JPH0656196B2 - Vehicle drive - Google Patents
Vehicle driveInfo
- Publication number
- JPH0656196B2 JPH0656196B2 JP59248812A JP24881284A JPH0656196B2 JP H0656196 B2 JPH0656196 B2 JP H0656196B2 JP 59248812 A JP59248812 A JP 59248812A JP 24881284 A JP24881284 A JP 24881284A JP H0656196 B2 JPH0656196 B2 JP H0656196B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- reduction
- shaft
- reverse
- differential
- 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 - Fee Related
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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement Of Transmissions (AREA)
- Retarders (AREA)
- Structure Of Transmissions (AREA)
Description
【発明の詳細な説明】 （産業上の利用分野） 本発明は、常時噛合式変速機と差動装置とを備え、前後
進切換え可能とした車輛の駆動装置に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle drive device that includes a constant mesh transmission and a differential device and is capable of switching between forward and backward movements.
（発明の背景） 小型の車輛において、エンジンの回転出力を、常時噛合
式変速機および差動装置を介して左右一対の駆動輪に伝
達することが考えられている。ここに特に小型の車輛で
前後進切換可能とする場合には、変速機、差動装置およ
び前後進切換装置を小型化することが求められる。(Background of the Invention) In a small vehicle, it is considered to transmit the rotation output of an engine to a pair of left and right drive wheels via a constant mesh type transmission and a differential device. Here, in order to enable forward / reverse switching in a particularly small vehicle, it is required to downsize the transmission, the differential device and the forward / reverse switching device.
（発明の目的） 本発明はこのような事情に鑑みなされたものであり、常
時噛合式変速機と差動装置と前後進切換装置とを有機的
に組み合わせて小型化を可能にした車輛の駆動装置を提
供することを目的とするものである。(Object of the Invention) The present invention has been made in view of the above circumstances, and is a drive for a vehicle that can be miniaturized by organically combining a constant mesh transmission, a differential device, and a forward / reverse switching device. The purpose is to provide a device.
（発明の構成） 本発明によればこの目的は、エンジンの回転出力を、常
時噛合式変速機および差動装置を介して左右一対の駆動
輪へ伝達する車輛の駆動装置において、前記差動装置の
差動歯車箱の固設された互いに歯数が異なる一対の減速
大歯車と、これら各減速大歯車に噛合し減速歯車軸に遊
転自在に保持される一対の減速小歯車と、前記減速歯車
軸上で軸方向に摺動し前進状態で前記減速小歯車のいず
れかに選択的に係合するスライダと、前記減速歯車軸に
並設され前記エンジンの回転出力を前記減速歯車軸に伝
達する入力軸と、前記減速小歯車の一方の前記スライダ
側の面に設けられた後進用大歯車と、後進状態で前記入
力軸の回転を前記後進用大歯車に伝達する後進用アイド
ル歯車とを備え、後進状態ではこの入力軸の回転を後進
用アイドル歯車を介していずれか１つの減速小歯車に伝
えるようにしたことを特徴とする車輛の駆動装置により
達成される。(Structure of the Invention) According to the present invention, an object of the present invention is to provide a vehicle drive device for transmitting a rotational output of an engine to a pair of left and right drive wheels via a constant mesh type transmission and a differential device. , A pair of fixed reduction gears having different numbers of teeth, and a pair of reduction gears meshed with these reduction gears and rotatably held on the reduction gear shaft. A slider that slides axially on the gear shaft and selectively engages with one of the reduction gears in a forward state, and a rotation output of the engine that is installed in parallel with the reduction gear shaft and is transmitted to the reduction gear shaft. An input shaft, a large reverse gear provided on the one slider side surface of the reduction gear, and a reverse idle gear that transmits the rotation of the input shaft to the large reverse gear in a reverse state. Equipped with the rotation of this input shaft for reverse when in reverse The present invention is achieved by a drive device for a vehicle characterized in that transmission is made to any one of the reduction gears through an idle gear.
（実施例） 以下図面に基づき、本発明を詳細に説明する。(Example) The present invention will be described in detail below with reference to the drawings.
第１図は本発明の一実施例の側面図、第２図はその動力
装置の側面図、第３図は平面図、第４図はそのIV−IV線
断面図、第５図は動力伝達系路を示す展開図である。FIG. 1 is a side view of an embodiment of the present invention, FIG. 2 is a side view of the power unit, FIG. 3 is a plan view, FIG. 4 is a sectional view taken along the line IV-IV, and FIG. 5 is power transmission. It is a development view showing a path.
第１図で符号１０は左右一対の操向前輪（一方のみ図
示）、１２は操向ハンドル、１４は運転シート、１６は
ボデーである。１８（１８ａ，１８ｂ）はボデー１６の
下側部を前後方向に通るサイドメンバ、２０は両サイド
メンバ１８をつなぐクロスメンバであり、これらの各メ
ンバ１８，２０および他の部材（図示せず）によりフレ
ーム２２が構成される。なおサイドメンバ１８は、シー
ト１４の後方が斜め上後方に立上つている。In FIG. 1, reference numeral 10 is a pair of left and right steering front wheels (only one is shown), 12 is a steering wheel, 14 is a driving seat, and 16 is a body. Reference numeral 18 (18a, 18b) is a side member that passes through the lower side of the body 16 in the front-rear direction, and 20 is a cross member that connects both side members 18, and these members 18, 20 and other members (not shown). The frame 22 is constituted by The rear side of the seat 14 of the side member 18 rises obliquely upward and rearward.
２４は後車軸管であり、左右一対の前後方向にのびる揺
動アーム２６（２６ａ，２６ｂ）により、クロスメンバ
２０に連結され、上下動可能となっている。なお２８は
パナールロッドであり、その一端は後車軸管２４の左端
部に、他端はサイドメンバ１８から垂下され左右方向に
高剛性を持つ腕３０に連結されている。このパナールロ
ッド２８は後車軸管２４の左右への移動を規制する作用
を持つ。３２（３２ａ，３２ｂ）は左右一対の緩衝ユニ
ットで、その下端は後車軸管２４の左右端部に、その上
端はサイドメンバ１８の後端部にそれぞれ連結されてい
る。A rear axle tube 24 is connected to the cross member 20 by a pair of left and right swing arms 26 (26a, 26b) extending in the front-rear direction and is vertically movable. Reference numeral 28 denotes a Panhard rod, one end of which is connected to the left end of the rear axle tube 24, and the other end of which is connected to an arm 30 which is hung from the side member 18 and has high rigidity in the left-right direction. The Panhard rod 28 has a function of restricting the movement of the rear axle tube 24 to the left and right. Reference numeral 32 (32a, 32b) denotes a pair of left and right cushioning units, the lower end of which is connected to the left and right ends of the rear axle tube 24 and the upper end of which is connected to the rear end of the side member 18, respectively.
後車軸管２４の中央付近にはデフケース３４が一体に結
合されている。このデフケース３４の下部には公知のは
ねかけ潤滑式の差動装置３６が収納されている。この差
動装置３６は、左右側面に互いに歯数が異なる減速大歯
車３８（３８ａ，３８ｂ）が一体に成形された差動歯車
箱４０、この歯車箱４０内に固定された支持軸４２、こ
の支持軸４２に回転自在に保持された差動小歯車４４、
この差動小歯車４４に左右から噛合する一対の差動大歯
車４６（４６ａ，４６ｂ）を備える（第５図）。後車軸
管２４内には左右一対の後輪軸４８（４８ａ，４８ｂ）
が挿通され、これらの内端は差動大歯車４６に結合さ
れ、外端は後車軸管２４から左右に突出してこの突出端
に駆動輪である後輪５０（５０ａ，５０ｂ）が固定され
ている。A differential case 34 is integrally connected near the center of the rear axle tube 24. A known splash-lubricating differential device 36 is housed in the lower portion of the differential case 34. The differential device 36 includes a differential gear box 40 integrally formed with reduction gears 38 (38a, 38b) having different numbers of teeth on the left and right sides, a support shaft 42 fixed in the gear box 40, A differential small gear 44 rotatably held on the support shaft 42,
A pair of large differential gears 46 (46a, 46b) that mesh with the small differential gear 44 from the left and right are provided (FIG. 5). A pair of left and right rear wheel shafts 48 (48a, 48b) are provided in the rear axle tube 24.
, The inner ends of which are coupled to the large differential gear 46, and the outer ends of the rear axle tube 24 project to the left and right, and the rear wheels 50 (50a, 50b) that are drive wheels are fixed to the projecting ends. There is.
前記デフケース３４は第４図に示すように縦長に作ら
れ、その内部には変速歯車軸５２、入力軸５４が直線Ａ
（第４図）上に載るように上方へ順次並設されている。
入力軸５４には、後記エンジン１００の回転がＶベルト
式無段変速機５６および遠心クラッチ５８を介して伝え
られる。入力軸５４の回転は歯車６０，６２を介して変
速歯車軸５２に伝えられる。この変速歯車軸５２には前
記減速大歯車３８ａ，３８ｂに噛合する減速小歯車６４
（６４ａ，６４ｂ）が遊転自在に保持され、これら両減
速小歯車６４ａ，６４ｂ間にはスライダ６６が軸方向に
摺動自在に取付けられている。なおスライダ６６と変速
歯車軸５２の軸方向の溝に装着されたボール６８（第５
図）は、スライダ６６の摺動を円滑にする作用を持つ。
このスライダ６６の左右両端と減速小歯車６４ａ，６４
ｂとは、それぞれ噛合いクラッチを形成する。スライダ
６６を摺動させることにより一方の噛合いクラッチが選
択的に係合して、変速歯車軸５２の回転はスライダ６
６、減速小歯車６４ａまたは６４ｂに伝えられる。すな
わち公知の常時噛合式２段変速機７０が形成される。な
お一方の減速小歯車６４ａには噛合いクラッチの爪と一
体に後進用の歯車１１８が形成されている。As shown in FIG. 4, the differential case 34 is made vertically long, and the transmission gear shaft 52 and the input shaft 54 have a straight line A therein.
(FIG. 4) They are arranged side by side upward so as to be placed on top.
The rotation of the engine 100 described later is transmitted to the input shaft 54 via a V-belt type continuously variable transmission 56 and a centrifugal clutch 58. The rotation of the input shaft 54 is transmitted to the speed change gear shaft 52 via the gears 60 and 62. The transmission gear shaft 52 has a reduction gear 64 that meshes with the reduction gears 38a and 38b.
(64a, 64b) are rotatably held, and a slider 66 is axially slidably mounted between the two reduction gears 64a, 64b. The slider 68 and the ball 68 (fifth portion of the ball mounted on the axial groove of the speed change gear shaft 52).
The drawing) has the function of smoothing the sliding of the slider 66.
The left and right ends of the slider 66 and the reduction gears 64a, 64
b and a mesh clutch, respectively. By sliding the slider 66, one of the dog clutches is selectively engaged, so that the rotation of the transmission gear shaft 52 is prevented from rotating.
6. The reduction gear is transmitted to the small gear 64a or 64b. That is, the known constant mesh type two-stage transmission 70 is formed. It should be noted that a gear 118 for backward movement is formed integrally with the pawl of the dog clutch on one of the reduction gears 64a.
前記直線Ａの前方、すなわち変速歯車軸５２および入力
軸５４の車軸前進方向側には、後進用アイドル歯車７２
を遊転可能に支持する支軸７４，シフタ７６（７６ａ，
７６ｂ）を摺動自在に支持するシフタ軸７８、変速ドラ
ム８０が後輪軸４８と平行に配設されている。変速ドラ
ム８０の一端はデフケース３４から突出しここにワイヤ
ドラム８２が固定されている（第５図）。このワイヤド
ラム８２にはワイヤ８４が巻付けられ、このワイヤ８４
の両端はコイルばね８６（一方のみ図示）を介してそれ
ぞれ他のワイヤ８８（一方のみ図示）に接続されてい
る。他のワイヤ８８は運転席に設けた操作レバー（図示
せず）に接続され、この操作レバーの操作によりワイヤ
８８，８４の一方が引かれ他方が緩められてドラム８
２，８０が強制的に回動される。なおワイヤ８４の途中
はワイヤドラム８２に係止されている。また第５図で９
０はワイヤドラム８２に固定されたカム板、９２はこの
カム板９０に弾接するカムフォロワであり、これらカム
板９０、カムフォロワ９２により変速ドラム８０は前進
第１，２速、中立および後進位置に保持される。The reverse idle gear 72 is provided in front of the straight line A, that is, in the forward direction of the axle of the speed change gear shaft 52 and the input shaft 54.
Support shaft 74 and shifter 76 (76a,
A shifter shaft 78 and a transmission drum 80, which slidably support 76b), are arranged in parallel with the rear wheel shaft 48. One end of the transmission drum 80 projects from the differential case 34, and the wire drum 82 is fixed thereto (FIG. 5). A wire 84 is wound around the wire drum 82.
Both ends of each are connected to other wires 88 (only one shown) via coil springs 86 (only one shown). The other wire 88 is connected to an operating lever (not shown) provided in the driver's seat, and one of the wires 88 and 84 is pulled and the other is loosened by the operation of this operating lever to loosen the drum 8
2, 80 are forcibly rotated. The wire 84 is locked in the wire drum 82 in the middle thereof. Also, in FIG.
Reference numeral 0 is a cam plate fixed to the wire drum 82, and 92 is a cam follower elastically contacting the cam plate 90. To be done.
第１，２，３図において、９４はトルクアームであり、
略Ｕ字状のパイプの両端に固着されたブラケット板９６
（９６ａ，９６ｂ）がデフケース３４に一体的に固定さ
れ、Ｕ字状パイプの部分が前方にのびている。このトル
クアーム９４の前端はゴムダンパ９８からなる自在継手
により、前記クロスメンバ２０の中央付近に連結されて
いる（第２，３図）。このトルクアーム９４は発進・制
動に伴って後車軸管２４に加わる後輪５０の回転反力を
受ける作用を持つ。In FIGS. 1, 2, and 3, 94 is a torque arm,
Bracket plates 96 fixed to both ends of a substantially U-shaped pipe
(96a, 96b) are integrally fixed to the differential case 34, and a U-shaped pipe portion extends forward. The front end of the torque arm 94 is connected to the vicinity of the center of the cross member 20 by a universal joint made of a rubber damper 98 (Figs. 2 and 3). The torque arm 94 has a function of receiving a rotational reaction force of the rear wheel 50 applied to the rear axle tube 24 as the vehicle starts and brakes.
１００はほぼ垂直なシリンダを有する直立型エンジンで
あり、トルクアーム９４上にゴムダンパ１０２，１０４
を介して搭載されている。このエンジン１００のクラン
ク軸１０６の回転は減速歯車１０８，１１０（第５図）
を介して、前記Ｖベルト式無段変速機５６の駆動プーリ
５６ａに伝えられる。この駆動プーリ５６ａの間隔は、
ボール１１２に働く遠心力の増加につれて減少し、これ
に伴って前記入力軸５４に設けられた従動プーリ５６ａ
の間隔が増大して変速が行われる。なお１１４はエンジ
ン１００の前側に接続された気化器である。Reference numeral 100 is an upright type engine having a substantially vertical cylinder, and rubber dampers 102, 104 are mounted on a torque arm 94.
Is installed through. The rotation of the crankshaft 106 of the engine 100 is caused by the reduction gears 108 and 110 (Fig. 5).
Via the drive pulley 56a of the V-belt type continuously variable transmission 56. The distance between the drive pulleys 56a is
The centrifugal force acting on the ball 112 decreases as the centrifugal force increases, and accordingly, a driven pulley 56a provided on the input shaft 54.
The interval is increased and gear shifting is performed. Reference numeral 114 is a carburetor connected to the front side of the engine 100.
この実施例において操作レバーの中立位置ではスライダ
６６は両減速小歯車６４に係合せず、アイドル歯車７２
は第５図の実線位置にくる。このため入力軸５４、変速
歯車軸５２は空転する。操作レバーの前進１速（第２
速）位置では、変速ドラム８０によってシフタ７６ｂは
スライダ６６を右側（左側）へ送られ減速小歯車６４ｂ
（６４ａ）に係合される。このため入力軸５４の回転
は、変速歯車軸５２、スライダ６６、減速小歯車６４ｂ
（６４ａ）、減速大歯車３８ｂ（３８ａ）、差動装置３
６を介して後輪軸４８に伝えられる。In this embodiment, in the neutral position of the operating lever, the slider 66 does not engage with both the reduction gears 64 and the idle gear 72
Comes to the position indicated by the solid line in FIG. Therefore, the input shaft 54 and the speed change gear shaft 52 run idle. Forward 1st speed of operation lever (2nd
In the (speed) position, the shift drum 80 causes the shifter 76b to move the slider 66 to the right (left side) and the reduction gear 64b.
(64a) is engaged. Therefore, the rotation of the input shaft 54 is caused by the speed change gear shaft 52, the slider 66, and the reduction small gear 64b.
(64a), reduction gear 38b (38a), differential device 3
It is transmitted to the rear wheel shaft 48 via 6.
操作レバーの後進位置では、スライダ６６は第５図の中
立位置に戻ると共に、アイドル歯車７２は仮想線位置に
移動し、入力軸５４の回転は歯車１１６、アイドル歯車
７２、減速小歯車６４ａと一体の歯車１１８に伝えら
れ、減速大歯車３８ａ、後輪軸４８を後進方向に回転さ
せる。In the reverse position of the operation lever, the slider 66 returns to the neutral position in FIG. 5, the idle gear 72 moves to the imaginary line position, and the rotation of the input shaft 54 is integrated with the gear 116, the idle gear 72, and the reduction gear 64a. Is transmitted to the gear 118 of the gear, and rotates the large reduction gear 38a and the rear wheel shaft 48 in the reverse direction.
以上のように減速歯車軸５２には入力軸５４の回転が歯
車６０，６２により減速されて常時伝えられ、この減速
歯車軸５２は常に一定方向に回転される。そして前進時
にはスライダ６６の移動により減速小歯車６４ａ，６４
ｂの一方が選択的に減速歯車軸５２に固定されて、この
減速歯車軸５２の回転が差動装置３６に伝えられる。ま
た後進時には入力軸５４の回転は後進用アイドル歯車７
２を介して一方の減速小歯車６４ａに伝えられる。また
減速大歯車３８ａ、３８ｂは差動歯車箱に固定し、この
差動歯車箱に隣接する減速歯車軸にスライダ６６および
減速小歯車６４ａ、６４ｂを設けているから、通常の主
軸と副軸を持った常時噛合式減速機のように差動装置か
ら独立した副軸が不要になる。すなわち従来装置におけ
る副軸を本発明では差動歯車箱で兼用していることにな
る。このため小型化が図れることになる。As described above, the rotation of the input shaft 54 is decelerated by the gears 60 and 62 and continuously transmitted to the reduction gear shaft 52, and the reduction gear shaft 52 is always rotated in a fixed direction. When moving forward, the reduction gears 64a, 64a are moved by the movement of the slider 66.
One of b is selectively fixed to the reduction gear shaft 52, and the rotation of the reduction gear shaft 52 is transmitted to the differential device 36. When the vehicle is moving backward, the input shaft 54 rotates in the backward idle gear 7
2 is transmitted to one of the reduction gears 64a. Further, the large reduction gears 38a, 38b are fixed to a differential gear box, and the slider 66 and the small reduction gears 64a, 64b are provided on the reduction gear shaft adjacent to the differential gear box. It eliminates the need for an auxiliary shaft that is independent of the differential device, such as the constant mesh reducer. That is, in the present invention, the counter shaft in the conventional device is also used as the differential gear box. Therefore, the size can be reduced.
なお本実施例では減速小歯車６４ａ，６４ｂと減速歯車
軸５２との固定を、スライダ６６と共に構成される噛合
いクラッチで行うので、一方の減速小歯車６４ａに設け
られる噛合いクラッチの爪と一体に後進用の歯車１１８
を形成した。このため差動装置３６と変速機７０との間
の空間を有効に利用して後進用の歯車１１８を大径にで
き、後進時の減速比を大きくすることができる。また変
速機７０の幅も拡大することがない。In the present embodiment, the reduction gears 64a and 64b and the reduction gear shaft 52 are fixed by the meshing clutch configured together with the slider 66, so that they are integrated with the claws of the meshing clutch provided on one of the reduction gears 64a. Reverse gear 118
Was formed. Therefore, the space between the differential device 36 and the transmission 70 can be effectively used to increase the diameter of the reverse gear 118 and increase the reduction ratio during reverse. Further, the width of the transmission 70 does not increase.
（発明の効果） 本発明は以上のように、入力軸の回転を減速歯車軸に伝
え、前進時にはこの減速歯車軸の回転を選択的に減速小
歯車に伝えさらに差動歯車箱に伝える一方、後進時には
入力軸の回転を後進用アイドル歯車を介して１つの減速
小歯車に伝える。従って１つの減速小歯車は前進時と後
進時とで共用されることになり、変速機の幅を拡大する
ことなく前後進切換装置を有機的に組込むことが可能に
なる。また本発明は、通常の主軸と副軸とを有する常時
噛合式変速機における副軸を差動歯車箱で兼用したもの
と考えることができ、独立した副軸が不用になる。さら
に後進用大歯車は一方の減速小歯車のスライダ側の面に
設けているから、変速機の幅は十分に狭くすることがで
きる。従って駆動装置の小型化が図れる。(Effect of the invention) As described above, the present invention transmits the rotation of the input shaft to the reduction gear shaft, selectively transmits the rotation of the reduction gear shaft to the reduction gear and further to the differential gear box during forward movement, During reverse travel, the rotation of the input shaft is transmitted to one reduction gear through the reverse idle gear. Therefore, one deceleration small gear is commonly used during forward movement and during reverse movement, and the forward / reverse switching device can be organically incorporated without expanding the width of the transmission. Further, the present invention can be considered that the auxiliary shaft in the constant mesh type transmission having the normal main shaft and the auxiliary shaft is also used as the differential gear box, and the independent auxiliary shaft becomes unnecessary. Further, since the large reverse gear is provided on the slider-side surface of one of the small reduction gears, the width of the transmission can be made sufficiently narrow. Therefore, the drive device can be downsized.
第１図は本発明の一実施例の側面図、第２図はその動力
装置の側面図、第３図は平面図、第４図はそのIV−IV線
断面図、第５図は動力伝達系路を示す展開図である。 ３６……差動装置、３８……減速大歯車、 ４０……差動歯車箱、５２……変速歯車軸、 ５４……入力軸、６４……減速小歯車、 ７０……変速機、 ７２……後進用アイドル歯車、 １００……エンジン。FIG. 1 is a side view of an embodiment of the present invention, FIG. 2 is a side view of the power unit, FIG. 3 is a plan view, FIG. 4 is a sectional view taken along the line IV-IV, and FIG. 5 is power transmission. It is a development view showing a path. 36 ... Differential gear, 38 ... Large reduction gear, 40 ... Differential gear box, 52 ... Transmission gear shaft, 54 ... Input shaft, 64 ... Reduction gear, 70 ... Transmission, 72 ... … Idle gears for reverse, 100 …… Engine.
Claims (1)
および差動装置を介して左右一対の駆動輪へ伝達する車
輛の駆動装置において、 前記差動装置の差動歯車箱の固設された互いに歯数が異
なる一対の減速大歯車と、これら各減速大歯車に噛合し
減速歯車軸に遊転自在に保持される一対の減速小歯車
と、前記減速歯車軸上で軸方向に摺動し前進状態で前記
減速小歯車のいずれかに選択的に係合するスライダと、
前記減速歯車軸に並設され前記エンジンの回転出力を前
記減速歯車軸に伝達する入力軸と、前記減速小歯車の一
方の前記スライダ側の面に設けられた後進用大歯車と、
後進状態で前記入力軸の回転を前記後進用大歯車に伝達
する後進用アイドル歯車とを備え、後進状態ではこの入
力軸の回転を後進用アイドル歯車を介していずれか１つ
の減速小歯車に伝えるようにしたことを特徴とする車輛
の駆動装置。Claim: What is claimed is: 1. A vehicle drive device for transmitting rotational output of an engine to a pair of left and right drive wheels via a constant mesh transmission and a differential device, wherein a differential gear box of the differential device is fixedly installed. A pair of reduction gears having different numbers of teeth, a pair of reduction gears meshing with the reduction gears and rotatably held on the reduction gear shaft, and axially sliding on the reduction gear shaft. And a slider that selectively engages with one of the reduction gears in the forward movement state,
An input shaft that is provided in parallel with the reduction gear shaft and transmits the rotational output of the engine to the reduction gear shaft, and a reverse large gear that is provided on the one slider side surface of the reduction small gear,
And a reverse idle gear that transmits the rotation of the input shaft to the reverse large gear in the reverse state, and transmits the rotation of the input shaft to any one reduction gear through the reverse idle gear in the reverse state. The vehicle drive device characterized by the above.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59248812A JPH0656196B2 (en) | 1984-11-27 | 1984-11-27 | Vehicle drive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59248812A JPH0656196B2 (en) | 1984-11-27 | 1984-11-27 | Vehicle drive |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1767484A Division JPS60163727A (en) | 1984-02-04 | 1984-02-04 | Driving gears for car |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60164049A JPS60164049A (en) | 1985-08-27 |
| JPH0656196B2 true JPH0656196B2 (en) | 1994-07-27 |
Family
ID=17183770
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59248812A Expired - Fee Related JPH0656196B2 (en) | 1984-11-27 | 1984-11-27 | Vehicle drive |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0656196B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001322442A (en) * | 2000-05-12 | 2001-11-20 | Honda Motor Co Ltd | Power transmission device for small-sized vehicle |
| JP2007145259A (en) * | 2005-11-30 | 2007-06-14 | Honda Motor Co Ltd | Vehicular power unit |
| CN100402333C (en) * | 2000-03-30 | 2008-07-16 | 本田技研工业株式会社 | Power gearing device for small vehicle |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2826323B2 (en) * | 1988-08-11 | 1998-11-18 | ヤマハ発動機株式会社 | Transmission system for vehicle engine |
| CN105008765A (en) * | 2013-02-27 | 2015-10-28 | 爱信Ai株式会社 | Transmission |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5337681Y2 (en) * | 1973-07-02 | 1978-09-12 | ||
| JPS5314870U (en) * | 1976-07-19 | 1978-02-07 |
-
1984
- 1984-11-27 JP JP59248812A patent/JPH0656196B2/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100402333C (en) * | 2000-03-30 | 2008-07-16 | 本田技研工业株式会社 | Power gearing device for small vehicle |
| JP2001322442A (en) * | 2000-05-12 | 2001-11-20 | Honda Motor Co Ltd | Power transmission device for small-sized vehicle |
| JP4499871B2 (en) * | 2000-05-12 | 2010-07-07 | 本田技研工業株式会社 | Power transmission device for small vehicles |
| JP2007145259A (en) * | 2005-11-30 | 2007-06-14 | Honda Motor Co Ltd | Vehicular power unit |
| JP4509919B2 (en) * | 2005-11-30 | 2010-07-21 | 本田技研工業株式会社 | Power unit for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60164049A (en) | 1985-08-27 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |