JPH0747644Y2 - Diesel vehicle transmission - Google Patents
Diesel vehicle transmissionInfo
- Publication number
- JPH0747644Y2 JPH0747644Y2 JP1988075694U JP7569488U JPH0747644Y2 JP H0747644 Y2 JPH0747644 Y2 JP H0747644Y2 JP 1988075694 U JP1988075694 U JP 1988075694U JP 7569488 U JP7569488 U JP 7569488U JP H0747644 Y2 JPH0747644 Y2 JP H0747644Y2
- Authority
- JP
- Japan
- Prior art keywords
- speed
- clutch
- shaft
- gear
- reverse
- 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
Links
- 230000005540 biological transmission Effects 0.000 title claims description 20
- 230000008878 coupling Effects 0.000 description 7
- 238000010168 coupling process Methods 0.000 description 7
- 238000005859 coupling reaction Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Landscapes
- Gear-Shifting Mechanisms (AREA)
Description
【考案の詳細な説明】 （産業上の利用分野） 前後進ともに２速段の切換えができる入力軸と出力軸が
同心のディーゼル動車用変速機に関するものである。[Detailed Description of the Invention] (Industrial field of application) The present invention relates to a diesel vehicle transmission having an input shaft and an output shaft which are concentric and which can switch between a second speed stage in forward and backward movements.
（従来の技術） 第２図は従来の前後進２速段の同心形のディーゼル動車
用変速機を示したものである。(Prior Art) FIG. 2 shows a conventional concentric diesel vehicle transmission having two forward and reverse speeds.
第２図においてディーゼルエンジン（図示せず）からの
動力は，継手１から流体式変速機２の入力軸３より直結
クラッチ４を一体に組合せたトルクコンバータ５のイン
ペラホイールカバーを経てインペラホイール６に伝達さ
れ，このインペラホイール６の回転によってトルクコン
バータ５のサーキット内に生じた充填油の循環によるポ
ンプ作用によってタービンホイール８が回転され，ター
ビンホイール８と一体のタービン軸９にトルクを増大し
た回転を出力する。In FIG. 2, power from a diesel engine (not shown) is transmitted from the joint 1 to the impeller wheel 6 of the torque converter 5 in which the direct coupling clutch 4 is integrally combined with the input shaft 3 of the hydraulic transmission 2. The turbine wheel 8 is transmitted by the rotation of the impeller wheel 6 and the turbine wheel 8 is rotated by the pump action due to the circulation of the filling oil generated in the circuit of the torque converter 5, so that the turbine shaft 9 integrated with the turbine wheel 8 is rotated with increased torque. Output.
又，直結クラッチ４が係合されるときは，入力軸３の回
転，即ち，エンジンの回転が，直接タービンホイール８
を経てタービン軸９に出力される。このタービン軸９が
接続される変速機10の入力軸11を，この出力軸12と同心
にするために前進用の1,2速クラッチと後進用の1,2速ク
ラッチとを別々の軸に設けている。即ち，前進軸13に前
進１速クラッチ14と前進２速クラッチ15とを，そして，
後進軸16に後進１速クラッチ17と後進２速クラッチ18と
を設け，各軸の２組のクラッチはそれぞれ背中合わせに
結合し，各クラッチの入力側であるクラッチドラム19,2
0及び21,22をそれぞれ軸13及び16と一体に設け，この前
進軸13と一体の被動歯車23を入力軸11と一体の駆動歯車
24に噛合せることによって，入力回転が前進軸13に伝達
され，又，後進軸16と一体の被動歯車25が前進軸13と一
体の駆動歯車26と噛合せることによって，歯車24,23,前
進軸13,そして，歯車26,25を経て後進軸16に入力回転が
逆転して伝達される。クラッチの出力側については，前
進軸13及び後進軸16に回転自在に軸支した前進１速クラ
ッチ14及び後進１速クラッチ17のそれぞれの出力軸27及
び28に一体のピニオン29及び30を出力軸12と一体の１速
出力歯車31に噛合せることによって，前進，又は，後進
の１速段が出力され，同様に，回転自在に軸支した前進
２速クラッチ15及び後進２速クラッチ22のそれぞれの出
力軸32及び33に一体のピニオン34及び35を出力軸12と一
体の２速度出力歯車36と噛合せることによって，前進，
又は，後進の２速が出力される。出力軸12からは図示さ
れていない自在継手及びベベルギヤを介して車軸に動力
が伝達される。Further, when the direct coupling clutch 4 is engaged, the rotation of the input shaft 3, that is, the rotation of the engine is directly transmitted to the turbine wheel 8
Is output to the turbine shaft 9. In order to make the input shaft 11 of the transmission 10 to which the turbine shaft 9 is connected concentric with the output shaft 12, the forward and backward first and second speed clutches and the backward and forward first and second speed clutches are provided as separate shafts. It is provided. That is, a forward first speed clutch 14 and a forward second speed clutch 15 are provided on the forward shaft 13, and
The reverse shaft 16 is provided with a reverse first speed clutch 17 and a reverse second speed clutch 18, two sets of clutches for each shaft are connected back to back, and the clutch drums 19, 2 on the input side of each clutch are connected.
0, 21, and 22 are provided integrally with shafts 13 and 16, respectively, and a driven gear 23 integral with the forward shaft 13 is a drive gear integral with the input shaft 11.
The input rotation is transmitted to the forward shaft 13 by meshing with the gear 24, and the driven gear 25 integral with the reverse shaft 16 is meshed with the drive gear 26 integral with the forward shaft 13 to couple the gears 24, 23, forward. The input rotation is reversely transmitted to the reverse shaft 16 via the shaft 13 and the gears 26 and 25. On the output side of the clutch, pinions 29 and 30 integrated with the output shafts 27 and 28 of the forward first speed clutch 14 and the reverse first speed clutch 17, which are rotatably supported by the forward shaft 13 and the reverse shaft 16, are provided. By engaging with the 1st speed output gear 31 integrated with 12, the forward or reverse 1st speed is output, and similarly, the forward 2nd speed clutch 15 and the reverse 2nd speed clutch 22 are rotatably supported respectively. By engaging the pinions 34 and 35 integral with the output shafts 32 and 33 with the two-speed output gear 36 integral with the output shaft 12,
Alternatively, the reverse second speed is output. Power is transmitted from the output shaft 12 to the axle via a universal joint and a bevel gear (not shown).
各クラッチは，多板式油圧クラッチで構成されており，
出力軸（27）の外周部のスプラインに軸方向摺動自在に
嵌合した出力側クラッチ板（37）と，入力側のクラッチ
ドラム（20）の内周部のスプラインに軸方向摺動自在に
嵌合した入力側クラッチ板（38）とが交互に配列され，
図示されていない油圧源から切換弁を経て供給される油
圧で作動するクラッチピストン（39）と，バッキングプ
レート（40）との間で与えられる押圧力によって係合し
て回転を伝達するようになっている。Each clutch consists of a multi-plate hydraulic clutch,
The output side clutch plate (37) is slidably fitted in the spline on the outer periphery of the output shaft (27), and the spline on the inner periphery of the input side clutch drum (20) is slidable in the axial direction. The fitted input side clutch plates (38) are arranged alternately.
The clutch piston (39) operated by the hydraulic pressure supplied from a hydraulic source (not shown) through the switching valve and the backing plate (40) are engaged by the pressing force applied to transmit the rotation. ing.
直結クラッチ４の係脱は，大きい出力トルクを必要とす
るスタート時などのトルクコンバータによる変速運転
と，高速下の直結運転との間の切換えをするもので，直
結クラッチ４を脱にした，一般に，スタート時の変速運
転の下では１速クラッチを係合し，車速が充分に増加し
た後，直結クラッチ４を係合して１速の直結運転に入
り，そして車速が１速の所定の速度に達したならば,2速
に切換えて，所定の速度まで加速する。The engagement / disengagement of the direct coupling clutch 4 is to switch between the speed change operation by the torque converter at the time of start requiring a large output torque and the direct engagement operation at a high speed. Generally, the direct coupling clutch 4 is disengaged. , Under the variable speed operation at the start, the first speed clutch is engaged, and after the vehicle speed is sufficiently increased, the direct coupling clutch 4 is engaged to enter the first speed direct coupling operation, and the vehicle speed is a predetermined speed. If it reaches, switch to 2nd speed and accelerate to the specified speed.
（考案が解決しようとする問題点） しかし、前記のような入力軸と出力軸が同心配置で、前
後進ともに２速段の変速機は歯車のかみ合い数が多く構
造が複雑で価格的に高価であり、解放されているクラッ
チの引きずりトルクによる摩擦損失も大きく伝達効率の
点でも問題があった。本考案はこれらの問題を解決する
コンパクトで安価な、伝達効率の優れた前後進２速段の
ディーゼル動車用変速機を提供することを目的とするも
のである。(Problems to be solved by the invention) However, the transmission having the concentric arrangement of the input shaft and the output shaft as described above and the second speed stage for both forward and backward movement has a large number of gear meshes, has a complicated structure and is expensive in terms of price. The friction loss due to the drag torque of the released clutch is large, and there is a problem in terms of transmission efficiency. It is an object of the present invention to provide a compact and inexpensive transmission for a diesel moving vehicle having two forward and reverse speeds, which is compact and inexpensive and has excellent transmission efficiency.
（問題を解決するための手段） 上記の目的を達成するため、本考案では入力軸と出力軸
とを同心に配置した前後進２速段の変速機において、第
１変速軸と第２変速軸とを平行に設け、第１変速軸に前
進クラッチと２速クラッチとを背中合わせにして前進ク
ラッチドラム及び２速クラッチドラムを一体に設け、さ
らに、第２変速軸に後進クラッチと１速クラッチとを背
中合わせにして後進クラッチドラム及び１速クラッチド
ラムを一体に設け、上記の前進クラッチドラム及び２速
クラッチドラムと一体の第１歯車と、後進クラッチドラ
ム及び１速クラッチドラムと一体の第２歯車とをかみ合
わせ、第１変速軸及び第２変速軸にそれぞれ回転自在に
軸支した前進クラッチ及び後進クラッチの入力軸として
の前進歯車軸及び後進歯車軸にそれぞれ一体の前進ピニ
オン及び後進ピニオンを、入力軸と一体の入力歯車にか
み合わせ、同様にして、第１変速軸及び第２変速軸にそ
れぞれ回転自在に軸支した２速クラッチ及び１速クラッ
チの出力軸としての２速歯車軸及び１速歯車軸にそれぞ
れ一体の２速歯車と１速歯車とをかみ合わせ、更に２速
歯車軸と一体に形成した２速ピニオンを出力軸と一体の
出力歯車にかみ合わせるよう構成したものである。(Means for Solving the Problem) In order to achieve the above object, in the present invention, in a forward and reverse second speed transmission in which an input shaft and an output shaft are concentrically arranged, a first shift shaft and a second shift shaft are provided. Are provided in parallel, a forward clutch and a second speed clutch are provided back to back on the first speed change shaft, and a forward clutch drum and a second speed clutch drum are integrally provided. Further, a second reverse speed clutch and a first speed clutch are provided on the second speed change shaft. A reverse clutch drum and a first speed clutch drum are integrally provided back to back, and a first gear that is integrated with the forward clutch drum and the second speed clutch drum and a second gear that is integrated with the reverse clutch drum and the first speed clutch drum are provided. The forward gear shaft and the reverse gear shaft as input shafts of the forward clutch and the reverse clutch rotatably supported by the first speed change shaft and the second speed change shaft, respectively, are engaged with each other. The forward and backward pinion of the body are engaged with the input gear integrated with the input shaft, and similarly, the output shafts of the second speed clutch and the first speed clutch which are rotatably supported by the first speed change shaft and the second speed change shaft, respectively. The second speed gear shaft and the first speed gear shaft are engaged with the second speed gear and the first speed gear, respectively, and the second speed pinion formed integrally with the second speed gear shaft is engaged with the output gear integrated with the output shaft. It is configured as follows.
（実施例） 本考案の変速機の実施例を第１図に示す。(Embodiment) An embodiment of the transmission of the present invention is shown in FIG.
直結クラッチ４とトルクコンバータ５については従来例
と同じ構成であるから説明を省略する。第１図におい
て，流体式変速機41の変速機42の入力軸11と出力軸43と
は同心に設け，これらの軸に，前進クラッチ44と２速ク
ラッチ45とを背中合せにして架設した第１変速軸46と，
後進クラッチ47と１速クラッチ48とを背中合せにして架
設した第２変速軸49とを平行に配設し，第１変速軸46及
び第２変速軸49に回転自在に軸支した前進クラッチ44及
び後進クラッチ47の入力軸としての前進歯車軸50及び後
進歯車軸51と一体の前進ピニオン52及び後進ピニオン53
を入力軸11と一体の入力歯車54と噛合せ，前進クラッチ
44と２速クラッチ45とのクラッチドラム55,56と一体の
第１歯車57を，後進クラッチ47と１速クラッチ48とのク
ラッチドラム58,59と一体の第２歯車60に噛合せ,1速ク
ラッチ48の第２変速軸49に回転自在に軸支した１速歯車
軸61と一体の１速歯車62を２速クラッチ45の第１変速軸
46に回転自在に軸支した２速歯車軸63と一体の２速歯車
64に噛合せ，そして，この２速歯車軸63と一体の２速ピ
ニオン65を出力軸43と一体の出力歯車66に噛合せて構成
されている。Since the direct coupling clutch 4 and the torque converter 5 have the same configuration as the conventional example, the description thereof will be omitted. In FIG. 1, an input shaft 11 and an output shaft 43 of a transmission 42 of a hydraulic transmission 41 are concentrically provided, and a forward clutch 44 and a second speed clutch 45 are installed back to back on these shafts. Gearbox 46,
A reverse clutch 47 and a first speed clutch 48 are arranged in parallel with a second speed change shaft 49 installed back to back, and a forward clutch 44 is rotatably supported by the first speed change shaft 46 and the second speed change shaft 49. A forward pinion 52 and a reverse pinion 53 integrated with the forward gear shaft 50 and the reverse gear shaft 51 as the input shaft of the reverse clutch 47.
Meshes with the input gear 54 integrated with the input shaft 11
The first gear 57, which is integrated with the clutch drums 55 and 56 of the 44 and the second speed clutch 45, is meshed with the second gear 60, which is integrated with the clutch drums 58 and 59 of the reverse clutch 47 and the first speed clutch 48, and the first speed is set. The first speed gear 62 integral with the first speed gear shaft 61 rotatably supported on the second speed change shaft 49 of the clutch 48 is the first speed change shaft of the second speed clutch 45.
Second speed gear that is integral with second speed gear shaft 63 that is rotatably supported by 46
The second gear pinion 65, which is in mesh with the second gear shaft 63, is meshed with the output gear 66, which is integral with the output shaft 43.
各クラッチの係脱は，第１変速軸（46）に回転自在に軸
支した前進歯車軸（50）の外周部のスプラインに軸方向
摺動自在に嵌合したクラッチ板（67）とクラッチドラム
（55）の内周部のスプラインに軸方向摺動自在に嵌合し
たクラッチ板（68）とを交互に配列し，図示されていな
い油圧源から切換弁を経て与えられる油圧で作動するク
ラッチピストン（69）とバッキングプレート（70）との
間で押圧されることによってなされる。To engage and disengage each clutch, the clutch plate (67) and the clutch drum which are axially slidably fitted to the spline on the outer periphery of the forward gear shaft (50) rotatably supported by the first speed change shaft (46). A clutch piston which is alternately arranged with a clutch plate (68) axially slidably fitted to a spline of the inner peripheral portion of (55) and is operated by a hydraulic pressure supplied from a hydraulic source (not shown) through a switching valve. This is done by pressing between the (69) and the backing plate (70).
上記のような構成において，まず前進の１速は，前進ク
ラッチ44と１速クラッチ48を係合することによって，入
力軸11の回転を入力歯車54,前進ピニオン52,前進クラッ
チ44,第１歯車57,第２歯車60,1速クラッチ48,1速歯車6
2,2速歯車64,2速ピニオン65及び出力歯車66を経て出力
軸43に伝達され，次に，前進の２速は前進クラッチ44と
２速クラッチ45とを係合することによって，入力軸11の
回転を入力歯車54,前進ピニオン52,前進クラッチ44,2速
クラッチ45,2速ピニオン65及び出力歯車66を経て出力軸
43に伝達される。更に，後進の１速又は２速は，後進ク
ラッチ47とともに,1速クラッチ48,又は,2速クラッチ45
を係合することによって，入力歯車54,後進ピニオン53,
後進クラッチ47,1速クラッチ48,1速歯車62,2速歯車64,2
速ピニオン65及び出力歯車66を経て出力軸43に，又は，
入力歯車54,後進ピニオン53,後進クラッチ47,第２歯車6
0,第１歯車57,2速クラッチ45,2速ピニオン65及び出力歯
車66を経て出力軸43にそれぞれなされる。In the above-described structure, first, in the forward first speed, the forward clutch 44 and the first speed clutch 48 are engaged to rotate the input shaft 11 to rotate the input gear 54, the forward pinion 52, the forward clutch 44, and the first gear. 57, second gear 60, first speed clutch 48, first speed gear 6
It is transmitted to the output shaft 43 through the second and second speed gears 64, the second speed pinion 65 and the output gear 66, and then the second forward speed is obtained by engaging the forward clutch 44 and the second speed clutch 45. 11 rotations through the input gear 54, forward pinion 52, forward clutch 44, second speed clutch 45, second speed pinion 65 and output gear 66
Transmitted to 43. Further, the reverse first speed or the second speed, together with the reverse clutch 47, the first speed clutch 48 or the second speed clutch 45.
By engaging the input gear 54, the reverse pinion 53,
Reverse clutch 47, 1st speed clutch 48, 1st speed gear 62, 2nd speed gear 64, 2
To the output shaft 43 via the speed pinion 65 and the output gear 66, or
Input gear 54, reverse pinion 53, reverse clutch 47, second gear 6
0, the first gear 57, the second speed clutch 45, the second speed pinion 65 and the output gear 66, and the output shaft 43.
クラッチの切換えは，図示されていない油圧回路に設け
られた前後進クラッチ切換電磁弁及び1,2速クラッチ切
換電磁弁を電気的に操作することによってなされ，前進
クラッチ又は後進クラッチの，及び,1速クラッチ又は２
速クラッチのそれぞれどちらかの一方のクラッチガ係合
されているときは，他方のクラッチが確実に脱されるよ
うに，切換電磁弁が作動して，両クラッチが同時に係合
するのを防止する構成になっている。The switching of the clutch is performed by electrically operating the forward / reverse clutch switching solenoid valve and the 1st and 2nd speed clutch switching solenoid valves provided in a hydraulic circuit (not shown). Speed clutch or 2
A structure in which a switching solenoid valve is actuated to prevent both clutches from being engaged at the same time so that when one of the high speed clutches is engaged, the other clutch is surely disengaged. It has become.
（考案の効果） 上記した如く本考案は，入出力軸を同心的に設け，この
入力軸に併設した二本の変速軸のそれぞれ一方の同じ側
に前進クラッチと後進クラッチを，他方の同じ側に１速
クラッチと２速クラッチを，一方の側のクラッチと他方
の側のクラッチとを背中合せにキャリアを一体にして設
け，上記の一方の側の前進及び後進クラッチを入力側と
し，他方の側の１速及び２速クラッチを出力側としたの
で出力軸と一体の出力歯車が１個で済み、所要の総歯車
数が10個から９個になって１個削減されると共に、出力
軸が短かくなり変速機の構成が簡素化されて製作及び保
守が容易になる。また、入力軸から出力軸へ動力が伝達
される際に、前進クラッチと２速クラッチ及び後進クラ
ッチと１速クラッチの組み合わせのうち、それぞれのい
ずれか一方のクラッチが常時係合されることになり、解
放されているクラッチは従来の３つから２つに減少する
ので、脱状態にあるクラッチの引きずりトルクによる摩
擦損失が減少して動力伝達効率が改善される。(Effect of the Invention) As described above, the present invention has the input and output shafts concentrically provided, and the forward and reverse clutches are provided on the same side of one of the two speed change shafts provided side by side with the input shaft, and the same side of the other transmission shaft. 1st speed clutch and 2nd speed clutch, one side clutch and the other side clutch are back-to-back integrated with the carrier, and the forward and reverse clutches on the one side are used as the input side and the other side clutch is used. Since the 1st and 2nd speed clutches on the output side are on the output side, only one output gear is required to be integrated with the output shaft, and the required total number of gears has been reduced from 10 to 9 and the output shaft is reduced. It is short and simplifies the structure of the transmission to facilitate manufacture and maintenance. Further, when power is transmitted from the input shaft to the output shaft, one of the clutches of the forward clutch and the second speed clutch and the reverse clutch and the first speed clutch is always engaged. Since the number of released clutches is reduced from three to two, the friction loss due to the drag torque of the clutch in the disengaged state is reduced and the power transmission efficiency is improved.
第１図は本考案の変速機を結合した流体変速機を及び第
２図は同様に従来例を示したものである。 11……入力軸,43……出力軸,44……前進クラッチ,45…
…２速クラッチ,46……第１変速軸,47……後進クラッ
チ,48……１速クラッチ,49……第２変速軸,50……前進
歯車軸,51……後進歯車軸,52……前進ピニオン,53……
後進ピニオン,54……入力歯車,55……前進クラッチドラ
ム,56……２速クラッチドラム,57……第１歯車,58……
後進クラッチドラム,59……１速クラッチドラム,60……
第２歯車,61……１速歯車軸,62……１速歯車,63……２
速歯車軸,64……２速歯車,65……２速ピニオン,66……
出力歯車FIG. 1 shows a fluid transmission in which the transmission of the present invention is combined, and FIG. 2 similarly shows a conventional example. 11 …… input shaft, 43 …… output shaft, 44 …… forward clutch, 45…
… 2nd speed clutch, 46 …… 1st speed change shaft, 47 …… reverse gear clutch, 48 …… 1st speed clutch, 49 …… 2nd speed change shaft, 50 …… forward gearwheel shaft, 51 …… reverse gearwheel shaft, 52… … Forward pinion, 53 ……
Reverse gear, 54 …… Input gear, 55 …… Forward clutch drum, 56 …… Second speed clutch drum, 57 …… First gear, 58 ……
Reverse clutch drum, 59 …… First speed clutch drum, 60 ……
2nd gear, 61 …… 1st speed gear shaft, 62 …… 1st speed gear, 63 …… 2
High speed gear shaft, 64 …… Second speed gear, 65 …… Second speed pinion, 66 ……
Output gear
Claims (1)
２速段の変速機において、第１変速軸（46）と第２変速
軸（49）とを入力軸（11）にに平行に設け、第１変速軸
（46）に前進クラッチ（44）と２速クラッチ（45）とを
背中合わせにして前進クラッチドラム（55）及び２速ク
ラッチドラム（56）を一体に設け、さらに、第２変速軸
（49）に後進クラッチ（47）と１速クラッチ（48）とを
背中合わせにして後進クラッチドラム（58）及び１速ク
ラッチドラム（59）を一体に設け、上記の前進クラッチ
ドラム（55）及び２速クラッチドラム（56）と一体の第
１歯車（57）と、後進クラッチドラム（58）及び１速ク
ラッチドラム（59）と一体の第２歯車（60）とをかみ合
わせ、第１変速軸（46）及び第２変速軸（49）にそれぞ
れ回転自在に軸支した前進クラッチ（44）及び後進クラ
ッチ（47）の入力軸としての前進歯車軸（50）及び後進
歯車軸（51）にそれぞれ一体の前進ピニオン（52）及び
後進ピニオン（53）を、入力軸（11）と一体の入力歯車
（54）にかみ合わせ、同様にして、第１変速軸（46）及
び第２変速軸（49）にそれぞれ回転自在に軸支した２速
クラッチ（45）及び１速クラッチ（48）の出力軸として
の２速歯車軸（63）及び１速歯車軸（61）にそれぞれ一
体の２速歯車（64）と１速歯車（62）とをかみ合わせ、
更に２速歯車軸（63）と一体に形成した２速ピニオン
（65）を出力軸（43）と一体の出力歯車（66）にかみ合
わせたことを特徴とするディーゼル動車用変速機。1. A forward and reverse second speed transmission in which an input shaft and an output shaft are concentrically arranged, and a first speed change shaft (46) and a second speed change shaft (49) are used as an input shaft (11). They are provided in parallel, the forward clutch (44) and the second speed clutch (45) are back-to-back on the first speed change shaft (46), and the forward clutch drum (55) and the second speed clutch drum (56) are integrally provided. A reverse clutch drum (58) and a first speed clutch drum (59) are integrally provided on the second speed change shaft (49) with the reverse clutch (47) and the first speed clutch (48) back to back, and the forward clutch drum (58 55) and the first gear (57) integrated with the second speed clutch drum (56) and the second gear (60) integrated with the reverse clutch drum (58) and the first speed clutch drum (59) are engaged to form the first gear. A forward clutch that is rotatably supported by the speed change shaft (46) and the second speed change shaft (49). The forward gear pinion (52) and the reverse gear pinion (53), which are integrated with the forward gear shaft (50) and the reverse gear shaft (51) as the input shafts of the (44) and the reverse clutch (47), are connected to the input shaft (11). Similarly, a second speed clutch (45) and a first speed clutch (48) are meshed with an integral input gear (54) and are similarly rotatably supported by a first speed change shaft (46) and a second speed change shaft (49), respectively. The second speed gear (64) and the first speed gear (62), which are integrated with the second speed gear shaft (63) and the first speed gear shaft (61), respectively, as the output shaft of
Furthermore, a transmission for a diesel vehicle, characterized in that a second speed pinion (65) formed integrally with the second speed gear shaft (63) is engaged with an output gear (66) integrated with the output shaft (43).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1988075694U JPH0747644Y2 (en) | 1988-06-07 | 1988-06-07 | Diesel vehicle transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1988075694U JPH0747644Y2 (en) | 1988-06-07 | 1988-06-07 | Diesel vehicle transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01178262U JPH01178262U (en) | 1989-12-20 |
| JPH0747644Y2 true JPH0747644Y2 (en) | 1995-11-01 |
Family
ID=31300751
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1988075694U Expired - Lifetime JPH0747644Y2 (en) | 1988-06-07 | 1988-06-07 | Diesel vehicle transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0747644Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4589617B2 (en) * | 2003-11-10 | 2010-12-01 | 株式会社日立ニコトランスミッション | Diesel vehicle power transmission |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE789545A (en) * | 1971-09-30 | 1973-01-15 | Clark Equipment Co | GEAR GEARBOX |
-
1988
- 1988-06-07 JP JP1988075694U patent/JPH0747644Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01178262U (en) | 1989-12-20 |
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