JPS622175B2 - - Google Patents

Info

Publication number
JPS622175B2
JPS622175B2 JP56144135A JP14413581A JPS622175B2 JP S622175 B2 JPS622175 B2 JP S622175B2 JP 56144135 A JP56144135 A JP 56144135A JP 14413581 A JP14413581 A JP 14413581A JP S622175 B2 JPS622175 B2 JP S622175B2
Authority
JP
Japan
Prior art keywords
planetary gear
gear
gear set
sun
planetary
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
Application number
JP56144135A
Other languages
Japanese (ja)
Other versions
JPS57134049A (en
Inventor
Noboru Murakami
Koichiro Hirozawa
Kazuo Obara
Koichi Matsuo
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.)
Aisin Corp
Original Assignee
Aisin Seiki 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 Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Priority to JP56144135A priority Critical patent/JPS57134049A/en
Publication of JPS57134049A publication Critical patent/JPS57134049A/en
Publication of JPS622175B2 publication Critical patent/JPS622175B2/ja
Granted 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
    • 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • 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
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
    • 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
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0091—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising three reverse speeds
    • 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
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • 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
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears

Description

【発明の詳細な説明】 本発明は車輌用、特に自動車用の流体継手と組
合せて使用されるのに適した変速装置に関するも
のである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a transmission suitable for use in combination with a fluid coupling for vehicles, particularly automobiles.

トラツクあるいはバス等の大型車輌用の変速装
置としては少なくとも４段以上の変速段を有する
ことが望ましい。このためシングルピニオン式あ
るいはダブルピニオン式単純プラネタリギヤセツ
トを３組あるいは４組又はそれ以上組合わせ、そ
の中の各要素を適当に結びつけることにより４段
以上の変速段を実現することが考えられる。 It is desirable for a transmission device for a large vehicle such as a truck or bus to have at least four or more gear stages. Therefore, it is conceivable to realize four or more gear stages by combining three or four or more sets of single-pinion type or double-pinion type simple planetary gear sets and appropriately connecting each element therein.

このように組合わせた変速装置は非常に多数の
組合わせが考えられるが、更に以下に記す様な各
条件を満たすことが望しい。 Although a large number of combinations of transmissions are possible, it is desirable that the following conditions be satisfied.

(1) 出力軸は各変速段とも同一の要素と連結され
ること。(1) The output shaft must be connected to the same element for each gear.

(2) 各プラネタリギヤセツトの各要素は軸受部の
周速を低くするためその回転数が低いこと。(2) Each element of each planetary gear set has a low rotational speed in order to reduce the circumferential speed of the bearing.

(3) 各歯車の強度上の問題から各要素の歯荷重即
ち接線力が小さいこと。(3) Due to strength issues of each gear, the tooth load, or tangential force, of each element must be small.

(4) 各プラネタリギヤセツトの各歯車の歯数は噛
合条件を満足し、最小径となるサンギヤ及びプ
ラネタリギヤも必要歯数以上であること。(4) The number of teeth of each gear in each planetary gear set shall satisfy the meshing conditions, and the minimum diameter sun gear and planetary gear shall also have the required number of teeth or more.

(5) 各プラネタリギヤセツトの各要素の連結関係
がなるべく短かい長さで簡単に行ない得るこ
と。(5) The connection of each element of each planetary gear set can be easily achieved with the shortest possible length.

(6) 走行時の変速時には摩擦係合手段を切換えて
変速するが、この切換は切換シヨツクを小さく
なすために１個のみの切換で行なえること。(6) When changing gears while driving, the frictional engagement means are switched to change gears, but this switching can be done with only one switch in order to reduce the size of the switching shock.

本発明はこれらの各条件を考慮して基本的にシ
ングルピニオン式単純プラネタリギヤセツトを２
組、又ダブルピニオン式単純プラネギヤセツトを
１組使用し、クラツチ装置としては基本的に２
個、ブレーキ装置としては基本的に３個使用し、
各プラネタリギヤセツトの可動メンバーを適切に
結合し、クラツチ装置およびブレーキ装置を適宜
結合、解除することにより少なくとも前進４段、
後進１段の変速段を有する変速装置の提供を目的
とする。 Taking these conditions into account, the present invention basically consists of two single pinion type simple planetary gear sets.
One set of double pinion type simple planet gear set is used, and basically two clutch devices are used.
Basically, three brake devices are used.
By appropriately connecting the movable members of each planetary gear set and appropriately connecting and releasing the clutch devices and brake devices, at least four forward speeds can be achieved.
The object of the present invention is to provide a transmission having one reverse speed.

以下添付図面により本発明の実施態様を説明す
る。 Embodiments of the present invention will be described below with reference to the accompanying drawings.

本発明装置の第１実施例を第１Ａ図にて説明す
ると入力軸と出力軸との間にはダブルピニオン式
の第１プラネタリギヤセツトＸ１、シングルピニ
オン式の第２プラネタリギヤセツトＸ２、シング
ルピニオン式の第３プラネタリギヤセツトＸ３が
存在する。 The first embodiment of the device of the present invention will be explained with reference to FIG. 1A. Between the input shaft and the output shaft, there are a double pinion type first planetary gear set X1, a single pinion type second planetary gear set X2, and a single pinion type planetary gear set X2. A third planetary gear set X3 is present.

前記第１プラネタリギヤセツトＸ１は第１サン
ギヤＳ１と該第１サンギヤに噛合う第１プラネタ
リギヤＰ１と該第１プラネタリギヤに噛合う第２
プラネタリギヤＰ２と該第２プラネタリギヤに噛
合う第１リングギヤRG１と前記第１、第２プラ
ネタリギヤＰ１，Ｐ２を枢支する第１キヤリヤＣ
１を有する。 The first planetary gear set X1 includes a first sun gear S1, a first planetary gear P1 meshing with the first sun gear, and a second planetary gear P1 meshing with the first sun gear.
A planetary gear P2, a first ring gear RG1 that meshes with the second planetary gear, and a first carrier C that pivotally supports the first and second planetary gears P1 and P2.
1.

同様に前記第２プラネタリギヤセツトＸ２は第
２サンギヤＳ２と該第２サンギヤに噛合う第３プ
ラネタリギヤＰ３と該第３プラネタリギヤに噛合
う第２リングギヤRG２と前記第３プラネタリギ
ヤＰ３を枢支する第２キヤリヤＣ２を有する。又
第３プラネタリギヤセツトＸ３は第３サンギヤＳ
３と該第３サンギヤＳ３に噛合う第４プラネタリ
ギヤＰ４と該第４プラネタリギヤに噛合う第３リ
ングギヤRG３と前記第４プラネタリギヤＰ４を
枢支する第３キヤリヤＣ３とを有する。前記第１
リングギヤRG１と前記第２サンギヤＳ２とは駆
動的に連結される。前記第１キヤリヤＣ１と前記
第２キヤリヤＣ２と前記第３リングギヤRG３と
は夫々互に駆動的連結される。前記第２リングギ
ヤRG２と前記第３キヤリヤＣ３とは駆動的に連
結される。入力軸と前記第１リングギヤRG１、
前記第２サンギヤＳ２との間には、入力軸と該第
１リングギヤRG１、該第２サンギヤＳ２とを一
体的に締結したり切離したりする第１クラツチ
CL１が配設されている。入力軸と前記第１キヤ
リヤＣ１、前記第２キヤリヤＣ２、前記第３リン
グギヤRG３との間には入力軸と該第１キヤリヤ
Ｃ１、該第２キヤリヤＣ２、該第３リングギヤ
RG３とを一体的に締結したり切離したりする第
２クラツチCL２が配設されている。入力軸と前
記第１サンギヤＳ１との間には入力軸と該第１サ
ンギヤＳ１とを一体的に締結したり切離したりす
る第３クラツチCL３が配設されている。前記第
１サンギヤＳ１とケースとの間には第１ブレーキ
Ｂ１が設けられ、該ブレーキが作動した時には前
記第１サンギヤＳ１を固締し得る様になつてい
る。前記第１キヤリヤＣ１、前記第２キヤリヤＣ
２、前記第３キヤリヤRG３とケースとの間には
第２ブレーキＢ２が設けられ、該ブレーキが作動
した時には前記第１キヤリヤＣ１、前記第２キヤ
リヤＣ２、前記第３リングギヤRG３を固締し得
る様になつている。前記第３サンギヤＳ３とケー
スとの間には第３ブレーキＢ３が設けられ、該ブ
レーキが作動した時には前記第３サンギヤＳ３を
固締し得る様になつている。前記第２リングギヤ
RG２と前記第３キヤリヤＣ３は出力軸に動力的
に一体に連結されている。そして各プラネタリギ
ヤセツトＸ１，Ｘ２，Ｘ３において次式（後述の
全ての実施例に於いても同様である。）が成立す
る。 Similarly, the second planetary gear set X2 includes a second sun gear S2, a third planetary gear P3 meshing with the second sun gear, a second ring gear RG2 meshing with the third planetary gear, and a second carrier pivotally supporting the third planetary gear P3. It has C2. Also, the third planetary gear set X3 is the third sun gear S.
3, a fourth planetary gear P4 that meshes with the third sun gear S3, a third ring gear RG3 that meshes with the fourth planetary gear, and a third carrier C3 that pivotally supports the fourth planetary gear P4. Said first
Ring gear RG1 and second sun gear S2 are drivingly connected. The first carrier C1, the second carrier C2, and the third ring gear RG3 are drivingly connected to each other. The second ring gear RG2 and the third carrier C3 are drivingly connected. an input shaft and the first ring gear RG1;
A first clutch is provided between the second sun gear S2 and the first clutch that integrally connects and disconnects the input shaft, the first ring gear RG1, and the second sun gear S2.
CL1 is installed. The input shaft and the first carrier C1, the second carrier C2, and the third ring gear RG3 are connected to each other between the input shaft and the first carrier C1, the second carrier C2, and the third ring gear RG3.
A second clutch CL2 is provided which integrally engages and disengages RG3. A third clutch CL3 is disposed between the input shaft and the first sun gear S1 to integrally connect or disconnect the input shaft and the first sun gear S1. A first brake B1 is provided between the first sun gear S1 and the case, and is configured to lock the first sun gear S1 when the brake is activated. The first carrier C1, the second carrier C
2. A second brake B2 is provided between the third carrier RG3 and the case, and when the brake is activated, it can lock the first carrier C1, the second carrier C2, and the third ring gear RG3. It's becoming like that. A third brake B3 is provided between the third sun gear S3 and the case, and is configured to lock the third sun gear S3 when the brake is activated. the second ring gear
RG2 and the third carrier C3 are dynamically connected integrally to the output shaft. The following equation (the same applies to all embodiments to be described later) holds true for each planetary gear set X1, X2, and X3.

ＮRG1−（１−I1）ＮC1−I1NS1＝０ ＮRG2−（１＋I2）ＮC２＋I2NS2＝０ ＮRG3−（１＋I3）ＮC３＋I3NS3＝０ 但し ＮRG1，ＮRG2，ＮRG3；第１、第２、第３リン
グギヤの回転数 ＮC１，ＮC２，ＮC３；第１、第２、第３キヤ
リヤの回転数 ＮS１，ＮS２，ＮS３；第１、第２、第３サン
ギヤの回転数 I1，I2，I3；各リングギヤと各サンギヤとの半
径比とする。N RG1 - (1 - I 1 ) N C1 - I 1 N S1 = 0 N RG2 - (1 + I 2 ) N C2 + I 2 N S2 = 0 N RG3 - (1 + I 3 ) N C3 + I 3 N S3 = 0 However, N RG1 , N RG2 , N RG3 ; Number of rotations of the first, second, and third ring gears N C1 , N C2 , N C3 ; Number of rotations of the first, second, and third carriers N S1 , N S2 , N S3 ; The rotation speeds I 1 , I 2 , I 3 of the first, second, and third sun gears are the radius ratios of each ring gear and each sun gear.

ここで本発明による変速装置の具体的な各変速
段の数値を例示すればI1＝0.419，I2＝0.500，I3＝
0.419（後述のすべての実施例に於いても同様で
ある。）であり、本発明の変速装置の各変速段に
おける各クラツチCL１，CL２，CL３及び各ブ
レーキＢ１，Ｂ２，Ｂ３の作動と各変速段の減速
比の関係をまとめると第１Ｂ図のようになる。 Here, to give an example of specific numerical values of each gear stage of the transmission according to the present invention, I 1 =0.419, I 2 =0.500, I 3 =
0.419 (the same applies to all embodiments to be described later), and the operation of each clutch CL1, CL2, CL3 and each brake B1, B2, B3 at each gear stage of the transmission of the present invention and each shift The relationship between the speed reduction ratios of the stages is summarized as shown in FIG. 1B.

但しFn（ｎ＝１，２，３……）は前進変速段
を示し、例えばＦ１は前進第１速、Ｆ２は前進第
２速であり、又Rn（ｎ＝１，２……）は後進変
速段を示し、例えばＲ１は後進第１速であり又減
速比１：1.00を得るにはクラツチCL１，CL２，
CL３のうち何れか２個を適宜組み合わせれば得
られるものであり、少くともCL１とCL２、又は
CL１とCL３、或はCL２とCL３とを結合すれば
良い。第１Ｂ図ではCL１、CL２、CL３の全ク
ラツチを係合し得るとして表わしてある。以下後
述の全ての実施例も同様とする。そして各変速段
における各プラネタリギヤセツトの各要素の回転
数と接線力をまとめると第１Ｃ図のようになる。
但し、その値は入力軸を１とした比で表わされ、
但し接線力は入力軸のトルクがリングギヤに作用
したと仮定したときを１とする比で表わし、又プ
ラネタリギヤの接線力はサンギヤ及びリングギヤ
に等しいものである。尚、前述の第１Ｂ図と同一
の符号は同一対象物を意味するものであり、更に
Ａは変速段、Ｂはプラネタリギヤセツトの項目を
示しＮは回転数、Ｗは接線力を示すものであり、
又数字が少数点以下の場合は０を省略し例えば．
42として表わしまた．00は零を意味（後述のすべ
ての実施例に於ても同様とする。）する。尚、Ｆ
４（前進第４速）は減速比が１：1.00であるた
め、各々のサンギヤ、リングギヤ及びキヤリヤの
回転数Ｎは1.00、又各々のプラネタリギヤの回転
数Ｎは0.00であり、又その接線力Ｗは他の変速段
にて生ずる接線力に比して大巾に小となるもので
あり、即ち他の変速段では各々のクラツチのうち
何れか一個のクラツチのみの係合により、その係
合されたクラツチを介してのみ入力軸のトルクが
各要素に伝達されるのに対して、Ｆ４（前進第４
速）は少なくとも二個のクラツチの係合がなされ
ることにより、入力軸のトルクはその両クラツチ
にて分担され、その分担された入力軸のトルクが
各要素に伝達されるため、それにより生ずる各要
素の接線力は一個のみのクラツチの係合により入
力軸のトルクが分担されず、そのまま伝達される
場合に比して小さいことは白明であり、以下減速
比が１：1.00である。 However, Fn (n=1, 2, 3...) indicates the forward gear, for example, F1 is the first forward gear, F2 is the second forward gear, and Rn (n=1, 2...) is the reverse gear. For example, R1 is the first reverse gear, and to obtain a reduction ratio of 1:1.00, clutches CL1, CL2,
It can be obtained by appropriately combining any two of CL3, and at least CL1 and CL2, or
CL1 and CL3 or CL2 and CL3 may be combined. In FIG. 1B, all clutches CL1, CL2, and CL3 are shown as being able to be engaged. The same applies to all embodiments described below. The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 1C.
However, the value is expressed as a ratio with the input axis as 1,
However, the tangential force is expressed as a ratio assuming that the torque of the input shaft acts on the ring gear is 1, and the tangential force of the planetary gear is equal to that of the sun gear and the ring gear. Note that the same reference numerals as in Fig. 1B above refer to the same objects, and furthermore, A indicates the gear stage, B indicates the planetary gear set, N indicates the rotation speed, and W indicates the tangential force. ,
Also, if the number is below the decimal point, omit the 0, for example.
Also expressed as 42. 00 means zero (the same applies to all embodiments described below). In addition, F
4 (fourth forward speed) has a reduction ratio of 1:1.00, so the rotational speed N of each sun gear, ring gear, and carrier is 1.00, and the rotational speed N of each planetary gear is 0.00, and the tangential force W is much smaller than the tangential force generated in other gears, that is, in other gears, the engagement of only one of the clutches causes the force to be engaged. The torque of the input shaft is transmitted to each element only through the F4 (fourth forward clutch).
Speed) is generated because at least two clutches are engaged, and the input shaft torque is shared between both clutches, and the shared input shaft torque is transmitted to each element. It is clear that the tangential force of each element is smaller than when the torque of the input shaft is not shared and transmitted as is due to the engagement of only one clutch, and the reduction ratio is 1:1.00 below.

変速段における各要素の回転数Ｎ及び接線力Ｗ
を省略する。 Rotational speed N and tangential force W of each element in the gear stage
omitted.

次に本発明装置の第２実施例を第２Ａ図にて説
明すると、第１Ａ図の前記第１実施例において前
記第３プラネタリギヤセツトＸ３と前記出力軸と
の間にシングルピニオン式の第４プラネタリギヤ
セツトＸ４を介在してなる構成であり各要素との
連結関係は以下の如くである。 Next, a second embodiment of the device of the present invention will be explained with reference to FIG. 2A. In the first embodiment shown in FIG. 1A, a single pinion type fourth planetary gear is provided between the third planetary gear set X3 and the output shaft. The structure is formed by interposing the set X4, and the connection relationship with each element is as follows.

前記第４プラネタリギヤセツトＸ４は第４サン
ギヤＳ４と該第４サンギヤに噛合う第５プラネタ
リキヤＰ５と該第５プラネタリギヤに噛合う第４
リングギヤRG４と前記第５プラネタリギヤを枢
支する第４キヤリヤＣ４とを有する。前記第４リ
ングギヤRG４は前記第３サンギヤＳ３と駆動的
に連結され、前記第３ブレーキＢ３が作動した時
前記第３サンギヤＳ３と同様に第４リングギヤ
RG４は固固締される。前記第４キヤリヤＣ４と
ケースとの間には第４ブレーキＢ４が設けられ、
該ブレーキが作動した時には前記第４キヤリヤＣ
４を固締し得る様になつている。前記第４サンギ
ヤＳ４は前記第２リングギヤRG２、前記第３キ
ヤリヤＣ３に駆動的に連結されるとともに前記出
力軸に動力的に一体に連結される。 The fourth planetary gear set X4 includes a fourth sun gear S4, a fifth planetary gear P5 that meshes with the fourth sun gear, and a fourth planetary gear P5 that meshes with the fifth planetary gear.
It has a ring gear RG4 and a fourth carrier C4 that pivotally supports the fifth planetary gear. The fourth ring gear RG4 is drivingly connected to the third sun gear S3, and when the third brake B3 is operated, the fourth ring gear RG4 is connected to the third sun gear S3.
RG4 is firmly fixed. A fourth brake B4 is provided between the fourth carrier C4 and the case,
When the brake is activated, the fourth carrier C
4 can be secured. The fourth sun gear S4 is drivingly connected to the second ring gear RG2 and the third carrier C3, and is integrally and dynamically connected to the output shaft.

そして第４プラネタリギヤセツトＸ４において
次式（後述の全ての実施例に於いても同様であ
る。）が成立する。 In the fourth planetary gear set X4, the following equation (the same applies to all embodiments described later) holds true.

ＮRG４−（１＋I4）ＮC４＋I4NS4＝０ 但し ＮRG４；第４リングギヤの回転数 ＮC４；第４キヤリヤの回転数 ＮS４；第４サンギヤの回転数 I4；第４リングギヤと第４サンキヤとと
の半径比とする。 N RG4 - (1 + I 4 ) N C4 + I 4 N S4 = 0 However, N RG4 ; Number of rotations of the 4th ring gear N C4 ; Number of rotations of the 4th carrier N S4 ; Number of rotations of the 4th sun gear I 4 ; Number of rotations of the 4th ring gear Let it be the radius ratio of the fourth sankhya.

ここで本発明による変速装置の具体的な各変速
段の数値を例示すればI4＝0.562であり本発明の
変速装置の各変速段における各クラツチCL１，
CL２，CL３及び各ブレーキＢ１，Ｂ２，Ｂ３，
Ｂ４の作動と各変速段の減速比の関係をまとめる
と第２Ｂ図のようになる。 Here, to give an example of specific numerical values for each gear stage of the transmission according to the present invention, I 4 =0.562, and each clutch CL1,
CL2, CL3 and each brake B1, B2, B3,
The relationship between the operation of B4 and the reduction ratio of each gear stage is summarized as shown in Fig. 2B.

そして各変速段における各プラネタリギヤセツ
トの各要素の回転数と接線力をまとめると第２Ｃ
図のようになる。 The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as 2C.
It will look like the figure.

次に本発明装置の第３実施例を第３Ａ図にて説
明すると本実施例は第２Ａ図の前記第２実施例と
同様に第１Ａ図の前記第１実施例において前記第
３プラネタリギヤセツトＸ３と前記出力軸との間
にシングルピニオン式の前記第４プラネタリギヤ
セツトＸ４を介在してなる構成であり、各要素と
の連結関係は以下の如くである。 Next, a third embodiment of the device of the present invention will be explained with reference to FIG. 3A. This embodiment will be explained in the same manner as the second embodiment shown in FIG. 2A. The fourth planetary gear set X4 of a single pinion type is interposed between the output shaft and the output shaft, and the connection relationship with each element is as follows.

前記第４サンギヤＳ４は前記第３サンギヤＳ３
と駆動的に連結され、前記第３ブレーキＢ３が作
動した時、前記第３サンギヤＳ３と同様に第４サ
ンギヤＳ４は固締される。前記第４キヤリヤＣ４
とケースとの間には第４ブレーキＢ４が設けら
れ、該ブレーキが作動した時には前記第４キヤリ
ヤＣ４を固締し得る様になつている。前記第４リ
ングギヤRG４は前記第２リングギヤRG２、前記
第３キヤリヤＣ３に駆動的に連結されるとともに
前記出力軸に動力的に一体に連結される。 The fourth sun gear S4 is the third sun gear S3.
When the third brake B3 is actuated, the fourth sun gear S4 is locked in the same way as the third sun gear S3. Said fourth carrier C4
A fourth brake B4 is provided between the fourth carrier C4 and the case, and is adapted to clamp the fourth carrier C4 when the brake is actuated. The fourth ring gear RG4 is drivingly connected to the second ring gear RG2 and the third carrier C3, and is integrally and dynamically connected to the output shaft.

ここで本発明による変速装置の具体的な変速段
の数値を例示すれば、I4＝0.562であり、本発明
の変速装置の各変速段における各クラツチ及びブ
レーキの作動と各変速段の減速比の関係をまとめ
ると、第３Ｂ図のようになる。 Here, to give an example of the numerical values of the specific gears of the transmission according to the present invention, I 4 =0.562, and the operation of each clutch and brake at each gear of the transmission of the present invention and the reduction ratio of each gear The relationship is summarized as shown in Figure 3B.

そして、各変速段における各プラネタリギヤセ
ツトの各要素の回転数と接線力をまとめると第３
Ｃ図のようになる。 Summarizing the rotational speed and tangential force of each element of each planetary gear set at each gear stage, the third
It will look like Figure C.

次に、本発明装置の第４実施例を第４Ａ図にて
説明すると本実施例は前記第２実施例と同様に前
記第１実施例において、前記第３プラネタリギヤ
セツトＸ３と前記出力軸との間にシングルピニオ
ン式の第４プラネタリギヤセツトＸ４を介在して
なる構成であり、各要素との連結関係は以下の如
くである。 Next, a fourth embodiment of the device of the present invention will be described with reference to FIG. 4A. Similar to the second embodiment, this embodiment is similar to the second embodiment in that the third planetary gear set X3 and the output shaft are connected to each other in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set X4 is interposed between them, and the connection relationship with each element is as follows.

前記第４キヤリヤＣ４は、前記第３サンギヤＳ
３に駆動的に連結され、前記第３ブレーキＢ３が
作動した時、前記第３サンギヤＳ３と同様に第４
キヤリヤＣ４は固締される。前記第４サンギヤＳ
４と前記ケースとの間には第４ブレーキＢ４が設
けられ、該ブレーキが作動した時には、前記第４
サンギヤＳ４を固締し得る様になつている。前記
第４リングギヤRG４は、前記第２リングギヤRG
２、前記第３キヤリヤＣ３に駆動的に連結される
とともに、前記出力軸に動力的に一体に連結され
る。 The fourth carrier C4 is the third sun gear S.
3, and when the third brake B3 operates, the fourth brake
Carrier C4 is secured. Said fourth sun gear S
A fourth brake B4 is provided between the fourth brake B4 and the case, and when the brake is operated, the fourth brake B4
It is designed to be able to secure the sun gear S4. The fourth ring gear RG4 is the second ring gear RG4.
2. It is drivingly connected to the third carrier C3, and is also dynamically connected integrally to the output shaft.

ここで本発明による変速装置の具体的な変速段
の数値を例示すれば、I4＝0.562であり、本発明
の変速装置の各変速段における各クラツチ及びブ
レーキの作動と各変速段の減速比の関係をまとめ
ると第４Ｂ図のようになる。 Here, to give an example of the numerical values of the specific gears of the transmission according to the present invention, I 4 =0.562, and the operation of each clutch and brake at each gear of the transmission of the present invention and the reduction ratio of each gear The relationship is summarized as shown in Figure 4B.

そして、各変速段における各プラネタリギヤセ
ツトの各要素の回転数と接線力をまとめると第４
Ｃ図のようになる。 Summarizing the rotational speed and tangential force of each element of each planetary gear set at each gear stage, the fourth
It will look like Figure C.

次に本発明装置の第５実施例を第５Ａ図にて説
明すると、本実施例は前記第２実施例と同様に前
記第１実施例において、前記第３プラネタリギヤ
セツトＸ３と前記出力軸との間にシングルピニオ
ン式の第４プラネタリギヤセツトＸ４を介在して
なる構成であり、各要素との連結関係は以下の如
くである。 Next, a fifth embodiment of the device of the present invention will be explained with reference to FIG. 5A. Similar to the second embodiment, this embodiment differs from the third planetary gear set X3 and the output shaft in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set X4 is interposed between them, and the connection relationship with each element is as follows.

前記第４キヤリヤＣ４は前記第３サンギヤＳ３
に駆動的に連結され、前記第３ブレーキＢ３が作
動した時、前記第３サンギヤＳ３と同様に第４キ
ヤリヤＣ４は固締される。前記第４リングギヤ
RG４と前記ケースとの間には第４ブレーキＢ４
が設けられ、該ブレーキが作動した時には前記第
４リングギヤRG４を固締し得る様になつてい
る。前記第４サンギヤＳ４は、前記第２リングギ
ヤRG２、前記第３キヤリヤＣ３と駆動的に連結
されるとともに、前記出力軸に動力的に一体に連
結される。 The fourth carrier C4 is the third sun gear S3.
When the third brake B3 is actuated, the fourth carrier C4 is fixed in the same way as the third sun gear S3. Said fourth ring gear
A fourth brake B4 is installed between RG4 and the case.
is provided so that the fourth ring gear RG4 can be fixed when the brake is activated. The fourth sun gear S4 is drivingly connected to the second ring gear RG2 and the third carrier C3, and is also dynamically connected integrally to the output shaft.

ここで本発明による変速装置の具体的な変速段
の数値を例示すれば、I4＝0.562であり、本発明
の変速装置の各変速段における各クラツチと各ブ
レーキ作動と各変速段の減速比の関係をまとめる
と第５Ｂ図のようになる。そして各変速段におけ
る各プラネタリギヤセツトの各要素の回転数と接
線力をまとめると第５Ｃ図のようになる。 Here, to give an example of the numerical values of the specific gears of the transmission according to the present invention, I 4 =0.562, and each clutch and each brake operation at each gear of the transmission of the present invention and the reduction ratio of each gear The relationship is summarized as shown in Figure 5B. The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 5C.

次に本発明装置の第６実施例を第６Ａ図にて説
明すると、本実施例は前記第２実施例と同様に前
記第１実施例において、前記第３プラネタリギヤ
セツトＸ３と前記出力軸との間にシングルピニオ
ン式の第４プラネタリギヤセツトＸ４を介在して
なる構成であり、各要素との連結関係は以下の如
くである。 Next, a sixth embodiment of the device of the present invention will be explained with reference to FIG. 6A. Similar to the second embodiment, this embodiment differs from the third planetary gear set X3 and the output shaft in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set X4 is interposed between them, and the connection relationship with each element is as follows.

前記第４サンギヤＳ４は、前記第３サンギヤＳ
３と駆動的に連結され、前記第３ブレーキＢ３が
作動した時、前記第３サンギヤＳ３と同様に第４
サンギヤＳ４は固締される。前記第４リングギヤ
RG４と前記ケースとの間には第４ブレーキＢ４
が設けられ、該ブレーキが作動した時には前記第
４リングギヤRG４を固締し得る様になつてい
る。前記第４キヤリヤＣ４は、前記第２リングギ
ヤRG２、前記第３キヤリヤＣ３に駆動的に連結
されるとともに、前記出力軸に動力的に一体に連
結される。 The fourth sun gear S4 is the third sun gear S4.
3, and when the third brake B3 operates, the fourth brake
Sun gear S4 is fixed. Said fourth ring gear
A fourth brake B4 is installed between RG4 and the case.
is provided so that the fourth ring gear RG4 can be fixed when the brake is activated. The fourth carrier C4 is drivingly connected to the second ring gear RG2 and the third carrier C3, and is also dynamically connected integrally to the output shaft.

ここで本発明による変速装置の具体的な変速段
の数値を例示すれば、I4＝0.437であり、本発明
の変速装置の各変速段におけるクラツチと各ブレ
ーキの作動と各変速段の減速比の関係をまとめる
と第６Ｂ図のようになる。そして、各変速段にお
ける各プラネタリギヤセツトの各要素の回転数と
接線力をまとめると第６Ｃ図のようになる。 Here, to give an example of the numerical values of the specific gears of the transmission according to the present invention, I 4 =0.437, and the operation of the clutch and each brake at each gear of the transmission of the present invention and the reduction ratio of each gear The relationships are summarized as shown in Figure 6B. The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 6C.

次に、本発明装置の第７実施例を第７Ａ図にて
説明すると、本実施例は、前記第２実施例と同様
に前記第１実施例において、前記第３プラネタリ
ギヤセツトＸ３と前記出力軸との間にシングルピ
ニオン式の第４プラネタリギヤセツトＸ４を介在
してなる構成であり、各要素との連結関係は以下
の如くである。前記第４リングギヤRG４は、前
記第３サンギヤＳ３に駆動的に連結され、前記第
３ブレーキＢ３が作動した時、前記第３サンギヤ
Ｓ３と同様に第４リングギヤRG４は固締され
る。 Next, a seventh embodiment of the device of the present invention will be explained with reference to FIG. 7A. In this embodiment, similar to the second embodiment, in the first embodiment, the third planetary gear set X3 and the output shaft A single-pinion type fourth planetary gear set X4 is interposed between the two, and the connection relationship with each element is as follows. The fourth ring gear RG4 is drivingly connected to the third sun gear S3, and when the third brake B3 is operated, the fourth ring gear RG4 is fixed similarly to the third sun gear S3.

前記第４サンギヤＳ４と前記ケースとの間には
第４ブレーキＢ４が設けられ、該ブレーキが作動
した時には第４サンギヤＳ４を固締し得る様にな
つている。前記第４キヤリヤＣ４は前記第２リン
グギヤRG２、前記第３キヤリヤＣ３に駆動的に
連結されるとともに、前記出力軸に動力的に一体
に連結される。 A fourth brake B4 is provided between the fourth sun gear S4 and the case, and is configured to lock the fourth sun gear S4 when the brake is activated. The fourth carrier C4 is drivingly connected to the second ring gear RG2 and the third carrier C3, and is also dynamically connected integrally to the output shaft.

ここで本発明による変速装置の具体的な変速段
の数値を例示すれば、I4＝0.562であり、本発明
の変速装置の各変速段における各クラツチと各ブ
レーキの作動と各変速段の減速比の関係をまとめ
ると第７Ｂ図のようになる。そして、各変速段に
おける各プラネタリギヤセツトの各要素の回転数
と接線力をまとめると第７Ｃ図のようになる。 Here, to give an example of a specific gear position value of the transmission according to the present invention, I 4 =0.562, and the operation of each clutch and each brake in each gear of the transmission according to the present invention and the deceleration of each gear The relationship between the ratios is summarized as shown in Figure 7B. The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 7C.

次に、本発明装置の第８実施例を第８Ａ図にて
説明すると、本実施例は前記第２実施例と同様
に、前記第１実施例において前記第３プラネタリ
ギヤセツトＸ３と前記出力軸との間にシングルピ
ニオン式の第４プラネタリギヤセツトＸ４を介在
してなる構成であり、各要素との連結関係は以下
の如くである。前記第４リングギヤRG４は前記
第１リングギヤRG１、前記第２サンギヤＳ２に
駆動的に連結される。 Next, an eighth embodiment of the device of the present invention will be explained with reference to FIG. 8A. In this embodiment, similarly to the second embodiment, in the first embodiment, the third planetary gear set X3 and the output shaft are connected to each other. A single pinion type fourth planetary gear set X4 is interposed between the two, and the connection relationship with each element is as follows. The fourth ring gear RG4 is drivingly connected to the first ring gear RG1 and the second sun gear S2.

前記第４サンギヤＳ４と前記ケースとの間には
第４ブレーキＢ４が設けられ該ブレーキＢ４が作
動した時には、第４サンギヤＳ４を固締し得る様
になつている。 A fourth brake B4 is provided between the fourth sun gear S4 and the case, and when the brake B4 is activated, the fourth sun gear S4 can be fixed.

前記第４キヤリヤＣ４は、前記第２リングギヤ
RG２、前記第３キヤリヤＣ３に駆動的に連結さ
れるとともに、前記出力軸に一体に連結される。 The fourth carrier C4 is the second ring gear
RG2 is drivingly connected to the third carrier C3 and integrally connected to the output shaft.

ここで本発明による変速装置の具体的な変速段
の数値を例示すれば、I4＝0.280であり、本発明
の変速装置の各変速段における各クラツチと各ブ
レーキの作動と各変速段の減速比の関係をまとめ
ると第８Ｂ図のようになる。 Here, to give an example of a specific gear position value of the transmission according to the present invention, I 4 =0.280, and the operation of each clutch and each brake in each gear of the transmission according to the present invention and the deceleration of each gear The relationship between the ratios is summarized as shown in Figure 8B.

そして、各変速段における各プラネタリギヤセ
ツトの各要素の回転数と接線力をまとめると、第
８Ｃ図のようになる。 The rotational speed and tangential force of each element of each planetary gear set at each gear stage are summarized as shown in FIG. 8C.

次に、本発明装置の第９実施例を第９Ａ図にて
説明すると、本実施例は前記第２実施例と同様に
前記第１実施例において前記第３プラネタリギヤ
セツトＸ３と前記出力軸との間にシングルピニオ
ン式の第４プラネタリギヤセツトＸ４を介在して
なる構成であり、各要素との連結関係は以下の如
くである。 Next, a ninth embodiment of the device of the present invention will be explained with reference to FIG. 9A. Similar to the second embodiment, this embodiment is similar to the second embodiment in that the third planetary gear set X3 and the output shaft are connected to each other in the first embodiment. It has a configuration in which a single pinion type fourth planetary gear set X4 is interposed between them, and the connection relationship with each element is as follows.

前記第４サンギヤＳ４は、前記第１リングギヤ
RG１、前記第２サンギヤＳ２に駆動的に連結さ
れる。 The fourth sun gear S4 is the first ring gear
RG1 is drivingly connected to the second sun gear S2.

前記第４リングギヤRG４と前記ケースとの間
には第４ブレーキＢ４が設けられ、該ブレーキＢ
４が作動した時には前記第４リングギヤRG４を
固締し得る様になつている。 A fourth brake B4 is provided between the fourth ring gear RG4 and the case, and the fourth brake B4 is provided between the fourth ring gear RG4 and the case.
When the fourth ring gear RG4 is activated, the fourth ring gear RG4 can be fixed.

前記第４キヤリヤＣ４は、前記第２リングギヤ
RG２、前記第３キヤリヤＣ３に駆動的に連結さ
れるとともに前記出力軸に動力的に一体に連結さ
れる。 The fourth carrier C4 is the second ring gear
RG2 is drivingly connected to the third carrier C3 and is integrally and dynamically connected to the output shaft.

ここで本発明による変速装置の具体的な変速段
の数値を例示すれば、I4＝0.280であり、本発明
の変速装置の各変速段における各クラツチと各ブ
レーキの作動と各変速段の減速比の関係をまとめ
ると第９Ｂ図のようになる。 Here, to give an example of a specific gear position value of the transmission according to the present invention, I 4 =0.280, and the operation of each clutch and each brake in each gear of the transmission according to the present invention and the deceleration of each gear The relationship between the ratios is summarized as shown in Figure 9B.

そして各変速段における各プラネタリギヤセツ
トの各要素の回転数と接線力をまとめると第９Ｃ
図のようになる。 Summarizing the rotational speed and tangential force of each element of each planetary gear set at each gear stage, it is 9C.
It will look like the figure.

以上の説明から明らかな様に、本発明によれば
基本的に３組のプラネタリギヤセツトを用いて初
期の目的を達成でき、実用上優れてなる少なくと
も前進４段、後進１段の変速段を得ることができ
工業上多大な効果を発揮する。 As is clear from the above description, according to the present invention, the initial objective can be achieved basically by using three planetary gear sets, and at least four forward gears and one reverse gear, which are excellent in practical use, can be obtained. It has great industrial effects.

【図面の簡単な説明】[Brief explanation of the drawing]

第１Ａ図は本発明の変速装置の第１実施例を線
図的に示す中央縦断面概略図、第１Ｂ図は本発明
装置の第１実施例の各変速段における各クラツチ
及び各ブレーキの作動とその作動により得られる
減速比の関係を示す説明図、第１Ｃ図は本発明装
置の第１実施例におけるプラネタリギヤセツトの
各要素の回転数と接線力との関係を示す説明図。
第２Ａ図は本発明の変速装置の第２実施例を線図
的に示す中央縦断面概略図、第２Ｂ図は本発明装
置の第２実施例の各変速段における各クラツチ及
び各ブレーキの作動とその作動により得られる減
速比の関係を示す説明図、第２Ｃ図は本発明装置
の第２実施例におけるプラネタリギヤセツトの各
要素の回転数と接線力との関係を示す説明図。第
３Ａ図は本発明の変速装置の第３実施例を線図的
に示す中央縦断面概略図、第３Ｂ図は本発明装置
の第３実施例の各変速段における各クラツチ及び
各ブレーキの作動とその作動により得られる減速
比の関係を示す説明図、第３Ｃ図は本発明装置の
第３実施例におけるプラネタリギヤセツトの各要
素の回転数と接線力との関係を示す説明図。第４
Ａ図は本発明の変速装置の第４実施例を線図的に
示す中央縦断面概略図、第４Ｂ図は本発明装置の
第４実施例の各変速段における各クラツチ及び各
ブレーキの作動とその作動により得られる減速比
の関係を示す説明図、第４Ｃ図は本発明装置の第
４実施例におけるプラネタリギヤセツトの各要素
の回転数と接線力との関係を示す説明図。第５Ａ
図は本発明の変速装置の第５実施例を線図的に示
す中央縦断面概略図、第５Ｂ図は本発明装置の第
５実施例の各変速段における各クラツチ及び各ブ
レーキの作動とその作動により得られる減速比の
関係を示す説明図、第５Ｃ図は本発明装置の第５
実施例におけるプラネタリギヤセツトの各要素の
回転数と接線力との関係を示す説明図。第６Ａ図
は本発明の変速装置の第６実施例を線図的に示す
中央縦断図概略図、第６Ｂ図は本発明装置の第６
実施例の各変速段における各クラツチ及び各ブレ
ーキの作動とその作動により得られる減速比の関
係を示す説明図、第６Ｃ図は本発明装置の第６実
施例におけるプラネタリギヤセツトの各要素の回
転数と接線力との関係を示す説明図。第７Ａ図は
本発明の変速装置の第７実施例を線図的に示す中
央縦断面概略図、第７Ｂ図は本発明装置の第７実
施例の各変速段における各クラツチ及び各ブレー
キの作動とその作動により得られる減速比の関係
を示す説明図、第７Ｃ図は本発明装置の第７実施
例におけるプラネタリギヤセツトの各要素の回転
数と接線力との関係を示す説明図。第８Ａ図は本
発明の変速装置の第８実施例を線図的に示す中央
縦断概略図、第８Ｂ図は本発明装置の第８実施例
の各変速段における各クラツチ及び各ブレーキの
作動とその作動により得られる減速比の関係を示
す説明図、第８Ｃ図は本発明装置の第８実施例に
おけるプラネタリギヤセツトの各要素の回転数と
接線力との関係を示す説明図。第９Ａ図は本発明
の変速装置を第９実施例を線図的に示す中央縦断
面概略図、第９Ｂ図は本発明装置の第９実施例の
各変速段における各クラツチ及び各ブレーキの作
動とその作動により得られる減速比の関係を示す
説明図、第９Ｃ図は本発明装置の第９実施例にお
けるプラネタリギヤセツトの各要素の回転数と接
線力との関係を示す説明図である。 Ｘ１……第１プラネタリギヤセツト、Ｘ２……
第２プラネタリギヤセツト、Ｘ３……第３プラネ
タリギヤセツト、Ｘ４……第４プラネタリギヤセ
ツト、Ｓ１……第１サンギヤ、Ｓ２……第２サン
ギヤ、Ｓ３……第３サンギヤ、Ｓ４……第４サン
ギヤ、Ｐ１……第１プラネタリギヤ、Ｐ２……第
２プラネタリギヤ、Ｐ３……第３プラネタリギ
ヤ、Ｐ４……第４プラネタリギヤ、Ｐ５……第５
プラネタリギヤ、RG１……第１リングギヤ、RG
２……第２リングギヤ、RG３……第３リングギ
ヤ、RG4……第４リングギヤ、Ｃ１……第１キヤ
リヤ、Ｃ２……第２キヤリヤ、Ｃ３……第３キヤ
リヤ、Ｃ４……第４キヤリヤ、CL１……第１ク
ラツチ、CL２……第２クラツチ、CL３……第３
クラツチ、Ｂ１……第１ブレーキ、Ｂ２……第２
ブレーキ、Ｂ３……第３ブレーキ、Ｂ４……第４
ブレーキ。 FIG. 1A is a schematic central longitudinal cross-sectional view diagrammatically showing a first embodiment of the transmission device of the present invention, and FIG. 1B is the operation of each clutch and each brake at each gear stage of the first embodiment of the device of the present invention. FIG. 1C is an explanatory diagram showing the relationship between the rotational speed of each element of the planetary gear set and the tangential force in the first embodiment of the device of the present invention.
FIG. 2A is a schematic central vertical cross-sectional view diagrammatically showing a second embodiment of the transmission device of the present invention, and FIG. 2B is the operation of each clutch and each brake at each gear stage of the second embodiment of the device of the present invention. FIG. 2C is an explanatory diagram showing the relationship between the rotational speed of each element of the planetary gear set and the tangential force in the second embodiment of the device of the present invention. FIG. 3A is a schematic central vertical cross-sectional view diagrammatically showing a third embodiment of the transmission device of the present invention, and FIG. 3B is the operation of each clutch and each brake at each gear stage of the third embodiment of the device of the present invention. FIG. 3C is an explanatory diagram showing the relationship between the rotational speed of each element of the planetary gear set and the tangential force in the third embodiment of the device of the present invention. Fourth
Fig. A is a schematic central vertical cross-sectional view diagrammatically showing a fourth embodiment of the transmission device of the present invention, and Fig. 4B shows the operation of each clutch and each brake at each gear stage of the fourth embodiment of the device of the present invention. FIG. 4C is an explanatory diagram showing the relationship between the speed reduction ratio obtained by the operation, and FIG. 4C is an explanatory diagram showing the relationship between the rotational speed and tangential force of each element of the planetary gear set in the fourth embodiment of the device of the present invention. 5th A
FIG. 5B is a central vertical cross-sectional schematic view diagrammatically showing a fifth embodiment of the transmission device of the present invention, and FIG. FIG. 5C is an explanatory diagram showing the relationship between the reduction ratios obtained through operation.
FIG. 3 is an explanatory diagram showing the relationship between the rotation speed and tangential force of each element of the planetary gear set in the example. FIG. 6A is a schematic central longitudinal sectional view diagrammatically showing a sixth embodiment of the transmission device of the present invention, and FIG. 6B is a sixth embodiment of the transmission device of the present invention.
An explanatory diagram showing the relationship between the operation of each clutch and each brake at each gear stage of the embodiment and the reduction ratio obtained by the operation, and Fig. 6C shows the rotational speed of each element of the planetary gear set in the sixth embodiment of the device of the present invention. FIG. 3 is an explanatory diagram showing the relationship between and tangential force. FIG. 7A is a schematic central longitudinal cross-sectional view diagrammatically showing a seventh embodiment of the transmission device of the present invention, and FIG. 7B is the operation of each clutch and each brake at each gear stage of the seventh embodiment of the device of the present invention. FIG. 7C is an explanatory diagram showing the relationship between the rotational speed of each element of the planetary gear set and the tangential force in the seventh embodiment of the device of the present invention. FIG. 8A is a schematic central longitudinal sectional view diagrammatically showing an eighth embodiment of the transmission device of the present invention, and FIG. 8B is a diagram showing the operation of each clutch and each brake at each gear stage of the eighth embodiment of the device of the present invention. FIG. 8C is an explanatory diagram showing the relationship between the speed reduction ratio obtained by the operation, and FIG. 8C is an explanatory diagram showing the relationship between the rotation speed and tangential force of each element of the planetary gear set in the eighth embodiment of the device of the present invention. FIG. 9A is a schematic central vertical cross-sectional view diagrammatically showing a ninth embodiment of the transmission device of the present invention, and FIG. 9B is the operation of each clutch and each brake at each gear stage of the ninth embodiment of the device of the present invention. FIG. 9C is an explanatory diagram showing the relationship between the rotational speed of each element of the planetary gear set and the tangential force in the ninth embodiment of the device of the present invention. X1...1st planetary gear set, X2...
2nd planetary gear set, X3...3rd planetary gear set, X4...4th planetary gear set, S1...1st sun gear, S2...2nd sun gear, S3...3rd sun gear, S4...4th sun gear, P1 ...First planetary gear, P2...Second planetary gear, P3...Third planetary gear, P4...Fourth planetary gear, P5...Fifth
Planetary gear, RG1...1st ring gear, RG
2...Second ring gear, RG3...Third ring gear, RG4...Fourth ring gear, C1...First carrier, C2...Second carrier, C3...Third carrier, C4...Fourth carrier, CL1 ...First clutch, CL2...Second clutch, CL3...Third
Clutch, B1...1st brake, B2...2nd
Brake, B3...Third brake, B4...Fourth
brake.

Claims (1)

【特許請求の範囲】 １ 入力軸、出力軸、各々がサンギヤとリングギ
ヤ及び該両ギヤ間の噛合連動を継成するプラネタ
リギヤを枢支するキヤリヤから成る数組のプラネ
タリギヤセツト、固定部材であるケースを有し、
ダブルピニオン式の第１プラネタリギヤセツトの
リングギヤとシングルピニオン式の第２プラネタ
リギヤセツトのサンギヤとが駆動的に連結され、
シングルピニオン式の第３プラネタリギヤセツト
のリングギヤと第１及び第２プラネタリギヤセツ
トの両キヤリヤとが駆動的に連結され、第２プラ
ネタリギヤセツトのリングギヤと第３プラネタリ
ギヤセツトのキヤリヤとが出力軸に駆動的に連結
されており、第１プラネタリギヤセツトのリング
ギヤと第２プラネタリギヤセツトのサンギヤとが
連結されてなるものと第３プラネタリギヤセツト
のリングギヤと第１及び第２プラネタリギヤセツ
トの両キヤリヤとが連結されてなるものと第１プ
ラネタリギヤセツトのサンギヤの三者の内少くと
も何れか二つを夫々入力軸に対し結合又は解放さ
せる二つのクラツチ装置、第１プラネタリギヤセ
ツトのサンギヤをケースに固締し得るブレーキ、
第３プラネタリギヤセツトのリングギヤと第１及
び第２プラネタリギヤセツトの両キヤリヤとが連
結されてなるものをケースに固締し得る他のブレ
ーキ、第３プラネタリギヤセツトのサンギヤをケ
ースに固締し得るもう一つのブレーキを備えて成
る変速装置。 ２ 入力軸、出力軸、各々がサンギヤとリングギ
ヤ及び該両ギヤ間の噛合連動を継成するプラネタ
リギヤを枢支するキヤリヤから成る数組のプラネ
タリギヤセツト、固定部材であるケースを有し、
ダブルピニオン式の第１プラネタリギヤセツトの
リングギヤとシングルピニオン式の第２プラネタ
リギヤセツトのサンギヤとが駆動的に連結され、
シングルピニオン式の第３プラネタリギヤセツト
のリングギヤと第１及び第２プラネタリギヤセツ
トの両キヤリヤとが駆動的に連結され、第２プラ
ネタリギヤセツトのリングギヤと第３プラネタリ
ギヤセツトのキヤリヤとが出力軸に駆動的に連結
されており、第１プラネタリギヤセツトのリング
ギヤと第２プラネタリギヤセツトのサンギヤとが
連結されてなるものと第３プラネタリギヤセツト
のリングギヤと第１及び第２プラネタリギヤセツ
トの両キヤリヤとが連結されてなるものと第１プ
ラネタリギヤセツトのサンギヤの三者の内少くと
も何れか二つを夫々入力軸に対し結合又は解放さ
せる二つのクラツチ装置、第１プラネタリギヤセ
ツトのサンギヤをケースに固締し得るブレーキ、
第３プラネタリギヤセツトのリングギヤと第１及
び第２プラネタリギヤセツトの両キヤリヤとが連
結されてなるものをケースに固締し得る他のブレ
ーキ、第３プラネタリギヤセツトのサンギヤをケ
ースに固締し得るもう一つのブレーキを備えると
ともに、第４プラネタリギヤセツトのサンギヤ、
リングギヤ、キヤリヤの内の任意の２つの何れか
一方が前記第３プラネタリギヤセツトのサンギヤ
に駆動的に連結され他方が前記出力軸に駆動的に
連結されており、第４プラネタリギヤセツトのサ
ンギヤ、リングギヤ、キヤリヤの内の残りの部材
を前記ケースに固締し得る別のブレーキを備えて
成る変速装置。 ３ 入力軸、出力軸、各々がサンギヤとリングギ
ヤ及び該両ギヤ間の噛合連動を継成するプラネタ
リギヤを枢支するキヤリヤから成る数組のプラネ
タリギヤセツト、固定部材であるケースを有し、
ダブルピニオン式の第１プラネタリギヤセツトの
リングギヤとシングルピニオン式の第２プラネタ
リギヤセツトのサンギヤとが駆動的に連結され、
シングルピニオン式の第３プラネタリギヤセツト
のリングギヤと第１及び第２プラネタリギヤセツ
トの両キヤリヤとが駆動的に連結され、第２プラ
ネタリギヤセツトのリングギヤと第３プラネタリ
ギヤセツトのキヤリヤとが出力軸に駆動的に連結
されており、第１プラネタリギヤセツトのリング
ギヤと第２プラネタリギヤセツトのサンギヤとが
連結されてなるものと第３プラネタリギヤセツト
のリングギヤと第１及び第２プラネタリギヤセツ
トの両キヤリヤとが連結されてなるものと第１プ
ラネタリギヤセツトのサンギヤの三者の内少くと
も何れか二つを夫々入力軸に対し結合又は解放さ
せる二つのクラツチ装置、第１プラネタリギヤセ
ツトのサンギヤをケースに固締し得るブレーキ、
第３プラネタリギヤセツトのリングギヤと第１及
び第２プラネタリギヤセツトの両キヤリヤとが連
結されてなるものをケースに固締し得る他のブレ
ーキ、第３プラネタリギヤセツトのサンギヤをケ
ースに固締し得るもう一つのブレーキを備えると
ともに、第４プラネタリギヤセツトのサンギヤ、
リングギヤ、キヤリヤの内の任意の２つの何れか
一方が前記第１プラネタリギヤセツトのリングギ
ヤと前記第２プラネタリギヤセツトのサンギヤと
に駆動的に連結され他方が前記出力軸に駆動的に
連結されており、第４プラネタリギヤセツトのサ
ンギヤ、リングギヤ、キヤリヤの内の残りの部材
を前記ケースに固締し得る別のブレーキを備えて
成る変速装置。[Claims] 1. An input shaft, an output shaft, several planetary gear sets each consisting of a sun gear, a ring gear, and a carrier that pivotally supports a planetary gear that connects the two gears, and a case that is a fixed member. death,
The ring gear of the double pinion type first planetary gear set and the sun gear of the single pinion type second planetary gear set are drivingly connected,
The ring gear of the single pinion type third planetary gear set and both carriers of the first and second planetary gear sets are drivingly connected, and the ring gear of the second planetary gear set and the carrier of the third planetary gear set are drivingly connected to the output shaft. The ring gear of the first planetary gear set and the sun gear of the second planetary gear set are connected, and the ring gear of the third planetary gear set and both carriers of the first and second planetary gear sets are connected. and two clutch devices for respectively coupling or releasing at least two of the three sun gears of the first planetary gear set with respect to the input shaft, and a brake capable of fixing the sun gear of the first planetary gear set to the case.
Another brake capable of securing the ring gear of the third planetary gear set and the carriers of the first and second planetary gear sets connected to the case, and another brake capable of securing the sun gear of the third planetary gear set to the case. A transmission consisting of two brakes. 2. An input shaft, an output shaft, several planetary gear sets each consisting of a sun gear, a ring gear, and a carrier that pivotally supports a planetary gear that connects the two gears, and a case that is a fixed member;
The ring gear of the double pinion type first planetary gear set and the sun gear of the single pinion type second planetary gear set are drivingly connected,
The ring gear of the single pinion type third planetary gear set and both carriers of the first and second planetary gear sets are drivingly connected, and the ring gear of the second planetary gear set and the carrier of the third planetary gear set are drivingly connected to the output shaft. The ring gear of the first planetary gear set and the sun gear of the second planetary gear set are connected, and the ring gear of the third planetary gear set and both carriers of the first and second planetary gear sets are connected. and two clutch devices for respectively coupling or releasing at least two of the three sun gears of the first planetary gear set with respect to the input shaft, and a brake capable of fixing the sun gear of the first planetary gear set to the case.
Another brake capable of securing the ring gear of the third planetary gear set and the carriers of the first and second planetary gear sets connected to the case, and another brake capable of securing the sun gear of the third planetary gear set to the case. In addition to being equipped with two brakes, the sun gear of the fourth planetary gear set,
Any two of the ring gear and the carrier are drivingly connected to the sun gear of the third planetary gear set, and the other is drivingly connected to the output shaft, and the sun gear and the ring gear of the fourth planetary gear set, A transmission comprising a further brake capable of securing the remaining parts of the carrier to said case. 3. An input shaft, an output shaft, several planetary gear sets each consisting of a sun gear, a ring gear, and a carrier that pivotally supports a planetary gear that connects the two gears, and a case that is a fixed member;
The ring gear of the double pinion type first planetary gear set and the sun gear of the single pinion type second planetary gear set are drivingly connected,
The ring gear of the single pinion type third planetary gear set and both carriers of the first and second planetary gear sets are drivingly connected, and the ring gear of the second planetary gear set and the carrier of the third planetary gear set are drivingly connected to the output shaft. The ring gear of the first planetary gear set and the sun gear of the second planetary gear set are connected, and the ring gear of the third planetary gear set and both carriers of the first and second planetary gear sets are connected. and two clutch devices for respectively coupling or releasing at least two of the three sun gears of the first planetary gear set with respect to the input shaft, and a brake capable of fixing the sun gear of the first planetary gear set to the case.
Another brake capable of securing the ring gear of the third planetary gear set and the carriers of the first and second planetary gear sets connected to the case, and another brake capable of securing the sun gear of the third planetary gear set to the case. In addition to being equipped with two brakes, the sun gear of the fourth planetary gear set,
One of the ring gear and the carrier is drivingly connected to the ring gear of the first planetary gear set and the sun gear of the second planetary gear set, and the other is drivingly connected to the output shaft, A transmission comprising another brake capable of securing the remaining members of the sun gear, ring gear, and carrier of the fourth planetary gear set to the case.
JP56144135A 1981-09-11 1981-09-11 Speed change gear Granted JPS57134049A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP56144135A JPS57134049A (en) 1981-09-11 1981-09-11 Speed change gear

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP56144135A JPS57134049A (en) 1981-09-11 1981-09-11 Speed change gear

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
JP10916373A Division JPS5738827B2 (en) 1973-09-27 1973-09-27

Publications (2)

Publication Number Publication Date
JPS57134049A JPS57134049A (en) 1982-08-19
JPS622175B2 true JPS622175B2 (en) 1987-01-19

Family

ID=15355027

Family Applications (1)

Application Number Title Priority Date Filing Date
JP56144135A Granted JPS57134049A (en) 1981-09-11 1981-09-11 Speed change gear

Country Status (1)

Country Link
JP (1) JPS57134049A (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63195452A (en) * 1987-02-10 1988-08-12 Mitsubishi Heavy Ind Ltd Transmission
US5378208A (en) * 1993-06-07 1995-01-03 General Motors Corporation Reversing assembly for multi-speed transmission
US6422969B1 (en) * 2000-08-14 2002-07-23 General Motors Corporation Powertrain with a six speed planetary transmission having three planetary gear sets
US6743139B1 (en) * 2002-11-26 2004-06-01 General Motors Corporation Multi-speed dual-clutch planetary transmissions having output shaft interconnected with three gear members

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5059661A (en) * 1973-09-27 1975-05-23
JPS5738827A (en) * 1980-08-18 1982-03-03 Sumitomo Chem Co Ltd Painting of molding comprising polyolefin composition

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5059661A (en) * 1973-09-27 1975-05-23
JPS5738827A (en) * 1980-08-18 1982-03-03 Sumitomo Chem Co Ltd Painting of molding comprising polyolefin composition

Also Published As

Publication number Publication date
JPS57134049A (en) 1982-08-19

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