JP4037874B2 - Power split type continuously variable transmission - Google Patents

Power split type continuously variable transmission Download PDF

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JP4037874B2
JP4037874B2 JP2005043753A JP2005043753A JP4037874B2 JP 4037874 B2 JP4037874 B2 JP 4037874B2 JP 2005043753 A JP2005043753 A JP 2005043753A JP 2005043753 A JP2005043753 A JP 2005043753A JP 4037874 B2 JP4037874 B2 JP 4037874B2
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power
transmission mechanism
shaft
gear
power transmission
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JP2006226483A (en
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泰夫 住
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JATCO Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/086—CVT using two coaxial friction members cooperating with at least one intermediate friction member

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Description

この発明は、パワースプリット型無段変速装置、特に自動車に搭載されるパワースプリット型無段変速装置に関する。   The present invention relates to a power split type continuously variable transmission, and more particularly to a power split type continuously variable transmission mounted in an automobile.

自動車用変速機として用いるパワースプリット型無段変速装置は、特許文献１に開示されるようにエンジン等の駆動源に接続する入力軸と、この入力軸に繋がる入力ディスクと出力ディスクとを備え、両ディスク間にパワーローラが傾転自在に配接されたダブルキャビティ式トロイダル型バリエータと、出力ディスクに接続してバリエータの出力を２自由度を有する遊星歯車機構にカウンタ軸等を用いて伝達する動力伝達機構と、入力軸よりバイパスして直接２自由度を有する遊星歯車機構に伝達するバイパス軸と、遊星歯車機構と接続して動力を駆動輪等に伝達する出力軸と、を備えている。   A power split type continuously variable transmission used as an automobile transmission includes an input shaft connected to a drive source such as an engine as disclosed in Patent Document 1, an input disk connected to the input shaft, and an output disk. A double-cavity toroidal variator, in which a power roller is tiltably disposed between both disks, and an output disk connected to the output disk to transmit the output of the variator to a planetary gear mechanism having two degrees of freedom using a counter shaft or the like. A power transmission mechanism, a bypass shaft that bypasses the input shaft and directly transmits to a planetary gear mechanism having two degrees of freedom, and an output shaft that is connected to the planetary gear mechanism and transmits power to a drive wheel or the like. .

ここで、２自由度を有する遊星歯車機構のリングギヤを低速用クラッチにより出力軸に固定することにより、カウンタ軸が出力軸に直接動力を伝達する第１モード(前進低速モード)を得ている。   Here, by fixing the ring gear of the planetary gear mechanism having two degrees of freedom to the output shaft by the low speed clutch, the first mode (forward low speed mode) in which the counter shaft directly transmits power to the output shaft is obtained.

また、この第１モードにおいて、低速用クラッチを解除して、伝達軸とバイパス軸とを固定する高速用クラッチを係合することにより、遊星歯車機構からバリエータに動力循環した動力が入力動力と合算されてバイパス軸を経て遊星歯車機構に流入し、出力軸には流入する動力と動力循環する動力の差が出力動力として出力される第２モード（前進高速モード）を得ている。   Further, in this first mode, by releasing the low speed clutch and engaging the high speed clutch for fixing the transmission shaft and the bypass shaft, the power circulated from the planetary gear mechanism to the variator is combined with the input power. Thus, the second mode (forward high speed mode) is obtained in which the difference between the power that flows in and the power that circulates through the power is output as output power to the output shaft via the bypass shaft.

上記第２モードにおいては、特許文献１の図２に示すごとく、高速走行時にバリエータに入力される動力を小さくして、このバリエータの構成部品の耐久性向上が図れると共に、伝達効率の向上が図れる。   In the second mode, as shown in FIG. 2 of Patent Document 1, the power input to the variator during high-speed running can be reduced to improve the durability of the components of the variator and improve the transmission efficiency. .

しかしながら、特許文献１で示したパワースプリット型無段変速装置では、第２モードにおいてはバリエータを通過する動力は入力した動力に比し小さくなるが、第１モードにおいてはバリエータを通過する動力は入力した動力と等しくなる。   However, in the power split type continuously variable transmission shown in Patent Document 1, the power passing through the variator is smaller than the input power in the second mode, but the power passing through the variator is input in the first mode. It becomes equal to the motive power.

このため、非特許文献１に記載のトロイダル型バリエータを用いたパワースプリット型変速装置では、全てのモードにおいて動力分配が行われる構成を提案している（図２参照のこと）。この変速装置によれば、全てのモードにおいて伝達効率の向上が図れるだけでなく、バリエータの小型化が達成できる。   For this reason, the power split type transmission using the toroidal variator described in Non-Patent Document 1 proposes a configuration in which power distribution is performed in all modes (see FIG. 2). According to this transmission, not only can the transmission efficiency be improved in all modes, but also the size of the variator can be reduced.

この非特許文献１の構成について説明する。非特許文献１の無段変速装置は、ダブルキャビティ式トロイダル型バリエータ（以下、単にバリエータという）３３と、動力源としてのエンジンＥの動力をバリエータ３３に選択的に伝達する発進装置３２と、複数の歯車からなる第１から第４動力伝達機構３４〜３７と、発進装置２の動力をバリエータ３３と第２動力伝達機構３５とに分配する遊星歯車機構３８と、第３動力伝達機構３６と第４動力機構３７に備えられ、歯車の回転を拘束するクラッチ群３９、４１、およびバリエータ３３と出力軸４２との接続を制御するクラッチ４０、バリエータ３３に平行配置された第１カウンタ軸４３、第２カウンタ軸４４とから構成される。   The configuration of Non-Patent Document 1 will be described. The continuously variable transmission of Non-Patent Document 1 includes a double cavity type toroidal variator (hereinafter simply referred to as a variator) 33, a starting device 32 that selectively transmits the power of the engine E as a power source to the variator 33, First to fourth power transmission mechanisms 34 to 37 composed of a plurality of gears, a planetary gear mechanism 38 that distributes the power of the starting device 2 to the variator 33 and the second power transmission mechanism 35, a third power transmission mechanism 36, and a third power transmission mechanism 36. A clutch group 39, 41 for restraining the rotation of gears, a clutch 40 for controlling the connection between the variator 33 and the output shaft 42, a first counter shaft 43 arranged in parallel to the variator 33, a first counter shaft 43; 2 counter shafts 44.

以上のように構成された無段変速装置は、クラッチ３９〜４１の締結・解放状態の組み合わせにより、前進低速モード、前進高速モードおよび後進モードの３つのモードを得ることができる。   The continuously variable transmission configured as described above can obtain three modes of the forward low-speed mode, the forward high-speed mode, and the reverse mode by combining the engagement and release states of the clutches 39 to 41.

前進低速モードでは、クラッチ３９が締結され、遊星歯車機構３８から第２動力伝達機構３５に分配された動力は、バリエータ３３と並設された第１カウンタ軸４３に伝達される。一方、遊星歯車機構３８からバリエータ３３に直接分配された動力は、第１動力伝達機構３４から第１カウンタ軸３４に伝達され、第２動力伝達機構３５から伝達された動力と合力され、第３動力伝達機構３６に伝達される。第３動力伝達機構３６に伝達された動力はクラッチ３９を経由して出力軸４２に伝達される。   In the forward low speed mode, the clutch 39 is engaged, and the power distributed from the planetary gear mechanism 38 to the second power transmission mechanism 35 is transmitted to the first counter shaft 43 provided in parallel with the variator 33. On the other hand, the power directly distributed from the planetary gear mechanism 38 to the variator 33 is transmitted from the first power transmission mechanism 34 to the first counter shaft 34, and combined with the power transmitted from the second power transmission mechanism 35. It is transmitted to the power transmission mechanism 36. The power transmitted to the third power transmission mechanism 36 is transmitted to the output shaft 42 via the clutch 39.

前進高速モードではクラッチ４０が締結され、遊星歯車機構３８から第２動力伝達機構３５に分配された動力は、バリエータ３３と並設された第１カウンタ軸４３を介して第１動力伝達機構３４に伝達され、バリエータ３３に伝達される。一方、遊星歯車機構３８からバリエータ３３に直接分配された動力は、第１動力伝達機構３４から伝達された動力と合力され、クラッチ４０を介して出力軸４２に伝達される。   In the forward high speed mode, the clutch 40 is engaged, and the power distributed from the planetary gear mechanism 38 to the second power transmission mechanism 35 is transmitted to the first power transmission mechanism 34 via the first counter shaft 43 provided in parallel with the variator 33. Is transmitted to the variator 33. On the other hand, the power directly distributed from the planetary gear mechanism 38 to the variator 33 is combined with the power transmitted from the first power transmission mechanism 34 and transmitted to the output shaft 42 via the clutch 40.

後進モードではクラッチ４１が締結され、第４動力伝達機構３７は、第１カウンタ軸４３と並設された第２カウンタ軸４４を介して第１動力伝達機構３４のカウンタギア４５と接続する。遊星歯車機構３８から第２動力伝達機構３５に分配された動力は、バリエータ３３と並設された第１カウンタ軸４３に伝達され、第１動力伝達機構３４のカウンタギア４５に伝達される。一方、遊星歯車機構３８からバリエータ３３に直接分配された動力は、第１動力伝達機構３４からカウンタギア４５に伝達され、第２動力伝達機構３５から伝達された動力と合力される。そしてカウンタギア４５に伝達された動力はクラッチ４１を経由して出力軸４１に伝達される。
特開平１１−６３１４７号公報 ＶＤＩ Ｂｅｒｉｃｈｔｅ Ｎｒ．１５６５，２０００，Ｐ．２５６のＢｉｌｄ２０ In the reverse mode, the clutch 41 is engaged, and the fourth power transmission mechanism 37 is connected to the counter gear 45 of the first power transmission mechanism 34 via the second counter shaft 44 provided in parallel with the first counter shaft 43. The power distributed from the planetary gear mechanism 38 to the second power transmission mechanism 35 is transmitted to the first counter shaft 43 provided in parallel with the variator 33 and is transmitted to the counter gear 45 of the first power transmission mechanism 34. On the other hand, the power directly distributed from the planetary gear mechanism 38 to the variator 33 is transmitted from the first power transmission mechanism 34 to the counter gear 45 and combined with the power transmitted from the second power transmission mechanism 35. The power transmitted to the counter gear 45 is transmitted to the output shaft 41 via the clutch 41.
Japanese Patent Laid-Open No. 11-63147 VDI Berichte Nr. 1565, 2000, p. 256 Build20

しかしながら、非特許文献１に記載の構成では、バリエータ３３の軸に平行なカウンタ軸が２本必要であり（第１カウンタ軸４３、第２カウンタ軸４４）、変速装置全体の寸法が大きくなる。このため、車両に変速装置を搭載する場合にレイアウト性が難しくなり、例えば、最低地上高が確保出来ないと言う欠点がある。さらには装置重量の増加やコストアップするという問題もある。   However, the configuration described in Non-Patent Document 1 requires two counter shafts parallel to the axis of the variator 33 (the first counter shaft 43 and the second counter shaft 44), which increases the overall size of the transmission. For this reason, when installing a transmission in a vehicle, layout property becomes difficult, for example, there exists a fault that the minimum ground clearance cannot be ensured. Furthermore, there is a problem that the weight of the apparatus is increased and the cost is increased.

この発明の目的は、装置全体を小型化出来、その結果、軽量で低コスト化が図れるパワースプリット型無段変速装置を提供することにある。   An object of the present invention is to provide a power split type continuously variable transmission that can reduce the size of the entire apparatus and, as a result, can be reduced in weight and cost.

本発明のパワースプリット型無段変速装置は、動力源により回転駆動される入力軸と、この入力軸が伝達する動力に基づいて動力を出力する出力軸と、第１回転要素、第２回転要素及び第３回転要素とから構成され、前記第１回転要素が前記入力軸に連結し、前記第１回転要素に入力された動力を前記第２回転要素及び第３回転要素へ分配する差動歯車機構と、この差動歯車機構の前記第２回転要素に連結するバリエータ入力軸と、一端が前記バリエータ入力軸に連結し、他端が前記出力軸に第１係合手段により選択的に連結するバイパス軸と、前記バリエータ入力軸に連結する無段変速機構と、前記バリエータ入力軸に並設されたカウンタ軸と、前記無段変速機構の出力を前記カウンタ軸に伝達する第１動力伝達機構と、前記差動歯車機構の前記第３回転要素の出力を前記カウンタ軸に伝達する第２動力伝達機構と、前記カウンタ軸及び前記出力軸に連結され、前記第１動力伝達機構の出力と前記第２動力伝達機構の出力とを合わせた出力を第２係合手段により前記カウンタ軸から前記出力軸に選択的に伝達する第３動力伝達機構と、前記カウンタ軸及び前記出力軸に連結され、前記第１動力伝達機構の出力と前記第２動力伝達機構の出力とを合わせた出力を、前記第３動力伝達機構が前記出力軸に伝達する回転方向と逆の回転方向で、第３係合手段により前記カウンタ軸から前記出力軸に選択的に伝達する第４動力伝達機構と、前記第１動力伝達機構及び前記第２動力伝達機構から伝達される動力を前記第３動力伝達機構で合わせて、前記出力軸に伝達する前進低速モードと、前記第１動力伝達機構及び第２動力伝達機構から伝達される動力を前記第４動力伝達機構で合わせて、前記出力軸に伝達する後進モードと、前記第２回転要素から前記バリエータ入力軸を経由した動力と、前記第３回転要素から前記第２動力伝達機構、前記第１動力伝達機構、前記無段変速機構を経由した動力とを前記バイパス軸で合わせて、前記第１係合手段を介して前記出力軸に伝達する前進高速モードとを前記第１から第３係合手段の係合状態を制御して切り換えるモード制御装置と、を備えた。   The power split type continuously variable transmission of the present invention includes an input shaft that is rotationally driven by a power source, an output shaft that outputs power based on the power transmitted by the input shaft, a first rotating element, and a second rotating element And a third rotating element, wherein the first rotating element is coupled to the input shaft, and the differential gear that distributes the power input to the first rotating element to the second rotating element and the third rotating element A mechanism, a variator input shaft connected to the second rotating element of the differential gear mechanism, one end connected to the variator input shaft, and the other end selectively connected to the output shaft by a first engagement means. A bypass shaft, a continuously variable transmission mechanism connected to the variator input shaft, a counter shaft provided in parallel with the variator input shaft, and a first power transmission mechanism for transmitting the output of the continuously variable transmission mechanism to the counter shaft; The differential gear mechanism A second power transmission mechanism for transmitting the output of the third rotating element to the counter shaft; and an output of the first power transmission mechanism and an output of the second power transmission mechanism coupled to the counter shaft and the output shaft; And a third power transmission mechanism for selectively transmitting the output from the counter shaft to the output shaft by the second engaging means, and an output of the first power transmission mechanism coupled to the counter shaft and the output shaft. And the output of the second power transmission mechanism in a rotational direction opposite to the rotational direction transmitted by the third power transmission mechanism to the output shaft, the output from the counter shaft by the third engagement means A fourth power transmission mechanism that selectively transmits to the shaft, and a forward power that is transmitted from the first power transmission mechanism and the second power transmission mechanism to the output shaft after being combined by the third power transmission mechanism Slow mode, A reverse mode in which the power transmitted from the first power transmission mechanism and the second power transmission mechanism is combined by the fourth power transmission mechanism and transmitted to the output shaft, and from the second rotation element via the variator input shaft And the power from the third rotating element through the second power transmission mechanism, the first power transmission mechanism, and the continuously variable transmission mechanism are combined by the bypass shaft, and the first engagement means is used. And a mode control device for switching the forward high speed mode transmitted to the output shaft by controlling the engagement state of the first to third engagement means.

この発明によれば、非特許文献の構成に対してバリエータと並設する１本のカウンタ軸のみを設ければよく、装置全体の大型やコストアップを防止するという効果がある。   According to the present invention, it is sufficient to provide only one counter shaft arranged in parallel with the variator with respect to the configuration of the non-patent document, and there is an effect of preventing an increase in size and cost of the entire apparatus.

図１に本発明のパワースプリット型無段変速装置の構成図を示す。本発明のパワースプリット型無段変速装置は、ダブルキャビティ式トロイダル型バリエータ（以下、単にバリエータという）２２と、動力源としてのエンジンＥに接続する駆動伝達軸１の動力をバリエータ２２に選択的に伝達する発進装置２と、複数の歯車からなる第１から第４動力伝達機構９〜１１、２１と、発進装置２の動力をバリエータ２２と第２動力伝達機構９とに伝達する遊星歯車機構１７と、第３動力伝達機構１１と第４動力機構２１に備えられ、歯車の回転を拘束するクラッチ群１４、１６、バリエータ２２と出力軸１９との接続を制御するクラッチ１５、およびクラッチ群１４〜１６を制御する制御装置２３から構成される。   FIG. 1 is a configuration diagram of a power split type continuously variable transmission according to the present invention. A power split type continuously variable transmission according to the present invention selectively transmits power of a double cavity toroidal variator (hereinafter simply referred to as a variator) 22 and a drive transmission shaft 1 connected to an engine E as a power source to the variator 22. The starting device 2 for transmitting, the first to fourth power transmission mechanisms 9 to 11 and 21 composed of a plurality of gears, and the planetary gear mechanism 17 for transmitting the power of the starting device 2 to the variator 22 and the second power transmitting mechanism 9. Clutch groups 14 and 16 that are provided in the third power transmission mechanism 11 and the fourth power mechanism 21 and restrict the rotation of the gears, the clutch 15 that controls the connection between the variator 22 and the output shaft 19, and the clutch groups 14 to 14. 16 is constituted by a control device 23 for controlling 16.

エンジンＥに連結された動力伝達軸１は、トルクコンバータ等の発進装置２、入力軸（タービン軸）３を介して遊星歯車機構（差動歯車機構）１７のリングギヤ（第１回転要素）１７ｅに連結される。このリングギヤ１７ｅに伝達された動力の一部が、遊星歯車機構１７のサンギヤ（第２回転要素）１７ａに伝達され、残りの動力がキャリヤ（第３回転要素）１７ｄに伝達される。すなわち、遊星歯車機構１７は動力分配機構として作用する。   The power transmission shaft 1 connected to the engine E is connected to a ring gear (first rotating element) 17e of a planetary gear mechanism (differential gear mechanism) 17 via a starting device 2 such as a torque converter and an input shaft (turbine shaft) 3. Connected. Part of the power transmitted to the ring gear 17e is transmitted to the sun gear (second rotating element) 17a of the planetary gear mechanism 17, and the remaining power is transmitted to the carrier (third rotating element) 17d. That is, the planetary gear mechanism 17 acts as a power distribution mechanism.

サンギヤ１７ａに伝達された動力は、入力軸３と同軸上に配置したバリエータ入力軸４を経て機械式ローディング機構１２に伝達される。この機械式ローディング機構１２を介してバリエータ２２の入力ディスク５に動力が伝達されるようになっている。ここで、機械式ローディング機構１２は、バリエータ２２に対して遊星歯車機構１２と相反する側に設置されている
バリエータ２２には、互いに対向する一対の入力ディスク５が設けられている。これら入力ディスク５は、入力ディスク連結軸６にて連結し、機械式ローディング機構１２の作用によりバリエータ入力軸４とともに回転する。この一対の入力ディスク５間にはバリエータ入力軸４及び入力ディスク連結軸６に対し回転自在の一対の出力ディスク７がこれら軸と同軸的に配置され互いに同期して回転する。 The power transmitted to the sun gear 17a is transmitted to the mechanical loading mechanism 12 via the variator input shaft 4 arranged coaxially with the input shaft 3. Power is transmitted to the input disk 5 of the variator 22 through the mechanical loading mechanism 12. Here, the mechanical loading mechanism 12 is installed on the side opposite to the planetary gear mechanism 12 with respect to the variator 22. The variator 22 is provided with a pair of input disks 5 facing each other. These input disks 5 are connected by an input disk connecting shaft 6 and rotated together with the variator input shaft 4 by the action of a mechanical loading mechanism 12. Between the pair of input disks 5, a pair of output disks 7 rotatable with respect to the variator input shaft 4 and the input disk connecting shaft 6 are arranged coaxially with these shafts and rotate in synchronization with each other.

入力ディスク５と出力ディスク７との間には傾転自在に転接された複数のパワーローラ８が設けられる。機械式ローディング機構１２により入力ディスク５が出力ディスク７にパワーローラ８を介して押圧されることで、動力は、パワーローラ８を介して入力ディスク５から出力ディスク７に伝達される。   Between the input disk 5 and the output disk 7, there are provided a plurality of power rollers 8 that are in rolling contact with each other. The mechanical loading mechanism 12 presses the input disk 5 against the output disk 7 via the power roller 8, so that power is transmitted from the input disk 5 to the output disk 7 via the power roller 8.

出力ディスク７は、第１動力伝達機構１０の出力ディスク７と同軸に設置された第１ギヤ１０ａと一体的に結合する。ここで、第１動力伝達機構１０は、第１ギヤ１０ａ、第１ギヤ１０ａと噛合する第２ギヤ１０ｂ、第２ギア１０ｂと噛合してカウンタ軸１８に固定される第３ギヤ１０ｃから構成される。カウンタ軸１８はバリエータ入力軸４と並行に設置される。したがって、出力ディスク７の動力は、第１ギヤ１０ａから、第２ギヤ１０ｂ、第３ギヤ１０ｃを介してカウンタ軸１８に伝達される。   The output disk 7 is integrally coupled to a first gear 10 a that is installed coaxially with the output disk 7 of the first power transmission mechanism 10. Here, the first power transmission mechanism 10 includes a first gear 10 a, a second gear 10 b that meshes with the first gear 10 a, and a third gear 10 c that meshes with the second gear 10 b and is fixed to the counter shaft 18. The The counter shaft 18 is installed in parallel with the variator input shaft 4. Therefore, the power of the output disk 7 is transmitted from the first gear 10a to the counter shaft 18 via the second gear 10b and the third gear 10c.

一方、遊星歯車機構１７のキャリヤ１７ｄは、第２動力伝達機構９の第４ギヤ９ａに結合する。ここで、第２動力伝達機構９は、第４ギヤ９ａ、カウンタ軸１８に固定された第５ギヤ９ｂで構成される。したがって、前記キャリヤ１７ｄの動力は、第２動力伝達機構９を介して、バリエータ入力軸４に並行に配置されたカウンタ軸１８に伝達される。   On the other hand, the carrier 17 d of the planetary gear mechanism 17 is coupled to the fourth gear 9 a of the second power transmission mechanism 9. Here, the second power transmission mechanism 9 includes a fourth gear 9 a and a fifth gear 9 b fixed to the counter shaft 18. Therefore, the power of the carrier 17d is transmitted to the counter shaft 18 disposed in parallel with the variator input shaft 4 via the second power transmission mechanism 9.

さらに、カウンタ軸１８は、前述のように第１動力伝達機構１０の第３ギヤ１０ｃにも結合しているため、第１動力伝達機構１０を経由した動力と第２動力伝達機構９を経由した動力とがカウンタ軸１８にて合わされる。さらに、このカウンタ軸１８の一端部には第３、第４動力伝達機構１１、２１が配置されている。 Further, since the counter shaft 18 is also coupled to the third gear 10c of the first power transmission mechanism 10 as described above, the power passing through the first power transmission mechanism 10 and the second power transmission mechanism 9 are passed through. The power is combined with the counter shaft 18. Further, third and fourth power transmission mechanisms 11 and 21 are arranged at one end of the counter shaft 18.

第３動力伝達機構１１は、第６ギヤ１１ａ、第６ギヤ１１ａと噛み合う第７ギヤ１１ｂを備える（図面上は第６ギヤ１１ａと第７ギヤ１１ｂは噛み合っていないが実際には噛み合う）。さらに、第６ギヤ１１ａはパワースプリット型無段変速装置の出力軸１９に結合するとともに、選択的に“締結”または“解放”を行える前進高速クラッチ（第１係合手段）１５を介して、機械式ローディング機構１２に接続するバイパス軸１３と選択的に連結する。一方、第７ギヤ１１ｂは選択的に“締結”または“解放”を行える前進低速クラッチ（第２係合手段）１４を介してカウンタ軸１８に連結している。   The third power transmission mechanism 11 includes a sixth gear 11a and a seventh gear 11b that meshes with the sixth gear 11a (in the drawing, the sixth gear 11a and the seventh gear 11b are not meshed but actually mesh). Further, the sixth gear 11a is coupled to the output shaft 19 of the power split type continuously variable transmission, and via a forward high-speed clutch (first engagement means) 15 that can be selectively "engaged" or "released", It is selectively connected to a bypass shaft 13 connected to the mechanical loading mechanism 12. On the other hand, the seventh gear 11b is connected to the counter shaft 18 via a forward low-speed clutch (second engagement means) 14 that can selectively "engage" or "release".

次に、第４動力伝達機構２１は、カウンタ軸１８に固定された第９ギヤ２１ａ、第９ギヤ２１ａと噛み合う第１０ギヤ２１ｂ、第６ギヤ１１ａと噛み合う第８ギヤ１１ｃとを備える。ここで、第１０ギヤ２１ｂはカウンタ軸１８と並設された第２カウンタ軸２１ｃに固定される。第２カウンタ軸２１ｃに同軸に設置された第８ギヤ１１ｃは選択的に“締結”または“解放”を行える後進クラッチ（第３係合手段）１６を介して選択的に第２カウンタ軸２１ｃに連結する。   Next, the fourth power transmission mechanism 21 includes a ninth gear 21a fixed to the counter shaft 18, a tenth gear 21b that meshes with the ninth gear 21a, and an eighth gear 11c that meshes with the sixth gear 11a. Here, the tenth gear 21 b is fixed to a second counter shaft 21 c provided in parallel with the counter shaft 18. The eighth gear 11c installed coaxially with the second countershaft 21c is selectively connected to the second countershaft 21c via a reverse clutch (third engaging means) 16 that can selectively "engage" or "release". Link.

パワースプリット型無段変速装置の出力軸１９は、前進高速クラッチ１５及びバイパス軸１３を介してバリエータ入力軸４に連結している。   The output shaft 19 of the power split type continuously variable transmission is connected to the variator input shaft 4 via the forward high speed clutch 15 and the bypass shaft 13.

このパワースプリット型無段変速装置は、例えば、入力トルクやエンジン負荷と、車速と、入力軸（トルクコンバータのタービン軸）回転数などから、表１に示すように、前進低速モード、前進高速モード及び後進モードを設定して、前進低速クラッチ１４、前進高速クラッチ１５、後進クラッチ１６の締結解放を制御する。これらクラッチ１４〜１６の締結解放制御（係合制御）および、バリエータ２２の変速比を制御する制御装置２３が備えられる。なお表中の○は締結（係合）、×は解放（非係合）を表している。   As shown in Table 1, the power split type continuously variable transmission includes, for example, an input low-speed mode, a high-speed forward mode and a high-speed forward mode, as shown in Table 1. In addition, the reverse mode is set to control the engagement and release of the forward low speed clutch 14, the forward high speed clutch 15, and the reverse clutch 16. A control device 23 for controlling the engagement / release control (engagement control) of the clutches 14 to 16 and the gear ratio of the variator 22 is provided. In the table, ◯ represents fastening (engaged) and x represents release (non-engaged).

Figure 0004037874
次に各動力伝達機構の減速比について説明する。
Figure 0004037874
 Next, the reduction ratio of each power transmission mechanism will be described.

ここで、バリエータ２２の最大増幅位置（最Ｈｉｇｈ）における変速比Ｖhighと、第１動力伝達機構１０の減速比Ｒ１と、第３動力伝達機構１１の第７ギヤ１１ｂと第６ギヤ１１ａとの間の減速比Ｒ３ｆとの関係を、
Ｖhigh≒Ｒ１・Ｒ３ｆ （１）
に設定している。 Here, the speed ratio Vhigh at the maximum amplification position (highest) of the variator 22, the reduction ratio R1 of the first power transmission mechanism 10, and the seventh gear 11b and the sixth gear 11a of the third power transmission mechanism 11 The relationship with the reduction ratio R3f of
Vhigh ≒ R1 ・ R3f (1)
Is set.

第１動力伝達機構１０の減速比Ｒ１は、以下の式で与えられる。   The reduction ratio R1 of the first power transmission mechanism 10 is given by the following equation.

Ｒ１＝Ｚ１０ａ／Ｚ１０ｂ
ただし、Ｚ１０ａ：第１動力伝達機構１０の第１ギヤ１０ａの歯数
Ｚ１０ｂ：第１動力伝達機構１０の第２ギヤ１０ｂの歯数
第３動力伝達機構１１の第６ギヤ１１ａと第７ギヤ１１ｂとの間の減速比Ｒ３ｆは、以下の式で与えられる。 R1 = Z10a / Z10b
However, Z10a: The number of teeth of the first gear 10a of the first power transmission mechanism 10
Z10b: Number of teeth of the second gear 10b of the first power transmission mechanism 10 A reduction ratio R3f between the sixth gear 11a and the seventh gear 11b of the third power transmission mechanism 11 is given by the following equation.

Ｒ３ｆ＝Ｚ１１ｂ／Ｚ１１ａ
ただし、Ｚ１１ａ：第３動力伝達機構１１の第６ギヤ１１ａの歯数
Ｚ１１ｂ：第３動力伝達機構１１の第７ギヤ１１ｂの歯数
次に、本発明の無段変速装置の作用を説明する。 R3f = Z11b / Z11a
However, Z11a: Number of teeth of the sixth gear 11a of the third power transmission mechanism 11
Z11b: Number of teeth of the seventh gear 11b of the third power transmission mechanism 11 Next, the operation of the continuously variable transmission of the present invention will be described.

今、入力軸３が停止しており、かつバリエータ２２が最大減速位置（最Ｌｏｗ）にあると共に、前進高速クラッチ１５と後進クラッチ１８が解放状態に、前進低速クラッチ１４が締結状態にあるとする。この状態から発進装置２の作用により入力軸３を所定方向に回転開始させると、この入力軸３の回転に伴って、遊星歯車機構１７のリングギヤ１７ｅが入力軸３と同方向に同一回転速度で回転する。そのとき、リングギヤ１７ｅの動力は遊星歯車機構１７のサンギヤ１７ａおよびキャリヤ１７ｄの各々に分配し伝達される。サンギヤ１７ａに分配された動力は、バリエータ入力軸４、バリエータ２２、すなわち、機械式ローディング機構１２、入力ディスク５、パワーローラ８、出力ディスク７を経て、第１動力伝達機構１０、カウンタ軸１８に伝達される。   Now, it is assumed that the input shaft 3 is stopped, the variator 22 is at the maximum deceleration position (lowest), the forward high-speed clutch 15 and the reverse clutch 18 are in the released state, and the forward low-speed clutch 14 is in the engaged state. . When the input shaft 3 starts to rotate in a predetermined direction by the action of the starting device 2 from this state, the ring gear 17e of the planetary gear mechanism 17 is rotated at the same rotational speed in the same direction as the input shaft 3 as the input shaft 3 rotates. Rotate. At that time, the power of the ring gear 17e is distributed and transmitted to each of the sun gear 17a and the carrier 17d of the planetary gear mechanism 17. The power distributed to the sun gear 17 a passes through the variator input shaft 4 and the variator 22, that is, the mechanical loading mechanism 12, the input disk 5, the power roller 8, and the output disk 7, and then to the first power transmission mechanism 10 and the counter shaft 18. Communicated.

一方、キャリヤ１７ｄに分配された動力は第２動力伝達機構９を経て、カウンタ軸１８に伝達される。カウンタ軸１８にて合わされた動力は、第３動力伝達機構１１を経て、出力軸１９に所定方向の回転で、かつ動力伝達軸１よりも低速回転となるように伝達される。これが前進低速モードとなる。   On the other hand, the power distributed to the carrier 17d is transmitted to the counter shaft 18 via the second power transmission mechanism 9. The power combined by the counter shaft 18 is transmitted to the output shaft 19 through the third power transmission mechanism 11 so as to rotate in a predetermined direction and at a lower speed than the power transmission shaft 1. This is the forward low speed mode.

そして、前進低速モードを維持しながらバリエータ２２を増速側に変速させると、出力軸１９の回転速度が増加し、パワースプリット型無段変速機の速度比が増速側に変化する。   When the variator 22 is shifted to the speed increasing side while maintaining the forward low speed mode, the rotational speed of the output shaft 19 increases, and the speed ratio of the power split type continuously variable transmission changes to the speed increasing side.

次に、前進高速クラッチ１５を締結し、前進低速クラッチ１４と後進クラッチ１６を解放する。この場合には、バリエータ２２を通過する動力の伝達方向が前進低速モードと逆になる。すなわち、前進低速モードと同じく、リングギヤ１７ｅの動力は、遊星歯車機構１７のサンギヤ１７ａおよびキャリヤ１７ｄの各々に分配されて伝達される。ここで、キャリヤ１７ｄに分配された動力は、第２動力伝達機構９、カウンタ軸１８、バリエータ２２、すなわち、出力ディスク７、パワーローラ８、入カディスク５、機械式ローディング機構１２を経て、バイパス軸１３に伝達される。一方、サンギヤ１７ａに分配された動力はバリエータ入力軸４を経てバイパス軸１３に伝達される。バイパス軸１３にて合わされた動力は、前進高速クラッチ１５を経て出力軸１９に伝達される。これが前進高速モードである。   Next, the forward high speed clutch 15 is engaged, and the forward low speed clutch 14 and the reverse clutch 16 are released. In this case, the transmission direction of the power passing through the variator 22 is opposite to that in the forward low speed mode. That is, as in the forward low speed mode, the power of the ring gear 17e is distributed and transmitted to each of the sun gear 17a and the carrier 17d of the planetary gear mechanism 17. Here, the power distributed to the carrier 17d is bypassed through the second power transmission mechanism 9, the counter shaft 18, and the variator 22, that is, the output disk 7, the power roller 8, the input disk 5, and the mechanical loading mechanism 12. It is transmitted to the shaft 13. On the other hand, the power distributed to the sun gear 17 a is transmitted to the bypass shaft 13 through the variator input shaft 4. The power combined in the bypass shaft 13 is transmitted to the output shaft 19 via the forward high speed clutch 15. This is the forward high speed mode.

次に、自動車を後退させるべく、出力軸１９を逆回転させる際には、前進低速クラッチ１４と前進高速クラッチ１５を解放し、後進クラッチ１６を締結する。その結果、遊星歯車機構１７で分配した動力は、前進低速モードと同様に、カウンタ軸１８で合わされる。この動力が第４動力伝達機構２１により、後進クラッチ１６を経て、出力軸１９に伝達される後進モードが得られる。   Next, in order to reversely rotate the output shaft 19 in order to reverse the automobile, the forward low speed clutch 14 and the forward high speed clutch 15 are released, and the reverse clutch 16 is engaged. As a result, the power distributed by the planetary gear mechanism 17 is combined by the counter shaft 18 as in the forward low speed mode. A reverse mode in which this power is transmitted to the output shaft 19 via the reverse clutch 16 by the fourth power transmission mechanism 21 is obtained.

したがって本発明によれば、前記第１動力伝達機構１０と第４動力伝達機構２１との間に１本のカウンタ軸１８のみを配設すればよく、装置全体の小型化が図れ、重量やコストの低減に貢献できる。   Therefore, according to the present invention, only one countershaft 18 needs to be disposed between the first power transmission mechanism 10 and the fourth power transmission mechanism 21, and the entire apparatus can be reduced in size, weight and cost. Can contribute to the reduction of

なお、本実施の形態では、動力伝達機構としてギヤを使った例を示したが、動力を伝達できる機構であればよく、ギヤのかわりに、例えば、チェーンやベルトなどを使った機構でもよいことは言うまでもない。さらに、本実施の形態では、差動歯車機構としていわゆるダブルピニオン型遊星歯車を使った例を示したが、動力を分配できる機構であれば、シングルピニオン遊星歯車を使った機構でもよいことは言うまでもない。   In this embodiment, an example in which a gear is used as the power transmission mechanism has been described. However, any mechanism that can transmit power may be used. For example, a mechanism using a chain or a belt may be used instead of the gear. Needless to say. Furthermore, in the present embodiment, an example using a so-called double pinion type planetary gear as a differential gear mechanism has been shown, but it goes without saying that a mechanism using a single pinion planetary gear may be used as long as the mechanism can distribute power. Yes.

さらに、前記無段変速機構としてトロイダル型無段変速機を配設したため、バリエータ入力軸と出力軸を同軸に配設出来、エンジン前置き後輪駆動のいわゆるＦＲ車に適した形状が可能となる効果もある。   Further, since the toroidal type continuously variable transmission is disposed as the continuously variable transmission mechanism, the variator input shaft and the output shaft can be disposed coaxially, and a shape suitable for a so-called FR vehicle of engine front and rear wheel drive is possible. There is also.

また、本実施の形態では、バリエータ２２の機械式ローディング機構１２を、バリエータ２２に対して差動歯車機構１７と反対側に配設したため、バリエータ入力軸４より軸径の太いバイパス軸１３を入力ディスク連結軸６の中を貫通する必要が無いため、さらなる径方向の短縮が図れる。   In this embodiment, since the mechanical loading mechanism 12 of the variator 22 is disposed on the opposite side of the variator 22 from the differential gear mechanism 17, the bypass shaft 13 having a larger shaft diameter than the variator input shaft 4 is input. Since there is no need to penetrate through the disk connecting shaft 6, further radial reduction can be achieved.

なお、本実施の形態では、ローディング機構として機械式ローディング機構１２を使った例を示したが、各ディスク間に押力を発生できる機構であればよく、機械式ローディング機構１２のほかに、例えば、油圧などを使った機構でもよいことは言うまでもない。   In the present embodiment, an example in which the mechanical loading mechanism 12 is used as the loading mechanism has been described. However, any mechanism that can generate a pressing force between the disks may be used. In addition to the mechanical loading mechanism 12, for example, Needless to say, a mechanism using hydraulic pressure may be used.

また、本実施の形態では、第４動力伝達機構２１を、前記トロイダル型バリエータと前記第３動力伝達機構の間に配設したため、バイパス軸１３に径方向に近接して第９ギヤ２１ａと第１０ギヤ２１ｂを配設出来るため、第４動力伝達機構２１の小型化が図れる。   In the present embodiment, since the fourth power transmission mechanism 21 is disposed between the toroidal variator and the third power transmission mechanism, the ninth gear 21a and the ninth gear 21a are disposed close to the bypass shaft 13 in the radial direction. Since the 10 gear 21b can be disposed, the fourth power transmission mechanism 21 can be downsized.

この発明の実施形態におけるパワースプリット型無段変速装置の構成図。The block diagram of the power split type continuously variable transmission in embodiment of this invention. 従来技術のパワースプリット型無段変速装置の構成図。The block diagram of the power split type continuously variable transmission of a prior art.

符号の説明Explanation of symbols

１…動力伝達軸
２…発進装置
３…タービン軸（入力軸）
４…バリエータ入力軸
５…入力ディスク
６…入力ディスク連結軸
７…出力ディスク
８…パワーローラ
９…第２動力伝達機構
１０…第１動力伝達機構
１１…第３動力伝達機構
１２…機械式ローディング機構
１３…バイパス軸
１４…前進低速クラッチ
１５…前進高速クラッチ
１６…後進クラッチ
１７…遊星歯車機構
１７ａ…サンギヤ
１７ｂ…第１ピニオンギヤ
１７ｃ…第２ピニオンギヤ
１７ｄ…キャリヤ
１７ｅ…リングギヤ
１８…カウンタ軸
１９…出力軸
２１…第４動力伝達機構
２２…バリエータ
２３…制御装置
Ｅ…エンジン DESCRIPTION OF SYMBOLS 1 ... Power transmission shaft 2 ... Starting device 3 ... Turbine shaft (input shaft)
4 ... variator input shaft 5 ... input disc 6 ... input disc connecting shaft 7 ... output disc 8 ... power roller 9 ... second power transmission mechanism 10 ... first power transmission mechanism 11 ... third power transmission mechanism 12 ... mechanical loading mechanism DESCRIPTION OF SYMBOLS 13 ... Bypass shaft 14 ... Forward low speed clutch 15 ... Forward high speed clutch 16 ... Reverse clutch 17 ... Planetary gear mechanism 17a ... Sun gear 17b ... First pinion gear 17c ... Second pinion gear 17d ... Carrier 17e ... Ring gear 18 ... Counter shaft 19 ... Output shaft 21 ... Fourth power transmission mechanism 22 ... Variator 23 ... Control device E ... Engine

Claims (6)

動力源により回転駆動される入力軸と、
この入力軸が伝達する動力に基づいて動力を出力する出力軸と、
第１回転要素、第２回転要素及び第３回転要素とから構成され、前記第１回転要素が前記入力軸に連結し、前記第１回転要素に入力された動力を前記第２回転要素及び第３回転要素へ分配する差動歯車機構と、
この差動歯車機構の前記第２回転要素に連結するバリエータ入力軸と、
一端が前記バリエータ入力軸に連結し、他端が前記出力軸に第１係合手段により選択的に連結するバイパス軸と、
前記バリエータ入力軸に連結する無段変速機構と、
前記バリエータ入力軸に並設されたカウンタ軸と、
前記無段変速機構の出力を前記カウンタ軸に伝達する第１動力伝達機構と、
前記差動歯車機構の前記第３回転要素の出力を前記カウンタ軸に伝達する第２動力伝達機構と、
前記カウンタ軸及び前記出力軸に連結され、前記第１動力伝達機構の出力と前記第２動力伝達機構の出力とを合わせた出力を第２係合手段により前記カウンタ軸から前記出力軸に選択的に伝達する第３動力伝達機構と、
前記カウンタ軸及び前記出力軸に連結され、前記第１動力伝達機構の出力と前記第２動力伝達機構の出力とを合わせた出力を、前記第３動力伝達機構が前記出力軸に伝達する回転方向と逆の回転方向で、第３係合手段により前記カウンタ軸から前記出力軸に選択的に伝達する第４動力伝達機構と、
前記第１動力伝達機構及び前記第２動力伝達機構から伝達される動力を前記第３動力伝達機構で合わせて、前記出力軸に伝達する前進低速モードと、前記第１動力伝達機構及び第２動力伝達機構から伝達される動力を前記第４動力伝達機構で合わせて、前記出力軸に伝達する後進モードと、前記第２回転要素から前記バリエータ入力軸を経由した動力と、前記第３回転要素から前記第２動力伝達機構、前記第１動力伝達機構、前記無段変速機構を経由した動力とを前記バイパス軸で合わせて、前記第１係合手段を介して前記出力軸に伝達する前進高速モードとを前記第１から第３係合手段の係合状態を制御して切り換えるモード制御装置と、
を備えることを特徴とするパワースプリット型無段変速装置。 An input shaft that is rotationally driven by a power source;
An output shaft that outputs power based on the power transmitted by the input shaft;
A first rotating element, a second rotating element, and a third rotating element are configured. The first rotating element is connected to the input shaft, and the power input to the first rotating element is transmitted to the second rotating element and the second rotating element. A differential gear mechanism for distributing to three rotating elements;
A variator input shaft coupled to the second rotating element of the differential gear mechanism;
A bypass shaft having one end connected to the variator input shaft and the other end selectively connected to the output shaft by a first engagement means;
A continuously variable transmission mechanism coupled to the variator input shaft;
A counter shaft arranged in parallel with the variator input shaft;
A first power transmission mechanism for transmitting the output of the continuously variable transmission mechanism to the counter shaft;
A second power transmission mechanism for transmitting the output of the third rotating element of the differential gear mechanism to the counter shaft;
An output that is coupled to the counter shaft and the output shaft and that combines the output of the first power transmission mechanism and the output of the second power transmission mechanism is selectively selected from the counter shaft to the output shaft by the second engagement means. A third power transmission mechanism for transmitting to
A rotational direction coupled to the counter shaft and the output shaft, and in which the third power transmission mechanism transmits the combined output of the first power transmission mechanism and the output of the second power transmission mechanism to the output shaft. A fourth power transmission mechanism for selectively transmitting from the counter shaft to the output shaft by a third engagement means in a direction opposite to the rotation direction;
A forward low-speed mode in which power transmitted from the first power transmission mechanism and the second power transmission mechanism is combined by the third power transmission mechanism and transmitted to the output shaft; and the first power transmission mechanism and the second power A reverse mode in which the power transmitted from the transmission mechanism is combined by the fourth power transmission mechanism and transmitted to the output shaft, power from the second rotating element via the variator input shaft, and from the third rotating element The forward high speed mode in which the power passing through the second power transmission mechanism, the first power transmission mechanism, and the continuously variable transmission mechanism is combined with the bypass shaft and transmitted to the output shaft via the first engagement means. A mode control device that controls and switches the engagement state of the first to third engagement means;
A power split type continuously variable transmission comprising: 前記無段変速機構は、
２組の入力ディスクと、２組の出力ディスクと、前記入力ディスクと前記出力ディスクの間に傾転自在に配設された複数のパワーローラからなるトロイダル型バリエータと、
前記バリエータ入力軸と前記バイパス軸との間に設けられ、前記入力ディスクを前記パワーローラを介して前記出力ディスクに押圧するローディング機構と、
を有することを特徴とする請求項１に記載のパワースプリット型無段変速装置。 The continuously variable transmission mechanism includes:
Two sets of input discs, two sets of output discs, and a toroidal variator comprising a plurality of power rollers arranged to be tiltable between the input discs and the output discs;
A loading mechanism which is provided between the variator input shaft and the bypass shaft and presses the input disk against the output disk via the power roller;
The power split type continuously variable transmission according to claim 1, comprising: 前記ローディング機構を、前記トロイダル型バリエータに対し、差動歯車機構と反対方向に配設したことを特徴とする請求項２に記載のパワースプリット型無段変速装置。   The power split type continuously variable transmission according to claim 2, wherein the loading mechanism is disposed in a direction opposite to the differential gear mechanism with respect to the toroidal variator. 前記第４動力伝達機構を、前記トロイダル型バリエータと前記第３動力伝達機構との間に配設したことを特徴とする請求項２または３に記載のパワースプリット型無段変速装置。   The power split type continuously variable transmission according to claim 2 or 3, wherein the fourth power transmission mechanism is disposed between the toroidal variator and the third power transmission mechanism. 前記差動歯車機構の前記第１回転要素はリングギヤで、前記第２回転要素はサンギヤで、前記第３回転要素はキャリアであることを特徴とする請求項１に記載のパワースプリット型無段変速装置。   The power split type continuously variable transmission according to claim 1, wherein the first rotating element of the differential gear mechanism is a ring gear, the second rotating element is a sun gear, and the third rotating element is a carrier. apparatus. 前記第１動力伝達機構は、前記無段変速機構の出力側に固定された第１ギヤと、前記第１ギヤに噛合する第２ギヤと、前記第２ギヤと噛合するとともに、前記カウンタ軸に固定された第３ギヤからなり、
前記第２動力伝達機構は、前記バリエータ入力軸に回転自在に設けられた第４ギヤと、この第４ギヤに噛合するとともに、前記カウンタ軸に固定された第５ギヤとからなり、
前記第３動力伝達機構は、前記出力軸に固定されるとともに、前記第１係合手段により前記バイパス軸に係合する第６ギヤと、前記カウンタ軸に回転自在に設けられ、前記第２係合手段により前記カウンタ軸と係合する第７ギヤとからなり、
前記第４動力伝達機構は、前記第６ギヤと噛合し、回転自在に設けられた第８ギヤと、前記カウンタ軸に固定された第９ギヤと、前記第６ギヤと前記第３係合手段を介して係合するとともに前記第９ギヤと噛合する第１０ギヤとからなり、
前記変速制御装置は、前記前進低速モード時に前記第２係合手段のみを係合し、前記前進高速モード時に前記第１係合手段のみを係合し、前記後進モード時に前記第３係合手段のみを係合するように制御することを特徴とする請求項１に記載のパワースプリット型無段変速装置。 The first power transmission mechanism meshes with a first gear fixed to the output side of the continuously variable transmission mechanism, a second gear meshing with the first gear, the second gear, and the counter shaft. Consisting of a fixed third gear,
The second power transmission mechanism includes a fourth gear rotatably provided on the variator input shaft, and a fifth gear meshed with the fourth gear and fixed to the counter shaft ,
The third power transmission mechanism is fixed to the output shaft, and is rotatably provided on the counter shaft and a sixth gear that is engaged with the bypass shaft by the first engagement means. A seventh gear engaged with the countershaft by a combination means;
The fourth power transmission mechanism is engaged with the sixth gear, and an eighth gear rotatably provided, a ninth gear fixed to the counter shaft, the sixth gear, and the third engagement means. And a tenth gear that engages with the ninth gear,
The speed change control device engages only the second engagement means in the forward low speed mode, engages only the first engagement means in the forward high speed mode, and the third engagement means in the reverse speed mode. 2. The power split type continuously variable transmission according to claim 1, wherein control is performed so that only the engagement is established.
JP2005043753A 2005-02-21 2005-02-21 Power split type continuously variable transmission Expired - Fee Related JP4037874B2 (en)

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