、必要とされる
後退側最ハイ変速比ＩｖRev、無段変速機直結モードの
とき、必要とされる前進側最ハイ変速比ＩｖHiにそれぞ
れ設定できるため、無段変速機の変速比範囲を有効に活
用できる。Therefore, at the minimum (highest) gear ratio IcHi of the continuously variable transmission 2, the total gear ratio Iv of the continuously variable transmission having an infinite gear ratio is the highest gear on the reverse side required in the power circulation mode. The gear ratio IvRev and the required maximum forward gear ratio IvHi in the continuously variable transmission direct connection mode can be set respectively, so that the gear ratio range of the continuously variable transmission can be effectively utilized.
【０１１４】こうして、遊星歯車機構３０５のギヤ比α
と無段変速機２の変速比幅λの関係を、上記（２０）式
もしくは、それにほぼ等しい値に設定する構成としたた
め、無段変速機の最小（最ハイ）変速比ＩｃHiにおい
て、変速比無限大無段変速機の総変速比Ｉｖを、動力循
環モードのときに必要とされる後退側最ハイ変速比Ｉｖ
Rev、無段変速機直結モードのときに必要とされる前進
側最ハイ変速比ＩｖHiにそれぞれ設定することができ、
無段変速機２の変速比範囲を有効に活用することが可能
となって、前記従来例のように無段変速機を大型化する
必要がなくなって、変速比無限大無段変速機の小型軽量
化を可能にすることができる。Thus, the gear ratio α of the planetary gear mechanism 305 is
Since the relationship between the gear ratio width λ of the continuously variable transmission 2 and the gear ratio width λ of the continuously variable transmission 2 is set to the above expression (20) or a value substantially equal thereto, the gear ratio at the minimum (highest) gear ratio IcHi of the continuously variable transmission is set. The total gear ratio Iv of the infinitely variable transmission is set to the highest reverse gear ratio Iv required in the power circulation mode.
Rev, it is possible to set the forward side maximum gear ratio IvHi required in the continuously variable transmission direct connection mode,
Since the gear ratio range of the continuously variable transmission 2 can be effectively utilized, there is no need to increase the size of the continuously variable transmission as in the conventional example, and the infinitely variable gear ratio of the continuously variable transmission can be achieved. The weight can be reduced.
【０１１５】図７は、第４の実施形態を示し、前記第３
実施形態の遊星歯車機構３０５の入出力の関係を変更す
るとともに、キャリアをダブルピニオンで構成した遊星
歯車機構４０５に置き換えたもので、その他の構成は、
前記第３実施形態と同様である。FIG. 7 shows the fourth embodiment, and the third embodiment
The input / output relationship of the planetary gear mechanism 305 of the embodiment is changed, and the carrier is replaced with a planetary gear mechanism 405 configured by a double pinion. Other configurations are as follows.
This is similar to the third embodiment.
【０１１６】遊星歯車機構４０５は、ダブルピニオンで
構成されたキャリア４０５ｂを無段変速機２と連結した
出力軸４に結合し、リングギヤ４０５ｃを一定変速機３
の出力軸３ｃに、ユニット出力軸６をサンギヤ４０５ａ
にそれぞれ結合したものである。The planetary gear mechanism 405 connects the carrier 405b composed of a double pinion to the output shaft 4 connected to the continuously variable transmission 2 and the ring gear 405c to the constant transmission 3.
The unit output shaft 6 to the output shaft 3c of the sun gear 405a.
Are combined with each other.
【０１１７】ダブルピニオンのキャリア４０５ｂを備え
た遊星歯車機構４０５のギヤ比α（＝サンギヤ４０５ａ
の歯数／リングギヤ４０５ｃの歯数）は、次のように設
定される。The gear ratio α (= sun gear 405a) of the planetary gear mechanism 405 provided with the double pinion carrier 405b.
The number of teeth / the number of teeth of the ring gear 405c) is set as follows.
【０１１８】[0118]
【数３３】 [Expression 33]
【０１１９】ここで、λは無段変速機２の変速比幅であ
り、変速比Ｉｃの範囲は、上記と同様であり、上記
（６）式で表される。Here, λ is the gear ratio width of the continuously variable transmission 2, and the range of the gear ratio Ic is the same as above, and is represented by the above equation (6).
【０１２０】すなわち、無段変速機２の最大（最ロー）
変速比ＩｃLOW及び最小（最ハイ）変速比ＩｃHiは、上
記（７）、（８）式で、それぞれ表される。That is, the maximum (lowest) of the continuously variable transmission 2
The gear ratio IcLOW and the minimum (highest) gear ratio IcHi are expressed by the above equations (7) and (8), respectively.
【０１２１】また、ＩｖHiは変速比無限大無段変速機に
必要とされる前進側最ハイ変速比、ＩｖRevは、変速比
無限大無段変速機に必要とされる後退側最ハイ変速比で
ある。IvHi is the maximum forward gear ratio required for an infinitely variable transmission continuously variable transmission, and IvRev is the maximum backward gear ratio required for an infinitely variable transmission continuously variable transmission. is there.
【０１２２】なお、上記と同様に、動力循環モードと無
段変速機直結モードとの切り換えを段差なく滑らかに行
うことができるよう、一定変速機３の変速比Ｉｇは、無
段変速機出力ギヤ列４０の変速比Ｉｄを用いて、上記
（９）式の関係を満たすよう設定されている。In the same manner as described above, the gear ratio Ig of the constant transmission 3 is set so that the power circulation mode and the continuously variable transmission direct coupling mode can be smoothly switched without any step. The gear ratio Id of the row 40 is used to satisfy the relationship of the above equation (9).
【０１２３】無段変速機２の最小（最ハイ）変速比Ｉｃ
Hiのときに無段変速機直結モードにおいて、変速比無限
大無段変速機の総変速比Ｉｖが必要とされる前進側最ハ
イ変速比ＩｖHiとなるとすれば、無段変速機出力ギヤ列
４０の変速比Ｉｄは、上記（１）式から（１０）式で表
される。Minimum (highest) gear ratio Ic of continuously variable transmission 2
If the total gear ratio Iv of the continuously variable transmission with infinite gear ratio becomes the required forward-side highest gear ratio IvHi in Hi direct mode, the continuously variable output gear train 40 The gear ratio Id is expressed by the above equations (1) to (10).
【０１２４】また、動力循環モードにおいて、変速比無
限大無段変速機の総変速比Ｉｖが必要とされる後退側最
ハイ変速比ＩｖRevとなる無段変速機２の変速比ＩｃRev
は、Further, in the power circulation mode, the gear ratio IcRev of the continuously variable transmission 2 at which the total gear ratio Iv of the infinite gear ratio continuously variable transmission becomes the reverse-side highest gear ratio IvRev required.
Is
【０１２５】[0125]
【数３４】 [Equation 34]
【０１２６】となるから、ＩｃRevは次の関係式を満た
す。Therefore, IcRev satisfies the following relational expression.
【０１２７】[0127]
【数３５】 [Equation 35]
【０１２８】ここで、遊星歯車機構４０５のギヤ比α
は、上記（２４）式のように設定されているので上記
（２６）式は、Here, the gear ratio α of the planetary gear mechanism 405 is
Is set as in the above equation (24), the above equation (26) is
【０１２９】[0129]
【数３６】 [Equation 36]
【０１３０】となり、無段変速機２の最小（最ハイ）変
速比ＩｃHi＝１／λ1/2において、変速比無限大無段変
速機の総減速比Ｉｖは、無段変速機直結モードのとき
は、必要とされる前進側最ハイ変速比となり、動力循環
モードのときは、必要とされる後退側最ハイ変速比とな
ることがわかる。Therefore, at the minimum (highest) gear ratio IcHi = 1 / λ 1/2 of the continuously variable transmission 2 , the total speed reduction ratio Iv of the continuously variable transmission having an infinite gear ratio is equal to that of the continuously variable transmission direct connection mode. It can be seen that the maximum forward gear ratio is required at this time, and the required maximum reverse gear ratio at the time of power circulation mode.
【０１３１】実際に数値をあてはめて、計算してみる。
無段変速機の変速比幅λと、ファイナルギヤ列減速比Ｉ
ｆを、
λ＝３
Ｉｆ＝３
に設定し、変速比無限大無段変速機に必要とされる前進
側最ハイ変速比ＩｖHiと必要とされる後退側最ハイ変速
比ＩｖRevを、
ＩｖHi＝1.2
ＩｖRev＝−7.5
にそれぞれ設定すると、変速比無限大無段変速機の諸元
設定は、上記式より、Apply numerical values and calculate.
The gear ratio width λ of the continuously variable transmission and the final gear train reduction ratio I
f is set to λ = 3 If = 3, and the forward-side highest gear ratio IvHi required for the infinite gear ratio continuously variable transmission and the backward-side highest gear ratio IvRev required for IvHi = 1.2. When IvRev = −7.5 is set, the specifications of the continuously variable transmission with infinite gear ratio are
【０１３２】[0132]
【数３７】 [Equation 37]
【０１３３】この場合、遊星歯車機構４０５のギヤ比α
は、上記（２４）式よりIn this case, the gear ratio α of the planetary gear mechanism 405 is
Is from the above equation (24)
【０１３４】[0134]
【数３８】 [Equation 38]
【０１３５】となる。この場合の無段変速機２の変速比
Ｉｃと変速比無限大無段変速機の総変速比Ｉｖの逆数の
関係は図８に示すようになる。It becomes: In this case, the relationship between the gear ratio Ic of the continuously variable transmission 2 and the reciprocal of the total gear ratio Iv of the continuously variable continuously variable transmission is as shown in FIG.
【０１３６】したがって、無段変速機２の最小（最ハ
イ）変速比ＩｃHiにおいて、変速比無限大無段変速機の
総変速比Ｉｖは、動力循環モードのとき、必要とされる
後退側最ハイ変速比ＩｖRev、無段変速機直結モードの
とき、必要とされる前進側最ハイ変速比ＩｖHiＩ．Ｈｉ
に設定することが可能となって、無段変速機２の変速比
範囲を有効に活用できる。Therefore, at the minimum (highest) gear ratio IcHi of the continuously variable transmission 2, the total gear ratio Iv of the continuously variable transmission having an infinite gear ratio is the highest gear on the reverse side required in the power circulation mode. When the gear ratio IvRev and the continuously variable transmission direct connection mode are set, the maximum forward gear ratio IvHiI. Hi
Can be set to, and the gear ratio range of the continuously variable transmission 2 can be effectively utilized.
【０１３７】こうして、遊星歯車機構４０５のギヤ比α
と無段変速機２の変速比幅λの関係を、上記（２４）式
もしくは、もしくは、それにほぼ等しい値に設定する構
成としたため、無段変速機の最小（最ハイ）変速比Ｉｃ
Hiにおいて、変速比無限大無段変速機の総変速比Ｉｖ
を、動力循環モードのときには必要とされる後退側最ハ
イ変速比ＩｖRevに、無段変速機直結モードのときには
必要とされる前進側最ハイ変速比ＩｖHiにそれぞれ設定
することができ、無段変速機２の変速比範囲を有効に活
用できるため、前記従来例のように無段変速機を大型化
することなく、変速比無限大無段変速機の小型軽量化を
可能にすることができる。Thus, the gear ratio α of the planetary gear mechanism 405 is
Since the relationship between the transmission ratio width λ of the continuously variable transmission 2 and the gear ratio width λ of the continuously variable transmission 2 is set to the above formula (24) or a value substantially equal thereto, the minimum (highest) gear ratio Ic of the continuously variable transmission is set.
At Hi, the total gear ratio Iv of the continuously variable transmission with infinite gear ratio
Can be set to the maximum backward gear ratio IvRev required in the power circulation mode and to the maximum forward gear ratio IvHi required in the continuously variable transmission direct connection mode. Since the gear ratio range of the machine 2 can be effectively utilized, it is possible to reduce the size and weight of the infinite gear ratio continuously variable transmission without increasing the size of the continuously variable transmission as in the conventional example.
【図１】本発明の一実施形態を示す変速比無限大無段変
速機の概念図。FIG. 1 is a conceptual diagram of an infinitely variable transmission continuously variable transmission according to an embodiment of the present invention.
【図２】同じく無段変速機の変速比Ｉｃとファイナルギ
ヤ減速比Ｉｆを含んだユニット総変速比Ｉｖの逆数の関
係を示すグラフ。FIG. 2 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio If.
【図３】第２の実施形態を示す変速比無限大無段変速機
の概念図。FIG. 3 is a conceptual diagram of an infinitely variable transmission continuously variable transmission according to a second embodiment.
【図４】同じく無段変速機の変速比Ｉｃとファイナルギ
ヤ減速比を含んだユニット総変速比Ｉｖの逆数との関係
を示すグラフ。FIG. 4 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio.
【図５】第３の実施形態を示す変速比無限大無段変速機
の概念図。FIG. 5 is a conceptual diagram of an infinitely variable transmission continuously variable transmission according to a third embodiment.
【図６】同じく無段変速機の変速比Ｉｃとファイナルギ
ヤ減速比を含んだユニット総変速比Ｉｖの逆数との関係
を示すグラフ。FIG. 6 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio.
【図７】第４の実施形態を示す変速比無限大無段変速機
の概念図。FIG. 7 is a conceptual diagram of an infinitely variable transmission continuously variable transmission according to a fourth embodiment.
【図８】同じく無段変速機の変速比Ｉｃとファイナルギ
ヤ減速比を含んだユニット総変速比Ｉｖの逆数との関係
を示すグラフ。FIG. 8 is a graph showing a relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio.
【図９】従来の変速比無限大無段変速機を示す概念図。FIG. 9 is a conceptual diagram showing a conventional infinitely variable transmission continuously variable transmission.
【図１０】同じく従来例で、無段変速機の変速比Ｉｃと
ファイナルギヤ減速比を含んだユニット総変速比Ｉｖの
逆数との関係を示すグラフ。FIG. 10 is a graph showing the relationship between the gear ratio Ic of the continuously variable transmission and the reciprocal of the unit total gear ratio Iv including the final gear reduction ratio in the same conventional example.
１ ユニット入力軸 ２ 無段変速機 ２ａ 無段変速機出力ギヤ ３ 一定変速機 ３ａ 入力ギヤ ３ｂ ギヤ ３ｃ 一定変速機出力軸 ４ 無段変速機出力軸 ４ａ ギヤ ６ ユニット出力軸 ７ 変速機出力ギヤ ８ 差動ギヤ ９ 動力循環モードクラッチ １０ 直結モードクラッチ １１ａ、１１ｂ 駆動軸 １２ ファイナルギヤ列 １２ａ ファイナルギヤ ２０ パワーローラ ２１ 入力ディスク ２２ 出力ディスク ４０ 無段変速機出力ギヤ列 １０５ 遊星歯車機構 １０５ａ サンギヤ １０５ｂ キャリア １０５ｃ リングギヤ ２０５ 遊星歯車機構 ２０５ａ サンギヤ ２０５ｂ キャリア ２０５ｃ リングギヤ ３０５ 遊星歯車機構 ３０５ａ サンギヤ ３０５ｂ キャリア ３０５ｃ リングギヤ ４０５ 遊星歯車機構 ４０５ａ サンギヤ ４０５ｂ キャリア ４０５ｃ リングギヤ 1 unit input shaft 2 continuously variable transmission 2a continuously variable transmission output gear 3 constant transmission 3a input gear 3b gear 3c constant transmission output shaft 4 Continuously variable transmission output shaft 4a gear 6 unit output shaft 7 Transmission output gear 8 differential gear 9 Power circulation mode clutch 10 Direct connection mode clutch 11a, 11b drive shaft 12 Final gear train 12a Final gear 20 power rollers 21 Input Disc 22 Output disc 40 continuously variable transmission output gear train 105 Planetary gear mechanism 105a sun gear 105b carrier 105c ring gear 205 Planetary gear mechanism 205a sun gear 205b carrier 205c ring gear 305 Planetary gear mechanism 305a Sun gear 305b carrier 305c ring gear 405 Planetary gear mechanism 405a Sun Gear 405b carrier 405c ring gear
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F16H 37/02 ─────────────────────────────────────────────────── ─── Continuation of front page (58) Fields surveyed (Int.Cl. 7 , DB name) F16H 37/02
Claims (4)
変速機及び一定変速機と、 無段変速機の出力軸に連結したサンギヤ、シングルピニ
オンで構成されて一定変速機の出力軸に連結したキャリ
ア及びユニット出力軸に連結したリングギヤとからなる
遊星歯車機構と、 前記ユニット入力軸から遊星歯車機構のキャリアへの動
力伝達経路の途中に介装された動力循環モードクラッチ
と、 前記無段変速機の出力軸からユニット出力軸の動力伝達
経路の途中に介装されて無段変速機の出力軸とユニット
出力軸を選択的に締結または遊星歯車機構の相互に歯合
する前記回転要素を選択的に固定する直結モードクラッ
チとを備えて、前記動力循環モードクラッチと直結モー
ドクラッチとを選択的に締結、解除可能な変速比無限大
無段変速機において、 変速比無限大無段変速機の前進側最ハイ変速比をＩｖHi
とし、同じく後退側最ハイ変速比をＩｖRevとするとと
もに、前記無段変速機の変速比幅をλとすると、 前記遊星歯車機構のサンギヤの歯数／リングギヤの歯数
で表されるギヤ比αは、 【数１】 に設定されたことを特徴とする変速比無限大無段変速
機。1. A continuously variable transmission and a constant transmission, each connected to a unit input shaft, a sun gear connected to an output shaft of the continuously variable transmission, and a single pinion, which are connected to an output shaft of the constant transmission. A planetary gear mechanism including a carrier and a ring gear connected to the unit output shaft; a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the carrier of the planetary gear mechanism; and the continuously variable transmission. The output element of the continuously variable transmission to selectively engage the output shaft of the continuously variable transmission or the output shaft of the unit output shaft with the output element of In a continuously variable transmission having an infinite transmission ratio capable of engaging and disengaging the power circulation mode clutch and the direct coupling mode clutch, the direct coupling mode clutch being fixed to Infinite transmission ratio The maximum forward transmission speed ratio of the continuously variable transmission is IvHi
Similarly, when the reverse side highest gear ratio is IvRev and the gear ratio width of the continuously variable transmission is λ, the gear ratio α represented by the number of teeth of the sun gear of the planetary gear mechanism / the number of teeth of the ring gear is α. Is the following An infinitely variable transmission with infinite transmission ratio.
変速機及び一定変速機と、 無段変速機の出力軸に連結したリングギヤ、シングルピ
ニオンで構成されて一定変速機の出力軸に連結したキャ
リア及びユニット出力軸に連結したサンギヤとからなる
遊星歯車機構と、 前記ユニット入力軸から遊星歯車機構のキャリアへの動
力伝達経路の途中に介装された動力循環モードクラッチ
と、 前記無段変速機の出力軸からユニット出力軸の動力伝達
経路の途中に介装されて無段変速機の出力軸とユニット
出力軸を選択的に締結または遊星歯車機構の相互に歯合
する前記回転要素を選択的に固定する直結モードクラッ
チとを備えて、前記動力循環モードクラッチと直結モー
ドクラッチとを選択的に締結、解除可能な変速比無限大
無段変速機において、 変速比無限大無段変速機の前進側最ハイ変速比をＩｖHi
とし、同じく後退側最ハイ変速比をＩｖRevとするとと
もに、前記無段変速機の変速比幅をλとすると、 前記遊星歯車機構のサンギヤの歯数／リングギヤの歯数
で表されるギヤ比αは、 【数２】 に設定されたことを特徴とする変速比無限大無段変速
機。2. A continuously variable transmission and a constant transmission, each connected to a unit input shaft, a ring gear connected to the output shaft of the continuously variable transmission, and a single pinion, which are connected to the output shaft of the constant transmission. A planetary gear mechanism consisting of a carrier and a sun gear connected to a unit output shaft; a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the carrier of the planetary gear mechanism; and the continuously variable transmission. The output element of the continuously variable transmission to selectively engage the output shaft of the continuously variable transmission or the output shaft of the unit output shaft with the output element of In a continuously variable transmission having an infinite transmission ratio capable of engaging and disengaging the power circulation mode clutch and the direct coupling mode clutch, the direct coupling mode clutch being fixed to Infinite transmission ratio The maximum forward transmission speed ratio of the continuously variable transmission is IvHi
Similarly, when the reverse side highest gear ratio is IvRev and the gear ratio width of the continuously variable transmission is λ, the gear ratio α represented by the number of teeth of the sun gear of the planetary gear mechanism / the number of teeth of the ring gear is α. Is given by An infinitely variable transmission with infinite transmission ratio.
変速機及び一定変速機と、 無段変速機の出力軸に連結したサンギヤ、一定変速機の
出力軸に連結したリングギヤ及びダブルピニオンで構成
されてユニット出力軸に連結したキャリアとからなる遊
星歯車機構と、 前記ユニット入力軸から遊星歯車機構のリングギヤへの
動力伝達経路の途中に介装された動力循環モードクラッ
チと、 前記無段変速機の出力軸からユニット出力軸の動力伝達
経路の途中に介装されて無段変速機の出力軸とユニット
出力軸を選択的に締結または遊星歯車機構の相互に歯合
する前記回転要素を選択的に固定する直結モードクラッ
チとを備えて、前記動力循環モードクラッチと直結モー
ドクラッチとを選択的に締結、解除可能な変速比無限大
無段変速機において、 変速比無限大無段変速機の前進側最ハイ変速比をＩｖHi
とし、同じく後退側最ハイ変速比をＩｖRevとするとと
もに、前記無段変速機の変速比幅をλとすると、 前記遊星歯車機構のサンギヤの歯数／リングギヤの歯数
で表されるギヤ比αは、 【数３】 に設定されたことを特徴とする変速比無限大無段変速
機。3. A continuously variable transmission and a constant transmission respectively connected to a unit input shaft, a sun gear connected to the output shaft of the continuously variable transmission, a ring gear connected to the output shaft of the constant transmission, and a double pinion. A planetary gear mechanism composed of a carrier connected to the unit output shaft, a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the ring gear of the planetary gear mechanism, and the continuously variable transmission. The output element of the continuously variable transmission to selectively engage the output shaft of the continuously variable transmission or the output shaft of the unit output shaft with the output element of In a continuously variable transmission having an infinite transmission ratio capable of engaging and disengaging the power circulation mode clutch and the direct coupling mode clutch, the direct coupling mode clutch being fixed to Infinite transmission ratio The maximum forward transmission speed ratio of the continuously variable transmission is IvHi
Similarly, when the reverse side highest gear ratio is IvRev and the gear ratio width of the continuously variable transmission is λ, the gear ratio α represented by the number of teeth of the sun gear of the planetary gear mechanism / the number of teeth of the ring gear is α. Is given by An infinitely variable transmission with infinite transmission ratio.
変速機及び一定変速機と、 ダブルピニオンで構成されて無段変速機の出力軸に連結
したキャリア、一定変速機の出力軸に連結したリングギ
ヤ及びユニット出力軸に連結したサンギヤとからなる遊
星歯車機構と、 前記ユニット入力軸から遊星歯車機構のリングギヤへの
動力伝達経路の途中に介装された動力循環モードクラッ
チと、 前記無段変速機の出力軸からユニット出力軸の動力伝達
経路の途中に介装されて無段変速機の出力軸とユニット
出力軸を選択的に締結または遊星歯車機構の相互に歯合
する前記回転要素を選択的に固定する直結モードクラッ
チとを備えて、前記動力循環モードクラッチと直結モー
ドクラッチとを選択的に締結、解除可能な変速比無限大
無段変速機において、 変速比無限大無段変速機の前進側最ハイ変速比をＩｖHi
とし、同じく後退側最ハイ変速比をＩｖRevとするとと
もに、前記無段変速機の変速比幅をλとすると、 前記遊星歯車機構のサンギヤの歯数／リングギヤの歯数
で表されるギヤ比αは、 【数４】 に設定されたことを特徴とする変速比無限大無段変速
機。4. A continuously variable transmission and a constant transmission which are respectively connected to a unit input shaft, a carrier which is composed of a double pinion and is connected to an output shaft of the continuously variable transmission, and a carrier which is connected to an output shaft of the constant transmission. A planetary gear mechanism composed of a ring gear and a sun gear connected to the unit output shaft; a power circulation mode clutch interposed in the power transmission path from the unit input shaft to the ring gear of the planetary gear mechanism; and the continuously variable transmission. The output element of the continuously variable transmission to selectively engage the output shaft of the continuously variable transmission or the output shaft of the unit output shaft with the output element of In a continuously variable transmission having an infinite transmission ratio capable of engaging and disengaging the power circulation mode clutch and the direct coupling mode clutch, the direct coupling mode clutch being fixed to Infinite transmission ratio The maximum forward transmission speed ratio of the continuously variable transmission is IvHi
Similarly, when the reverse side highest gear ratio is IvRev and the gear ratio width of the continuously variable transmission is λ, the gear ratio α represented by the number of teeth of the sun gear of the planetary gear mechanism / the number of teeth of the ring gear is α. Is given by An infinitely variable transmission with infinite transmission ratio.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30317897A JP3468060B2 (en) | 1997-11-05 | 1997-11-05 | Transmission ratio infinitely variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30317897A JP3468060B2 (en) | 1997-11-05 | 1997-11-05 | Transmission ratio infinitely variable transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11141646A JPH11141646A (en) | 1999-05-25 |
| JP3468060B2 true JP3468060B2 (en) | 2003-11-17 |
Family
ID=17917830
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30317897A Expired - Fee Related JP3468060B2 (en) | 1997-11-05 | 1997-11-05 | Transmission ratio infinitely variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3468060B2 (en) |
-
1997
- 1997-11-05 JP JP30317897A patent/JP3468060B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH11141646A (en) | 1999-05-25 |
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