JPH0765654B2 - Planetary gear train - Google Patents

Planetary gear train

Info

Publication number
JPH0765654B2
JPH0765654B2 JP1047795A JP4779589A JPH0765654B2 JP H0765654 B2 JPH0765654 B2 JP H0765654B2 JP 1047795 A JP1047795 A JP 1047795A JP 4779589 A JP4779589 A JP 4779589A JP H0765654 B2 JPH0765654 B2 JP H0765654B2
Authority
JP
Japan
Prior art keywords
gear
planetary gear
planetary
carrier
gears
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.)
Expired - Lifetime
Application number
JP1047795A
Other languages
Japanese (ja)
Other versions
JPH02229946A (en
Inventor
昇 服部
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to JP1047795A priority Critical patent/JPH0765654B2/en
Priority to DE69018675T priority patent/DE69018675T2/en
Priority to EP90103696A priority patent/EP0385345B1/en
Publication of JPH02229946A publication Critical patent/JPH02229946A/en
Priority to US07/815,617 priority patent/US5135444A/en
Publication of JPH0765654B2 publication Critical patent/JPH0765654B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears

Description

【発明の詳細な説明】 （産業上の利用分野） 本発明は、自動変速機の歯車変速機等に適応される遊星
歯車列に関する。Description: TECHNICAL FIELD The present invention relates to a planetary gear train adapted to a gear transmission of an automatic transmission and the like.

（従来の技術） 従来の歯車変速装置としては、例えば、特開昭50−6466
0号公報に示されている。(Prior Art) As a conventional gear transmission, for example, JP-A-50-6466
This is shown in Japanese Patent Publication No. 0.

この歯車変速装置には、第13図に示すように、シングル
プラネタリ型遊星歯車を３組用いた遊星歯車列が適用さ
れていて、この遊星歯車列は、第２サンギヤと第３サン
ギヤとを一体に結合して回転メンバが構成され、第３
キャリヤにより回転メンバが構成され、第１リングギ
ヤ，第２キャリヤ，第３リングギヤを一体に結合して回
転メンバが構成され、第２リングギヤ，第１キャリヤ
を一体に結合して回転メンバが構成され、第１サンギ
ヤにより回転メンバが構成されている。As shown in FIG. 13, a planetary gear train using three sets of single planetary type planetary gears is applied to this gear transmission, and this planetary gear train integrally includes a second sun gear and a third sun gear. To form a rotating member,
The carrier constitutes a rotary member, the first ring gear, the second carrier and the third ring gear are integrally coupled to form a rotary member, and the second ring gear and the first carrier are integrally coupled to constitute a rotary member, The first sun gear constitutes a rotating member.

そして、この遊星歯車列の５つの回転メンバに入力軸，
出力軸，ケースを加えた８つのメンバを直結または締結
要素を介して結合することで歯車変速装置が構成され
る。Then, the five rotary members of this planetary gear train are connected to the input shaft,
A gear transmission is constructed by directly connecting eight members including an output shaft and a case, or connecting the members through a fastening element.

即ち、回転メンバ，，をクラッチC1,C2,C3を介し
てそれぞれ入力軸に結合し、また、回転メンバ，，
をブレーキB1,B2,B3を介してそれぞれケースに固定
し、また、回転メンバを内力軸に直結して構成され
る。That is, the rotating members are connected to the input shafts via the clutches C1, C2 and C3, respectively, and the rotating members are
Are fixed to the case via brakes B1, B2, B3, respectively, and the rotating member is directly connected to the internal force shaft.

その結果、第14図の共線図に示すように、締結要素を２
組締結し、２つの拘束条件を与えることにより１つの変
速段を構成し、第15図の締結論理表に示すように、直結
変速段を含む前進６速，後退２速を達成している。As a result, as shown in the alignment chart of FIG.
One gear stage is configured by engaging the two sets and applying two restraint conditions, and as shown in the engagement logic table of FIG. 15, the sixth forward gear and the second reverse gear including the direct gear shift stage are achieved.

（発明が解決しようとする課題） しかしながら、この従来の遊星歯車列にあっては、締結
要素の数を６個用いながら前進６速，後退２速の多段化
要求に応えているものの、５つの回転メンバを構成する
のに３組のシングルプラネタリ型遊星歯車を用いたもの
である為、構成要素数が多くなりコスト面で不利である
し、また軸方向に長大化してサイズ面でも不利である。(Problems to be Solved by the Invention) However, in this conventional planetary gear train, while using the number of fastening elements of six, the requirement for multistages of six forward speeds and two reverse speeds is met, but five Since three sets of single planetary type planetary gears are used to form the rotating member, the number of constituent elements increases, which is disadvantageous in terms of cost, and the axial enlargement is disadvantageous in terms of size. .

（発明の目的） 本発明は、上述のような課題に着目してなされたもの
で、低コストと軸方向長さの短縮化を図りながら変速段
の多段化を達成出来る新規で有用な遊星歯車列を提供す
ることを目的とする。(Object of the Invention) The present invention has been made by paying attention to the above-mentioned problems, and is a novel and useful planetary gear that can achieve a multi-speed shift stage while achieving low cost and axial length reduction. Intended to provide columns.

（課題を解決するための手段） 上記課題を解決するために本願発明の遊星歯車列では、
第１リングギヤ，第１サンギヤ，第１キャリヤを有する
第１遊星歯車と、第２リングギヤ，第２サンギヤ，第２
キャリヤを有する第２遊星歯車とを備えた遊星歯車列に
おいて、 前記第１キャリヤ第２キャリヤを一体化すると共に、第
1,第２遊星歯車の動力伝達に関与するギヤに同時に噛み
合うロングピニオンを含むピニオンを回転可能に支承す
る共通キャリヤを設け、 前記第１遊星歯車側ギヤと第２遊星歯車側ギヤと共通キ
ャリヤにより、第１遊星歯車側ギヤの歯数と第２遊星歯
車側ギヤの歯数と各ギヤへの噛み合いピニオン歯数の設
定により決まる歯数比が変速比の決定に関与する第３の
等価遊星歯車を成立させ、 前記第1,第２遊星歯車に第３の等価遊星歯車を加えた３
組の遊星歯車の存在に基づき、第１リングギヤ，第１サ
ンギヤ，第２リングギヤ，第２サンギヤ，共通キャリヤ
により、所定の拘束条件を与えることで互いに異なる回
転をすることが可能な５つの回転メンバを構成し、 且つ、前記５つの回転メンバに、入力部材，出力部材，
ケースを加えた８個のメンバのうち２つのメンバ間を一
体に結合する拘束を２つ与えることで前後進の各変速段
を得る拘束条件付与手段を設けた事を特徴とする手段と
した。(Means for Solving the Problems) In order to solve the above problems, in the planetary gear train of the present invention,
A first planetary gear having a first ring gear, a first sun gear, and a first carrier, a second ring gear, a second sun gear, and a second planetary gear.
A planetary gear train including a second planetary gear having a carrier, wherein the first carrier and the second carrier are integrated, and
1, a common carrier that rotatably supports a pinion including a long pinion that simultaneously meshes with gears involved in power transmission of the second planetary gear is provided, and the first planetary gear side gear, the second planetary gear side gear, and the common carrier A third equivalent planetary gear in which a gear ratio determined by setting the number of teeth of the first planetary gear side gear, the number of teeth of the second planetary gear side gear, and the number of meshing pinion teeth for each gear is involved in the determination of the gear ratio 3 is obtained by adding a third equivalent planetary gear to the first and second planetary gears.
Based on the existence of a set of planetary gears, five rotating members that can rotate differently by applying a predetermined constraint condition by the first ring gear, the first sun gear, the second ring gear, the second sun gear, and the common carrier. And an input member, an output member, and
Among the eight members including the case, two means for integrally connecting the two members are provided with a restraint condition giving means for obtaining each forward and backward shift speed by giving two restraints.

（作 用） 本発明の遊星歯車列では、第１キャリヤと第２キャリヤ
を一体化すると共に、第1,第２遊星歯車の動力伝達に関
与するギヤに同時に噛み合うロングピニオンを含むピニ
オンを回転可能に支承する共通キャリヤが設けられ、第
１遊星歯車側ギヤ（第１リングギヤまたは第１サンギ
ヤ）と第２遊星歯車側ギヤ（第２リングギヤまたは第２
サンギヤ）と共通キャリヤにより、第１遊星歯車側ギヤ
の歯数と第２遊星歯車側ギヤの歯数と各ギヤへの噛み合
いピニオン歯数の設定により決まる歯数比が変速比の決
定に関与する第３の等価遊星歯車を成立させている。(Operation) In the planetary gear train of the present invention, the first carrier and the second carrier are integrated, and the pinion including the long pinion that simultaneously meshes with the gears involved in the power transmission of the first and second planetary gears can be rotated. Is provided with a common carrier for supporting the first planetary gear side gear (first ring gear or first sun gear) and the second planetary gear side gear (second ring gear or second ring gear or second ring gear).
The gear ratio determined by the number of teeth of the first planetary gear side gear, the number of teeth of the second planetary gear side gear, and the number of meshing pinion teeth engaged with each gear is involved in the determination of the gear ratio by the sun gear) and the common carrier. The third equivalent planetary gear is established.

第1,第２遊星歯車に第３の等価遊星歯車を加えた３組の
遊星歯車の存在に基づき、第１遊星歯車の第１リングギ
ヤ，第１サンギヤと、第２遊星歯車の第２リングギヤ，
第２サンギヤと第1,第２遊星歯車に共通な共通キャリヤ
により、所定の拘束条件を与えることで互いに異なる回
転をすることが可能な５つの回転メンバが構成される。Based on the existence of three sets of planetary gears in which the third equivalent planetary gear is added to the first and second planetary gears, the first ring gear of the first planetary gear, the first sun gear, and the second ring gear of the second planetary gear,
The common carrier common to the second sun gear and the first and second planetary gears constitutes five rotating members that can rotate differently from each other by applying a predetermined constraint condition.

そして、本発明の遊星歯車列により前後進の各変速段を
得る場合には、拘束条件付与手段において、第１リング
ギヤ，第１サンギヤ，第２リングギヤ，第２サンギヤ，
共通キャリヤによる５つの回転メンバに、入力部材，出
力部材，ケースを加えた８個のメンバのうち２つのメン
バ間を一体に結合する拘束を２つ与えることで得られ
る。When the forward and backward shift speeds are obtained by the planetary gear train of the present invention, the restraint condition giving means includes the first ring gear, the first sun gear, the second ring gear, the second sun gear,
It can be obtained by applying two restraints for integrally connecting two members out of eight members including the input member, the output member and the case to the five rotating members by the common carrier.

よって、外観的には２組の遊星歯車であることにより、
低コストと軸方向長さの短縮化を図りながら、実質的に
は３組の遊星歯車に基づく５つの回転メンバが構成され
ることにより、従来の遊星歯車では３列を必要とした共
線図を描くことができ、変速段の多段化要求に応えるこ
とができる。Therefore, because of the appearance of two sets of planetary gears,
The collinear diagram that requires three rows in the conventional planetary gears, because five rotating members based on three sets of planetary gears are substantially configured while achieving low cost and shortening the axial length. Can be drawn, and it is possible to meet the demand for multiple gears.

加えて、変速段の数を最大設定変速段未満の実用に供す
る変速段の数（例えば、前進５段や６段）に設定した場
合、変速比の設定が、第１遊星歯車の歯数比と第２遊星
歯車の歯数比と第３の等価遊星歯車による歯数比の３つ
の値により設定されるし、十分に変速比の選択自由度を
持つことで、各変速段で最適な変速比に設定することが
できる。In addition, when the number of gears is set to a number less than the maximum set gear for practical use (for example, 5 forward gears or 6 forward gears), the gear ratio is set to the gear ratio of the first planetary gears. It is set by three values of the gear ratio of the second planetary gear and the gear ratio of the third equivalent planetary gear, and by having a sufficient degree of freedom in selecting the gear ratio, the optimum gear shift at each gear stage is possible. It can be set to a ratio.

また、十分の選択余裕を持って変速段を設定しているも
のであるため、各変速段での２つの拘束条件の一方のみ
を変化させて隣接する変速段を得ることができ、これに
より、隣接する変速段への変速が最小限の締結要素の変
化によりなされることになり、良好な変速フィーリング
による変速品質を確保し易い。Further, since the shift speed is set with a sufficient selection margin, only one of the two constraint conditions at each shift speed can be changed to obtain the adjacent shift speed. The gear shift to the adjacent gear is performed by the minimum change of the engagement element, and it is easy to secure the gear quality with a good gear feel.

（実施例） 以下、本発明の実施例を図面に基づいて説明する。(Example) Hereinafter, the Example of this invention is described based on drawing.

まず、構成を説明する。First, the configuration will be described.

第１図は第１実施例の遊星歯車列を適用した遊星歯車変
速装置のスケルトン図である。FIG. 1 is a skeleton diagram of a planetary gear transmission to which the planetary gear train of the first embodiment is applied.

遊星歯車列は、第１リングギヤR1,第１サンギヤS1,第１
キャリヤを有する第１遊星歯車PG1と、第２リングギヤR
2,第２サンギヤS2,第２キャリヤを有する第２遊星歯車P
G2と、前記第１リングギヤR1と第１サンギヤS1とに噛み
合う第１ショートピニオンPS1と、第２リングギヤR2に
噛み合う第２ショートピニオンPS2と、第１遊星歯車PG1
側では第１ショートピニオンPS1に噛み合い、第２遊星
歯車PG2側では第２ショートピニオンPS2と第２サンギヤ
S2とに噛み合うロングピニオンPLを含むピニオンPS1,PS
2,PLを回転可能に支承する共通キャリヤPCとを備えてい
る。The planetary gear train includes the first ring gear R1, the first sun gear S1, and the first
A first planetary gear PG1 having a carrier and a second ring gear R
2, a second planetary gear P having a second sun gear S2 and a second carrier
G2, a first short pinion PS1 meshing with the first ring gear R1 and the first sun gear S1, a second short pinion PS2 meshing with the second ring gear R2, and a first planetary gear PG1.
On the side, meshes with the first short pinion PS1, and on the side of the second planetary gear PG2, the second short pinion PS2 and the second sun gear.
Pinion PS1, PS including long pinion PL that meshes with S2
It has a common carrier PC that rotatably supports the PL.

そして、前記第１サンギヤS1に連結される回転メンバ
と、共通キャリヤPCに連結される回転メンバと、第１
リングギヤR1に連結される回転メンバと、第２リング
ギヤR2に連結される回転メンバと、第２サンギヤS2に
連結される回転メンバにより、所定の拘束条件を与え
ることで互いに異なる回転をすることが可能な５つの回
転メンバが構成されている。The rotating member connected to the first sun gear S1, the rotating member connected to the common carrier PC, and the first
The rotating member connected to the ring gear R1, the rotating member connected to the second ring gear R2, and the rotating member connected to the second sun gear S2 can rotate differently by applying a predetermined constraint condition. 5 rotary members are configured.

そして、この遊星歯車列の５つの回転メンバに入力軸
，出力ギヤ，ケースを加えた８つのメンバを直結
または締結要素を介して結合することで歯車変速装置が
構成される。Then, a gear transmission is configured by connecting eight rotating members of the planetary gear train, which are added with an input shaft, an output gear, and a case, through direct connection or fastening elements.

即ち、回転メンバ，，をクラッチC1,C2,C3を介し
てそれぞれ入力軸に結合し、また、回転メンバ，
，をそれぞれブレーキB1,B2,B3を介してケースに
固定し、また、回転メンバを出力ギヤに直結して構
成される。That is, the rotating members are connected to the input shafts via the clutches C1, C2 and C3, respectively, and the rotating members are
, Are fixed to the case via brakes B1, B2, B3, respectively, and the rotating member is directly connected to the output gear.

また、締結要素であるクラッチC1,クラッチC2,クラッチ
C3とブレーキB1,B2,B3には、変速位置に対応して締結・
非締結を制御する締結要素制御手段（拘束条件付与手
段）が接続される。Also, clutch C1, clutch C2, clutch
Fasten C3 and brakes B1, B2, B3 according to the gear position.
A fastening element control means (constraint condition giving means) for controlling non-fastening is connected.

次に、第１実施例の作用を説明する。Next, the operation of the first embodiment will be described.

第１実施例の遊星歯車列を用いた歯車変速装置では、第
２図の共線図に示すように、締結要素を２組締結し、２
つの拘束条件を与えることにより１つの変速段を構成さ
れる。In the gear transmission using the planetary gear train of the first embodiment, two sets of fastening elements are fastened as shown in the alignment chart of FIG.
One shift stage is configured by giving one constraint condition.

即ち、横軸に設定歯数比に対応して割りふられる回転メ
ンバ，，，，の位置をとり、縦軸に回転速度
比（＝各メンバ−回転速度÷インプット回転速度）をと
り、前記回転メンバ，，，，の位置を通り縦
方向に引かれる直線と、回転速度比０と回転速度比１に
対応して横方向に引かれる直線との交点にそれぞれブレ
ーキとクラッチの締結要素を表示し、締結される２つの
締結要素を結ぶ線により共線図が描かれる。That is, the abscissa axis represents the positions of the rotating members, ..., Which are allocated corresponding to the set tooth number ratio, and the ordinate axis represents the rotational speed ratio (= each member-rotational speed ÷ input rotational speed). The engaging elements of the brake and clutch are displayed at the intersections of the straight line drawn in the vertical direction through the positions of the members, ..., and the straight line drawn in the horizontal direction corresponding to the rotation speed ratio 0 and the rotation speed ratio 1, respectively. , A collinear diagram is drawn by a line connecting two fastening elements to be fastened.

この共線図では、回転メンバ上で交わる交点が出力ギ
ヤの変速比の逆数を示し、締結要素を２組締結した場
合、回転速度比０を超え１未満のアンダードライブ側に
３つの変速段が得られ、回転速度比１を超えるオーバド
ライブ側に２つの変速段が得られ、回転速度比がマイナ
ス逆転側に２つの変速段が得られることになる。In this collinear diagram, the intersection point on the rotating member indicates the reciprocal of the gear ratio of the output gear, and when two sets of engaging elements are engaged, there are three gear stages on the underdrive side where the rotational speed ratio exceeds 0 and is less than 1. Thus, two shift speeds are obtained on the overdrive side where the rotation speed ratio exceeds 1, and two shift speeds are obtained on the minus reverse rotation side with the rotation speed ratio.

従って、変速比１の直結変速段を含んだ場合、第３図の
締結論理表に示すように、各前進変速比から次のより高
いまたはより低い変速比への変速が、一つの締結要素の
締結から非締結への変化と、他の一つの締結要素の非締
結から締結への変化によってなされ、最小限の締結要素
の変化によってなされるため、変速品質を確保しやす
く、下記に説明する様に、前進６速，後退２速を達成で
きる。Therefore, in the case of including the direct gear shift stage of the gear ratio 1, as shown in the engagement logic table of FIG. 3, the shift from each forward gear ratio to the next higher or lower gear ratio is performed by one engagement element. The change from the engagement to the non-engagement and the change from the other one of the engagement elements to the non-engagement to the engagement, and the minimum change in the engagement elements, it is easy to secure the shift quality, and as described below. In addition, 6 forward speeds and 2 reverse speeds can be achieved.

後退速の場合には、クラッチC1の締結による回転メンバ
からの入力とし、クラッチC1とブレーキB2の締結によ
り後退２速を得、クラッチC1とブレーキB3の締結により
後退１速を得ている。In the case of the reverse speed, the input from the rotating member is obtained by the engagement of the clutch C1, the second reverse speed is obtained by the engagement of the clutch C1 and the brake B2, and the first reverse speed is obtained by the engagement of the clutch C1 and the brake B3.

ニュートラルの場合は、締結要素の０ケ又は１ケの締結
により得られるもので、ここでは後退１速とニュートラ
ル相互変速時や前進１速とニュートラルの相互変速時に
変速要素の締結開放の数を少なく抑える為、ブレーキB3
を締結することで得ている。In the case of neutral, it can be obtained by engaging 0 or 1 engagement elements. Here, the number of disengagement of transmission elements is reduced during the first reverse and the neutral mutual shift, or the forward first and the neutral mutual shift. Brake B3 to hold
Is obtained by concluding.

前進速の場合で、アンダードライブ側では、クラッチC3
の締結による回転メンバからの入力とし、クラッチC3
とブレーキB3の締結により前進１速を得、クラッチC3と
ブレーキB2の締結により前後２速を得、クラッチC3とブ
レーキB1の締結により前進３速を得ている。On the underdrive side at forward speed, clutch C3
Clutch C3
The first forward speed is obtained by engaging the brake C3 and the brake B3, the front and rear second speed is obtained by engaging the clutch C3 and the brake B2, and the third forward speed is obtained by engaging the clutch C3 and the brake B1.

また、直結４速は、クラッチC1,C2,C3のうちいずれか２
つを選択することで得られるが、３速⇔４速や４速⇔５
速の時の締結要素の掛けかえを考慮してクラッチC2とク
ラッチC3との締結により得ている。In addition, the direct connection fourth speed is either clutch C1, C2, or C2
It can be obtained by selecting one, but it is 3 speed ⇔ 4 speed or 4 speed ⇔ 5
It is obtained by engaging the clutch C2 and the clutch C3 in consideration of the change of the engaging element at the time of high speed.

また、オーバドライブ側では、クラッチC2の締結による
回転メンバからの入力とし、クラッチC2とブレーキB1
の締結により前進５速を得、クラッチC2とブレーキB2の
締結により前進６速を得ている。On the overdrive side, the input from the rotating member is obtained by engaging the clutch C2, and the clutch C2 and the brake B1 are input.
The forward 5th speed is obtained by engaging the clutch and the forward 6th speed is achieved by engaging the clutch C2 and the brake B2.

以上説明してきたように、第１実施例の遊星歯車列にあ
っては、外観的に２組の遊星歯車であるが、所定の拘束
条件を与えることで互いに異なる回転をすることが可能
な５つの回転メンバが構成されている為、第１遊星歯車
PG1と第２遊星歯車PG2以外に、第１遊星歯車PG1側のギ
ヤ，第２遊星歯車PG2側のギヤ，共通キャリヤPCを有す
る等価遊星歯車を含み、実質的には３組の遊星歯車が存
在するとみなすことができる。As described above, the planetary gear train of the first embodiment has two sets of planetary gears in appearance, but it is possible to rotate the gears differently from each other by applying a predetermined constraint condition. The first planetary gear because it consists of two rotating members
In addition to PG1 and the second planetary gear PG2, the first planetary gear PG1 side gear, the second planetary gear PG2 side gear, an equivalent planetary gear having a common carrier PC are included, and substantially three sets of planetary gears exist. Then it can be considered.

この結果、従来の遊星歯車３列のものに対しては低コス
トと軸方向長さの短縮化を図り、従来の遊星歯車２列の
ものに対しては変速段の多段化要求に応える高い変速段
の設定自由度を持つ。As a result, the cost is reduced and the axial length is shortened with respect to the conventional planetary gear train of 3 rows, and the high speed shift corresponding to the multi-stage gear shift requirement is achieved with respect to the conventional planetary gear train of 2 rows. It has the freedom to set steps.

即ち、第２図と第14図に示す共線図及び第３図と第15図
に示す締結論理表の比較からも明らかなように、第１実
施例の２組の遊星歯車による遊星歯車列を歯車変速装置
に適用することで、従来例で示した３組のシングルプラ
ネタリ型遊星歯車による歯車変速装置（特開昭50−6466
0号）と全く同じ前進６速，後退２速を達成することが
出来る。That is, as is clear from the comparison of the alignment chart shown in FIGS. 2 and 14 and the engagement logic table shown in FIGS. 3 and 15, the planetary gear train using the two sets of planetary gears of the first embodiment is shown. Is applied to a gear transmission, the gear transmission using three single planetary type planetary gears shown in the conventional example (Japanese Patent Laid-Open No. 50-6466).
It is possible to achieve exactly the same 6th forward speed and 2nd reverse speed as No. 0).

次に第２実施例について説明する。Next, a second embodiment will be described.

第４図は第２実施例の遊星歯車列を適応した遊星歯車変
速装置のスケルトン図である。FIG. 4 is a skeleton diagram of a planetary gear transmission adapted to the planetary gear train of the second embodiment.

第２実施例の遊星歯車列は、第１リングギヤR1,第１サ
ンギヤS1,第１キャリヤを有する第１遊星歯車PG1と、第
２リングギヤR2,第２サンギヤS2,第２キャリヤを有する
第２遊星歯車PG2と、前記第１サンギヤS1に噛み合う第
１ショートピニオンPS1と、第２サンギヤS2に噛み合う
第２ショートピニオンPS2と、第１遊星歯車PG1側では第
１リングギヤR1と第１ショートピニオンPS1に噛み合
い、第２遊星歯車PG2側では第２リングギヤR2と第２シ
ョートピニオンPS2とに噛み合う歯数の異なるロングピ
ニオンPLを含むピニオンPS1,PS2,PLを回転可能に支承す
る共通キャリヤPCとを備えている。The planetary gear train of the second embodiment has a first planetary gear PG1 having a first ring gear R1, a first sun gear S1 and a first carrier, and a second planetary gear having a second ring gear R2, a second sun gear S2 and a second carrier. The gear PG2, the first short pinion PS1 that meshes with the first sun gear S1, the second short pinion PS2 that meshes with the second sun gear S2, and the first ring gear R1 and the first short pinion PS1 that mesh with the first planetary gear PG1 side. , The second planetary gear PG2 side is provided with a common carrier PC that rotatably supports the pinions PS1, PS2, PL including the long pinion PL with different number of teeth meshing with the second ring gear R2 and the second short pinion PS2. .

そして、前記共通キャリヤPCに連結される回転メンバ
と、第２リングギヤR2に連結される回転メンバと、第
１リングギヤR1に連結される回転メンバと、第２サン
ギヤS2に連結される回転メンバと、第１サンギヤS1に
連結される回転メンバにより、所定の拘束条件を与え
ることで互いに異なる回転をすることが可能な５つの回
転メンバが構成されている。A rotary member connected to the common carrier PC, a rotary member connected to the second ring gear R2, a rotary member connected to the first ring gear R1, and a rotary member connected to the second sun gear S2. The rotating members connected to the first sun gear S1 constitute five rotating members that can rotate differently from each other by applying a predetermined constraint condition.

そして、この遊星歯車列の５つの回転メンバに入力軸
，出力軸，ケースを加えた８つのメンバを直結ま
たは締結要素を介して結合することで歯車変速装置が構
成される。Then, a gear transmission is constructed by connecting eight members, which include an input shaft, an output shaft, and a case, to the five rotating members of the planetary gear train through direct connection or fastening elements.

即ち、回転メンバ，をクラッチC1,C2を介してそれ
ぞれ入力軸に結合し、また、回転メンバ，，を
それぞれブレーキB1,B2,B3を介してケースに固定し、
また、回転メンバを出力軸に直結して構成される。That is, the rotary member is connected to the input shaft via the clutches C1 and C2, and the rotary member is fixed to the case via the brakes B1, B2 and B3, respectively.
The rotary member is directly connected to the output shaft.

また、締結要素であるクラッチC1,クラッチC2とブレー
キB1,B2,B3には、変速位置に対応して締結・非締結を制
御する締結要素制御手段が接続される。Further, a clutch element C1, a clutch C2 and brakes B1, B2, B3, which are engagement elements, are connected with engagement element control means for controlling engagement / non-engagement in accordance with a shift position.

次に、第２実施例の作用を説明する。Next, the operation of the second embodiment will be described.

第２実施例の遊星歯車列を用いた歯車変速装置では、第
５図の共線図に示すように、締結要素を２組締結し、２
つの拘束条件を与えることにより１つの変速段を構成さ
れる。In the gear transmission using the planetary gear train of the second embodiment, two sets of fastening elements are fastened as shown in the alignment chart of FIG.
One shift stage is configured by giving one constraint condition.

即ち、横軸に設定歯数比に対応して割りふられる回転メ
ンバ，，，，の位置をとり、縦軸に回転速度
比をとり、前記回転メンバ，，，，の位置を
通り縦方向に引かれる直線と、回転速度比０と回転速度
比１に対応して横方向に引かれる直線との交点にそれぞ
れブレーキとクラッチの締結要素を表示し、締結される
２つの締結要素を結ぶ線により共線図が描かれる。That is, the abscissa represents the positions of the rotating members, ..., Which are allocated in correspondence with the set tooth number ratio, and the ordinate represents the rotational speed ratio, which passes through the positions of the rotating members ,. The engaging elements of the brake and the clutch are displayed at the intersections of the drawn straight line and the straight line drawn in the lateral direction corresponding to the rotational speed ratio 0 and the rotational speed ratio 1, respectively, and the line connecting the two engaging elements to be fastened is displayed. An alignment chart is drawn.

この共線図では、回転メンバ上で交わる交点が出力軸
の速度比の逆数を示し、締結要素を２組締結した場
合、回転速度比０を超え１未満のアンダードライブ側に
３つの変速段が得られ、回転速度比１を超えるオーバド
ライブ側に１つの変速段が得られ、回転速度比がマイナ
スの逆転側に１つの変速段が得られることになる。In this collinear diagram, the intersection point on the rotating member indicates the reciprocal of the speed ratio of the output shaft, and when two sets of fastening elements are fastened, three speed stages are provided on the underdrive side where the rotation speed ratio exceeds 0 and is less than 1. Thus, one shift speed is obtained on the overdrive side where the rotation speed ratio exceeds 1, and one shift speed is obtained on the reverse rotation side where the rotation speed ratio is negative.

従って、変速比１の直結変速段を含んだ場合、第６図の
締結論理表に示すように、各前進変速比から次のより高
いまたはより低い変速比への変速が、一つの締結要素の
締結から非締結への変化と、他の一つの締結要素の非締
結から締結への変化によってなされ、最小限の締結要素
の変化によってなされるため、変速品質を確保しやす
く、下記に説明する様に、前進５速，後退１速を達成で
きる。Therefore, in the case of including the direct gear shift stage of the gear ratio 1, as shown in the engagement logic table of FIG. 6, the shift from each forward gear ratio to the next higher or lower gear ratio is performed by one engagement element. The change from the engagement to the non-engagement and the change from the other one of the engagement elements to the non-engagement to the engagement, and the minimum change in the engagement elements, it is easy to secure the shift quality, and as described below. In addition, 5 forward speeds and 1 reverse speed can be achieved.

後退速の場合には、クラッチC1の締結による回転メンバ
からの入力とし、クラッチC1とブレーキB2の締結によ
り後退速を得ている。In the case of the reverse speed, the input from the rotating member is obtained by engaging the clutch C1, and the reverse speed is obtained by engaging the clutch C1 and the brake B2.

ニュートラルの場合は、締結要素の０ケ又は１ケ締結に
より得られるもので、ここでは後退１速とニュートラル
の相互変速時や前進１速とニュートラルの相互変速時に
変速要素の締結開放の数を少なく抑える為、ブレーキB2
を締結することで得ている。In the case of neutral, it can be obtained by engaging 0 or 1 engaging elements. Here, the number of disengagement of the speed change elements is reduced during mutual shift between 1st reverse and neutral, or 1st forward and mutual shift. Brake B2 to hold
Is obtained by concluding.

前進速の場合で、アンダードライブ側では、クラッチC2
の締結による回転メンバからの入力とし、クラッチC2
とブレーキB2の締結により前進１速を得、クラッチC2と
ブレーキB1の締結により前進２速を得、クラッチC2とブ
レーキB3の締結により前進３速を得ている。Clutch C2 on the underdrive side at forward speed
Clutch C2
The forward first speed is obtained by the engagement of the brake C2 and the brake B2, the second forward speed is obtained by the engagement of the clutch C2 and the brake B1, and the third forward speed is obtained by the engagement of the clutch C2 and the brake B3.

また、直結４速は、クラッチC1,C2の締結により得てい
る。In addition, the fourth directly connected speed is obtained by engaging the clutches C1 and C2.

また、オーバドライブ側では、クラッチC1の締結による
回転メンバからの入力とし、クラッチC1とブレーキB3
の締結により前進５速を得ている。On the overdrive side, clutch C1 and brake B3 are used as input from the rotating member by engaging clutch C1.
Fastening 5th is achieved by concluding.

尚、第６図の変速比の式において、α１は第１リングギ
ヤR1と第１サンギヤS1の比であり、α２は第２リングギ
ヤR2と第２サンギヤR2の比であり、ｋは第１リングギヤ
R1と第２リングギヤR2についての係数で（特許請求の範
囲に記載の第３の等価遊星歯車の歯数比）、ｋ＝ZA・Z
P2/ZD・ZP1で定義される（ZA;第１リングギヤ歯数,ZP1;
第１リングギヤとの噛み合いピニオン歯数,ZD;第２リン
グギヤ歯数,ZP2;第２リングギヤとの噛み合いピニオン
歯数）。In the gear ratio formula of FIG. 6, α 1 is the ratio of the first ring gear R1 and the first sun gear S1, α 2 is the ratio of the second ring gear R2 and the second sun gear R2, and k is the first Ring gear
A coefficient for R1 and the second ring gear R2 (the tooth number ratio of the third equivalent planetary gear set forth in the claims), k = Z A · Z
Defined by P2 / Z D・ Z P1 (Z A ; 1st ring gear tooth number, Z P1 ;
The number of pinion teeth meshing with the first ring gear, Z D ; the number of second ring gear teeth, Z P2 ; the number of pinion teeth meshing with the second ring gear).

以上説明してきたように、第２実施例の遊星歯車列にあ
っては、外観的に２組の遊星歯車であるが、所定の拘束
条件を与えることで互いに異なる回転をすることが可能
な５つの回転メンバが構成されている為、第１遊星歯車
PG1と第２遊星歯車PG2以外に、第１遊星歯車PG1側のギ
ヤ，第２遊星歯車PG2側のギヤと共通のキャリヤPCを有
する等価遊星歯車（特許請求の範囲に記載の第３の等価
遊星歯車）を含み、実質的には３組の遊星歯車が存在す
ることになる。As described above, the planetary gear train of the second embodiment has two sets of planetary gears in appearance, but it is possible to rotate the gears different from each other by applying a predetermined constraint condition. The first planetary gear because it consists of two rotating members
In addition to PG1 and the second planetary gear PG2, an equivalent planetary gear having a common carrier PC with the first planetary gear PG1 side gear and the second planetary gear PG2 side gear (the third equivalent planetary gear set forth in the claims). Gears), there will be substantially three sets of planet gears.

この結果、従来の遊星歯車３列のものに対しては低コス
トと軸方向長さの短縮化を図り、従来の遊星歯車２列の
ものに対しては変速段の多段化要求に応える高い変速段
の設定自由度を持つ。As a result, the cost is reduced and the axial length is shortened with respect to the conventional planetary gear train of 3 rows, and the high speed shift corresponding to the multi-stage gear shift requirement is achieved with respect to the conventional planetary gear train of 2 rows. It has the freedom to set steps.

即ち、締結要素に関しては、前進５速，後退１速を締結
要素５個により達成している。That is, with regard to the fastening elements, the fifth forward speed and the first reverse speed are achieved by the five fastening elements.

次に、本発明の遊星歯車列を拘束される回転関係式に基
づいて分けた各類型により説明する。Next, the types of the planetary gear train of the present invention will be described based on the types classified based on the constrained rotational relational expressions.

ここで、遊星歯車として、第１遊星歯車PG1,第２遊星歯
車PG2及び第１リングギヤR1,第２リングギヤR2,共通キ
ャリヤPCによる第３の等価遊星歯車が存在するものと
し、各遊星歯車の回転関係式が、シングルピニオン遊星
歯車の回転関係式により拘束される場合をＳとし、ダブ
ルピニオン遊星歯車の回転関係式により拘束される場合
をＷとして示す。また、ピニオンの数が最も少ないもの
を基本型とする（但し、同数の場合には同径のロングピ
ニオンを有するもの）。Here, as the planetary gears, the first planetary gear PG1, the second planetary gear PG2, the first ring gear R1, the second ring gear R2, and the third equivalent planetary gear by the common carrier PC are assumed to exist, and the rotation of each planetary gear The relational expression is represented by S when it is constrained by the rotation relational expression of the single pinion planetary gear, and W when it is constrained by the rotation relational expression of the double pinion planetary gear. The basic type is the one with the smallest number of pinions (however, if the number is the same, the long pinion with the same diameter is used).

＜SS−Ｓ＞ 第１遊星歯車PG1,第２遊星歯車PG2,第３の等価遊星歯車
が共にシングルピニオン遊星歯車の回転関係式により拘
束される場合の類型を第７図に示す。<SS-S> FIG. 7 shows a type in which the first planetary gear PG1, the second planetary gear PG2, and the third equivalent planetary gear are all constrained by the rotational relational expression of the single pinion planetary gear.

この第７図で左側の枠内には基本型が示され、右側の枠
内にはその変形例が示されている。In FIG. 7, the basic mold is shown in the left frame, and its modification is shown in the right frame.

＜SS−Ｗ＞ 第１遊星歯車PG1,第２遊星歯車PG2がシングルピニオン
遊星歯車の回転関係式により拘束され、第３の等価遊星
歯車がダブルピニオン遊星歯車の回転関係式により拘束
される場合の類型を第８図に示す。<SS-W> When the first planetary gear PG1 and the second planetary gear PG2 are constrained by the rotational relational expression of the single pinion planetary gear and the third equivalent planetary gear is constrained by the rotational relational expression of the double pinion planetary gear. The types are shown in FIG.

この第８図で左側の枠内には基本型が示され、右側の枠
内にはその変形例が示されている。In FIG. 8, the basic mold is shown in the left frame, and its modification is shown in the right frame.

＜SW−Ｓ（WS−Ｓ）＞ 第１遊星歯車PG1,第３の等価遊星歯車がシングルピニオ
ン遊星歯車が回転関係式により拘束され、第２遊星歯車
PG2がタブルピニオン遊星歯車の回転関係式により拘束
される場合の類型を第９図に示す。<SW-S (WS-S)> The first planetary gear PG1, the third equivalent planetary gear, the single pinion planetary gear is constrained by the rotational relational expression, and the second planetary gear
FIG. 9 shows a type in which PG2 is constrained by the rotational relational expression of the tabular pinion planetary gear.

この第９図で左側の枠内には基本型が示され、右側の枠
内にはその変形例が示されている。In FIG. 9, the basic mold is shown in the left frame, and its modification is shown in the right frame.

尚、第２遊星歯車PG2,第３の等価遊星歯車がシングルピ
ニオン遊星歯車の回転関係式により拘束され、第１遊星
歯車PG1がダブルピニオン遊星歯車の回転関係式により
拘束される、所謂、WS−ＳはSW−Ｓの第１遊星歯車PG1
と第２遊星歯車PG2とを入れ替えた形態であらわされる
ので、図示を省略する。The second planetary gear PG2 and the third equivalent planetary gear are constrained by the rotational relational expression of the single pinion planetary gear, and the first planetary gear PG1 is constrained by the rotational relational expression of the double pinion planetary gear, so-called WS- S is the first planetary gear PG1 of SW-S
Since the second planetary gear PG2 and the second planetary gear PG2 are interchanged, the illustration is omitted.

＜SW−Ｗ（WS−Ｗ）＞ 第１遊星歯車PG1がシングルピニオン遊星歯車の回転関
係式により拘束され、第２遊星歯車PG2と第３の等価遊
星歯車がダブルピニオン遊星歯車の回転関係式により拘
束される場合の類型を第10図に示す。<SW-W (WS-W)> The first planetary gear PG1 is constrained by the rotational relational expression of the single pinion planetary gear, and the second planetary gear PG2 and the third equivalent planetary gear are constrained by the rotational relational expression of the double pinion planetary gear. Figure 10 shows the types when restrained.

この第10図で左側の枠内には基本型が示され、右側の枠
内にはその変形例が示されている。In FIG. 10, the basic mold is shown in the left frame, and its modification is shown in the right frame.

尚、上記第１図に示す第１実施例の遊星歯車列はSW−Ｗ
型である。The planetary gear train of the first embodiment shown in FIG. 1 is SW-W.
It is a type.

また、第２遊星歯車PG2がシングルピニオン遊星歯車の
回転関係式により拘束され、第１遊星歯車PG1と第３の
等価遊星歯車がダブルピニオン遊星歯車の回転関係式に
より拘束される、所謂、WS−ＷはSW−Ｗの第１遊星歯車
PG1と第２遊星歯車PG2とを入れ替えた形態であらわされ
るので、図示を省略する。Also, the second planetary gear PG2 is constrained by the rotational relational expression of the single pinion planetary gear, and the first planetary gear PG1 and the third equivalent planetary gear are constrained by the rotational relational expression of the double pinion planetary gear, so-called WS- W is the first planetary gear of SW-W
Since the PG1 and the second planetary gear PG2 are interchanged, they are not shown.

＜WW−Ｓ＞ 第１遊星歯車PG1,第２遊星歯車PG2がダブルピニオン遊
星歯車の回転関係式により拘束され、第３の等価遊星歯
車が共にシングルピニオン遊星歯車の回転関係式により
拘束される場合の類型を第11図に示す。<WW-S> When the first planetary gear PG1 and the second planetary gear PG2 are constrained by the rotational relational expression of the double pinion planetary gear, and the third equivalent planetary gears are both constrained by the rotational relational expression of the single pinion planetary gear. Fig. 11 shows the types of.

この第11図で左側の枠内には基本型が示され、右側の枠
内にはその変形例が示されている。In FIG. 11, the basic mold is shown in the left frame, and its modification is shown in the right frame.

＜WW−Ｗ＞ 第１遊星歯車PG1,第２遊星歯車PG2,第３の等価遊星歯車
が共にダブルピニオン遊星歯車の回転関係式により拘束
される場合の類型を第12図に示す。<WW-W> FIG. 12 shows a type in which the first planetary gear PG1, the second planetary gear PG2, and the third equivalent planetary gear are all constrained by the rotational relational expression of the double pinion planetary gear.

この第12図で左側の枠内には基本型が示され、右側の枠
内にはその変形例が示されている。In FIG. 12, the basic mold is shown in the left frame, and its modification is shown in the right frame.

尚、上記第４図に示す第２実施例の遊星歯車列はWW−Ｗ
型である。The planetary gear train of the second embodiment shown in FIG. 4 is WW-W.
It is a type.

以上、実施例を図面に基づいて説明してきたが、具体例
な構成はこの実施例に限られるものではなく、本発明の
要旨を逸脱しない範囲における設計変更等があっても本
発明に含まれる。Although the embodiment has been described with reference to the drawings, the specific configuration is not limited to this embodiment, and even if there are design changes and the like within a range not departing from the gist of the invention, the invention is included in the invention. .

（発明の効果） 以上説明してきたように、本発明の遊星歯車列にあって
は、第１遊星歯車側ギヤと第２遊星歯車側ギヤと共通キ
ャリヤにより、第１遊星歯車側ギヤの歯数と第２遊星歯
車側ギヤの歯数と各ギヤへの噛み合いピニオン歯数の設
定により決まる歯数比が変速比の決定に関与する第３の
等価遊星歯車を成立させ、第1,第２遊星歯車に第３の等
価遊星歯車を加えた３組の遊星歯車の存在に基づき、第
１リングギヤ，第１サンギヤ，第２リングギヤ，第２サ
ンギヤ，共通キャリヤにより、所定の拘束条件を与える
ことで互いに異なる回転をすることが可能な５つの回転
メンバを構成したため、外観的には２組の遊星歯車であ
ることにより、低コストと軸方向長さの短縮化を図りな
がら、実質的には３組の遊星歯車に基づく５つの回転メ
ンバが構成され、従来の遊星歯車では３列を必要とした
共線図が描けることにより、変速段の多段化要求に応え
ることができるという効果が得られる。(Effect of the Invention) As described above, in the planetary gear train of the present invention, the number of teeth of the first planetary gear side gear is set by the first planetary gear side gear, the second planetary gear side gear, and the common carrier. And the number of teeth of the gear on the side of the second planetary gear and the number of teeth of the pinion that meshes with each gear establishes a third equivalent planetary gear that is involved in determining the gear ratio. Based on the existence of three sets of planetary gears, in which a third equivalent planetary gear is added to the gears, the first ring gear, the first sun gear, the second ring gear, the second sun gear, and the common carrier provide predetermined constraint conditions to each other. Since the five rotating members that can rotate differently are configured, the external appearance is two sets of planetary gears, so that the cost is reduced and the axial length is shortened. Five rotating men based on the planet gears There is constituted by the alignment chart that required three columns in the conventional planetary gear can be drawn, there is an advantage that it is possible to meet the multistage request gear.

加えて、変速段の数を最大設定変速段未満の実用に供す
る変速段の数に設定した場合、最適な変速比設定と容易
な変速品質確保を図ることができる。In addition, when the number of gear stages is set to a number less than the maximum set gear stage for practical use, it is possible to achieve optimum gear ratio setting and easy gear quality.

【図面の簡単な説明】[Brief description of drawings]

第１図は本発明第１実施例の遊星歯車列を適応した歯車
変速装置を示すスケルトン図、第２図は第１実施例装置
での変速関係を示す共線図、第３図は第１実施例装置で
の変速論理表を示す図である。 第４図は本発明第２実施例の遊星歯車列を適応した歯車
変速装置を示すスケルトン図、第５図は第２実施例装置
での変速関係を示す共線図、第６図は第２実施例装置で
の変速論理表を示す図である。 第７図はSS−Ｓ型の各遊星歯車列を示す概略図、第８図
はSS−Ｗ型の各遊星歯車列を示す概略図、第９図はSW−
Ｓ型（WS−Ｓ型）の各遊星歯車列を示す概略図、第10図
はSW−Ｗ型（WS−Ｗ型）の各遊星歯車列を示す概略図、
第11図はWW−Ｓ型の各遊星歯車列を示す概略図、第12図
はWW−Ｗ型の各遊星歯車列を示す概略図である。 第13図は従来の遊星歯車列を適応した歯車変速装置を示
すスケルトン図、第14図は従来の歯車変速装置での変速
関係を示す共線図、第15図は従来の歯車変速装置での変
速論理表を示す図である。 PG1……第１遊星歯車 R1……第１リングギヤ S1……第１サンギヤ PG2……第２遊星歯車 R1……第２リングギヤ S1……第２サンギヤ PS1……第１ショートピニオン PS2……第２ショートピニオン PL……ロングピニオン PC……共通キャリヤ ，，，，……回転メンバFIG. 1 is a skeleton diagram showing a gear transmission adapted to the planetary gear train of the first embodiment of the present invention, FIG. 2 is a collinear diagram showing a gear change relationship in the first embodiment, and FIG. It is a figure which shows the shift logic table in an Example apparatus. FIG. 4 is a skeleton diagram showing a gear transmission adapted to the planetary gear train of the second embodiment of the present invention, FIG. 5 is a collinear diagram showing a gear shifting relationship in the second embodiment, and FIG. It is a figure which shows the shift logic table in an Example apparatus. FIG. 7 is a schematic diagram showing each SS-S type planetary gear train, FIG. 8 is a schematic diagram showing each SS-W type planetary gear train, and FIG. 9 is a SW-
Schematic diagram showing each S-type (WS-S type) planetary gear train, FIG. 10 is a schematic diagram showing each SW-W type (WS-W type) planetary gear train,
FIG. 11 is a schematic diagram showing each WW-S type planetary gear train, and FIG. 12 is a schematic diagram showing each WW-W type planetary gear train. FIG. 13 is a skeleton diagram showing a conventional gear transmission adapted to a planetary gear train, FIG. 14 is a collinear diagram showing a gear change relationship in the conventional gear transmission, and FIG. 15 is a conventional gear transmission in the conventional gear transmission. It is a figure which shows a shift logic table. PG1 …… First planetary gear R1 …… First ring gear S1 …… First sun gear PG2 …… Second planetary gear R1 …… Second ring gear S1 …… Second sun gear PS1 …… First short pinion PS2 …… Second Short pinion PL …… Long pinion PC …… Common carrier ， ･ ･ ･ Rotating member

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】第１リングギヤ，第１サンギヤ，第１キャ
リヤを有する第１遊星歯車と、第２リングギヤ，第２サ
ンギヤ，第２キャリヤを有する第２遊星歯車とを備えた
遊星歯車列において、 前記第１キャリヤと第２キャリヤを一体化すると共に、
第1,第２遊星歯車の動力伝達に関与するギヤに同時に噛
み合うロングピニオンを含むピニオンを回転可能に支承
する共通キャリヤを設け、 前記第１遊星歯車側ギヤと第２遊星歯車側ギヤと共通キ
ャリヤにより、第１遊星歯車側ギヤの歯数と第２遊星歯
車側ギヤの歯数と各ギヤへの噛み合いピニオン歯数の設
定により決まる歯数比が変速比の決定に関与する第３の
等価遊星歯車を成立させ、 前記第1,第２遊星歯車に第３の等価遊星歯車を加えた３
組の遊星歯車の存在に基づき、第１リングギヤ，第１サ
ンギヤ，第２リングギヤ，第２サンギヤ，共通キャリヤ
により、所定の拘束条件を与えることで互いに異なる回
転をすることが可能な５つの回転メンバを構成し、 且つ、前記５つの回転メンバに、入力部材，出力部材，
ケースを加えた８個のメンバのうち２つのメンバ間を一
体に結合する拘束を２つ与えることで前後進の各変速段
を得る拘束条件付与手段を設けた事を特徴とする遊星歯
車列。1. A planetary gear train including a first planetary gear having a first ring gear, a first sun gear and a first carrier, and a second planetary gear having a second ring gear, a second sun gear and a second carrier. Integrating the first carrier and the second carrier,
A common carrier that rotatably supports a pinion including a long pinion that simultaneously meshes with gears involved in power transmission of the first and second planetary gears is provided, and the first planetary gear side gear, the second planetary gear side gear, and the common carrier As a result, the third equivalent planetary gear in which the gear ratio determined by the number of teeth of the first planetary gear side gear, the number of teeth of the second planetary gear side gear, and the number of meshing pinion teeth for each gear is involved in the determination of the gear ratio A gear is established, and a third equivalent planetary gear is added to the first and second planetary gears 3
Based on the existence of a set of planetary gears, five rotating members that can rotate differently by applying a predetermined constraint condition by the first ring gear, the first sun gear, the second ring gear, the second sun gear, and the common carrier. And an input member, an output member, and
A planetary gear train characterized by comprising constraint condition giving means for obtaining two forward and backward shift speeds by providing two constraints for integrally connecting two members out of eight members including a case.
JP1047795A 1989-02-28 1989-02-28 Planetary gear train Expired - Lifetime JPH0765654B2 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP1047795A JPH0765654B2 (en) 1989-02-28 1989-02-28 Planetary gear train
DE69018675T DE69018675T2 (en) 1989-02-28 1990-02-26 Epicyclic gear system.
EP90103696A EP0385345B1 (en) 1989-02-28 1990-02-26 Planetary gear system
US07/815,617 US5135444A (en) 1989-02-28 1992-01-07 Planetary gear system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1047795A JPH0765654B2 (en) 1989-02-28 1989-02-28 Planetary gear train

Publications (2)

Publication Number Publication Date
JPH02229946A JPH02229946A (en) 1990-09-12
JPH0765654B2 true JPH0765654B2 (en) 1995-07-19

Family

ID=12785306

Family Applications (1)

Application Number Title Priority Date Filing Date
JP1047795A Expired - Lifetime JPH0765654B2 (en) 1989-02-28 1989-02-28 Planetary gear train

Country Status (1)

Country Link
JP (1) JPH0765654B2 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3385374B2 (en) * 1995-07-06 2003-03-10 アイシン・エィ・ダブリュ株式会社 Automatic transmission
US5690578A (en) * 1996-04-29 1997-11-25 General Motors Corporation Ravigneaux planetary gear transmission
KR100341749B1 (en) * 1999-07-08 2002-06-24 이계안 GEAR TRAIN FOR ATs
US7033301B2 (en) * 2004-02-26 2006-04-25 Ford Global Technologies, Llc Planet pinion carrier assembly for Ravigneaux gearset
JP5617727B2 (en) 2011-03-28 2014-11-05 アイシン・エィ・ダブリュ株式会社 Automatic transmission

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63297844A (en) * 1987-05-28 1988-12-05 Toyota Motor Corp Speed change gear for automatic transmission
JPS63308252A (en) * 1987-06-05 1988-12-15 Toyota Motor Corp Speed change gears for automatic transmission

Also Published As

Publication number Publication date
JPH02229946A (en) 1990-09-12

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