JPH02290724A - Driving power transmission device for four-wheel drive vehicle - Google Patents

Driving power transmission device for four-wheel drive vehicle

Info

Publication number
JPH02290724A
JPH02290724A JP11071389A JP11071389A JPH02290724A JP H02290724 A JPH02290724 A JP H02290724A JP 11071389 A JP11071389 A JP 11071389A JP 11071389 A JP11071389 A JP 11071389A JP H02290724 A JPH02290724 A JP H02290724A
Authority
JP
Japan
Prior art keywords
differential
wheel drive
driving force
differential mechanism
wheel
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.)
Granted
Application number
JP11071389A
Other languages
Japanese (ja)
Other versions
JP2906249B2 (en
Inventor
Toru Hamada
濱田 透
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.)
Suzuki Motor Corp
Original Assignee
Suzuki Motor Corp
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 Suzuki Motor Corp filed Critical Suzuki Motor Corp
Priority to JP11071389A priority Critical patent/JP2906249B2/en
Publication of JPH02290724A publication Critical patent/JPH02290724A/en
Application granted granted Critical
Publication of JP2906249B2 publication Critical patent/JP2906249B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Abstract

PURPOSE:To improve the lack in driving power transmission for rear wheels so as to improve running performance by forming a front differential mechanism out of a viscous coupling and also a rear differential mechanism out of a differential gear train. CONSTITUTION:A four-wheel drive vehicle 2 converts the driving power of an internal engine 4 into a desired torque-speed by a transmission 6, and transmits it from a front end decelerating mechanism 8 to front axles 12 (12L, 12R) through a front differential mechanism 10. The driving power of the internal combustion engine 4 distributed by a driving power distribution mechanism 16 is transmitted to rear axles 24 (24L, 24R) from a rear end decelerating mechanism 20 through a rear differential mechanism 22 by a propeller shaft 18, whereas the front differential mechanism 10 is formed out of a viscous coupling 56, and the rear differential mechanism 22 is formed out of a differential gear train 58. It is thus possible to transmit driving power to front wheels side by the viscous coupling 56 only when hard starting is carried out or the difference in rotational speed occurs between front and rear wheels.

Description

【発明の詳細な説明】 〔産業上の利用分野〕 この発明は4輪駆動車の駆動力伝達装置に係り、特に前
置き内燃機関前部車輪駆動方式の車両を基にした4輪駆
動車における後部車輪への駆動力伝達不足を改善した4
輪駆動車の駆動力伝達装置に関する。
[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a drive power transmission device for a four-wheel drive vehicle, and particularly to a rear drive power transmission device for a four-wheel drive vehicle based on a front-mounted internal combustion engine front wheel drive vehicle. Improved the lack of drive power transmission to the wheels 4
The present invention relates to a driving force transmission device for a wheel drive vehicle.

〔従来の技術〕[Conventional technology]

近時、悪路走行や不整地走行のみならず、通常の走路走
行等のあらゆる走行状態における走行性能や安全性を向
上するために、内燃機関の駆動力を全ての車軸に伝達し
て全車輪を駆動する4輪駆動車が多種出現している。こ
のような4輪駆動車の駆動力伝達装置としては、特開昭
60〜1030号公報や特開昭60−236839号公
報に開示のものがある。
Recently, in order to improve driving performance and safety in all driving conditions, including driving on rough roads and uneven terrain, as well as driving on normal roads, the driving force of the internal combustion engine is transmitted to all axles to all wheels. Many types of four-wheel drive vehicles have appeared. Such a driving force transmission device for a four-wheel drive vehicle is disclosed in Japanese Patent Laid-Open No. 60-1030 and Japanese Patent Laid-Open No. 60-236839.

特開昭60−1030号公報に開示のものは、変速機の
出力歯車に噛合する前部終減速大歯車の半径方向内側で
且つ前部終減速大歯車と同軸に湿式クラッチ装置を設け
たことにより、前部差動機構の左右偏倚を防止して前部
左右車軸長の差を小とし、いわゆるトルクステア等の発
生を抑え得て、また、前部車輪及び後部車輪間の回転数
差を吸収し得るとともに前部車輪及び後部車輪に伝達さ
れる駆動力のトルク配分を変更可能としたものである。
What is disclosed in JP-A-60-1030 is that a wet clutch device is provided radially inside and coaxially with the front final reduction large gear that meshes with the output gear of the transmission. This prevents left-right deviation of the front differential mechanism, reduces the difference in front left and right axle lengths, suppresses the occurrence of so-called torque steer, and also reduces the difference in rotational speed between the front wheels and rear wheels. In addition to being able to absorb the torque, the torque distribution of the driving force transmitted to the front wheels and rear wheels can be changed.

また、特開昭60−236839号公報に開示のものは
、駆動力分配機構の歯車を支持するマウントケーシング
内に前部差動機構と同軸的に差動制限機構を配設し、こ
の差動制限機構を前部差動機構の入力側と他方の出力側
に介在させたことにより、前部差動機構の入力側と他方
の出力側との相対回転時に差動制限トルクを生じさせて
走行性能の向上を図るとともに、マウントケーシング内
の空間部を利用して差動制限機構をコンパクトに組付け
可能としたものである。
Furthermore, in the device disclosed in Japanese Patent Application Laid-open No. 60-236839, a differential limiting mechanism is disposed coaxially with the front differential mechanism in a mount casing that supports the gears of the driving force distribution mechanism. By interposing the limiting mechanism on the input side of the front differential mechanism and the other output side, a differential limiting torque is generated during relative rotation between the input side of the front differential mechanism and the other output side, allowing running. In addition to improving performance, the differential limiting mechanism can be assembled compactly by utilizing the space inside the mount casing.

〔発明が解決しようとする問題点〕[Problem that the invention seeks to solve]

ところで、4輪駆動車には、前方に載置した内燃機関の
駆動力により前部車輪を駆動する方式の、いわゆる前置
き内燃機関前部車輪動力式の車両を基にして、駆動力分
配機構により内燃機関の駆動力を分配して後部車輪を駆
動する4輪駆動車がある。
By the way, four-wheel drive vehicles are based on so-called front-mounted internal combustion engine front wheel powered vehicles, in which the front wheels are driven by the driving force of an internal combustion engine mounted in the front, and are equipped with a driving force distribution mechanism. There are four-wheel drive vehicles that drive rear wheels by distributing the driving force of an internal combustion engine.

例えば、第7〜IO図に示す如く、4輪駆動車202に
は、前方に載置した内燃機関204の駆動力を変速機2
06により所望のトルク・回転数に変換して取出し、こ
の駆動力を前部柊滅速機構20日から前部差動機構21
0を介して前部車軸212である前部右側車軸212R
及び前部左側車軸212Lに夫々伝達し、前部車輪21
4である前部右側車輪214R及び前部左側車輪214
Lを夫々駆動するとともに、駆動力分配機構216によ
り分配した駆動力を推進軸218により後部終減速機構
220から後部差動機構222を介して後部車軸224
である後部右側車軸224R及び後部左側車軸224L
に夫々伝達し、後部車輪226である後部右側車輪22
6R及び後部左側車輪226Lを夫々駆動するものがあ
る。
For example, as shown in FIG.
06 converts it into the desired torque and rotational speed and extracts it, and this driving force is transferred from the front Hiiragi speed reduction mechanism 20 to the front differential mechanism 21.
0 through the front right axle 212R, which is the front axle 212.
and the front left axle 212L, respectively, and the front wheel 21
4, the front right wheel 214R and the front left wheel 214
At the same time, the driving force distributed by the driving force distribution mechanism 216 is transferred from the rear final reduction mechanism 220 to the rear axle 224 via the rear differential mechanism 222 by the propulsion shaft 218.
The rear right axle 224R and the rear left axle 224L are
and the rear right wheel 22 which is the rear wheel 226.
There is one that drives the rear left wheel 6R and the rear left wheel 226L, respectively.

このような4輪駆動車202の前部車輪214と後部車
輪226との差動を許容するとともに一定以上の差動を
制限するために、粘性継手(ビスカスカップリング)2
28を設けたものがある。
In order to allow the differential movement between the front wheels 214 and the rear wheels 226 of the four-wheel drive vehicle 202 and limit the differential movement beyond a certain level, a viscous coupling 2 is used.
There is one with 28.

この粘性継手228は、例えば、第8図に示す如く駆動
力分配機構216の出力軸230と推進軸218との間
に設け、また、第9図に示す如く推進軸218の途中に
設け、あるいは、第10図に示す如く推進軸218と後
部終減速機構220の入力軸232との間に設けたもの
等がある。
This viscous joint 228 may be provided, for example, between the output shaft 230 of the driving force distribution mechanism 216 and the propulsion shaft 218 as shown in FIG. 8, or in the middle of the propulsion shaft 218 as shown in FIG. , as shown in FIG. 10, is provided between the propulsion shaft 218 and the input shaft 232 of the rear final reduction mechanism 220.

ところが、前記の如き前置き内燃機関前部車輪駆動方式
の車両を基にした4輪駆動車は、前部車輪及び後部車輪
の荷重配分が前部車輪側に偏ることになるため、後部車
輪に伝達される駆動力が不足する問題がある。このよう
な後部車輪への駆動力伝達不足は、特に、減速時に顕著
に現れる。このため、前置き内燃機関前部車輪駆動方式
の車両を基にした4輪駆動車は、前方に載置した内燃機
関の駆動力により後部車輪を駆動する方式の、いわゆる
前置き内燃機関後部車輪駆動方式の車両を基にした4輪
駆動車よりも走破性能等について不利となる不都合があ
った。
However, in a four-wheel drive vehicle based on a vehicle with a front-mounted internal combustion engine and a front wheel drive system as described above, the load distribution between the front wheels and rear wheels is biased toward the front wheels, so that the load is not transmitted to the rear wheels. There is a problem of insufficient driving force. This insufficient transmission of driving force to the rear wheels becomes particularly noticeable during deceleration. For this reason, 4-wheel drive vehicles based on vehicles with a front-mounted internal combustion engine and front wheel drive system use a so-called front-mounted internal combustion engine and rear wheel drive system, in which the rear wheels are driven by the driving force of the internal combustion engine mounted in the front. It had the disadvantage of being disadvantageous in terms of running performance, etc., compared to four-wheel drive vehicles based on the same vehicle.

〔発明の目的〕[Purpose of the invention]

そこで、この発明の目的は、前置き内燃機関前部車輪駆
動方式の車両を基にした4輪駆動車における後部車輪へ
の駆動力伝達不足を改善し得て、前置き内燃機関後部車
輪駆動方式の車両を基にした4輪駆動車と同等の走破性
能を発揮し得て、走行性能や安全性を向上し得る4輪駆
動車の駆動力伝達装置を実現することにある。
SUMMARY OF THE INVENTION Therefore, an object of the present invention is to improve the insufficient transmission of driving force to the rear wheels in a four-wheel drive vehicle based on a vehicle with a front internal combustion engine and rear wheel drive system. The object of the present invention is to realize a driving force transmission device for a four-wheel drive vehicle that can exhibit running performance equivalent to that of a four-wheel drive vehicle based on the above, and that can improve running performance and safety.

〔問題点を解決するための手段〕[Means for solving problems]

この目的を達成するために、この発明は、前方に載置し
た内燃機関の駆動力を前部差動機構を介して前部車軸に
伝達し前部車輪を駆動するとともに駆動力分配機構によ
り分配した前記内燃機関の駆動力を後部差動機構を介し
て後部車軸に伝達し後部車輪を駆動する4輪駆動車にお
いて、前記前部差動機構を粘性継手によりするとともに
構成前記後部差動機構を差動歯車列により構成したこと
を特徴とする。
In order to achieve this objective, the present invention transmits the driving force of an internal combustion engine mounted at the front to the front axle via a front differential mechanism to drive the front wheels, and distributes it by a driving force distribution mechanism. In a four-wheel drive vehicle in which the driving force of the internal combustion engine is transmitted to the rear axle via a rear differential mechanism to drive the rear wheels, the front differential mechanism is formed by a viscous coupling and the rear differential mechanism is configured. It is characterized by being constructed by a differential gear train.

〔作用〕[Effect]

この発明の構成によれば、前部差動機構を粘性継手によ
り構成したことにより、前部車輪と後部車輪との間に回
転数差がない場合に、粘性継手は内燃機関の駆動力を前
部車軸に伝達しないので前部車輪は駆動されず、急発進
や前部車輪及び後部車輪に対する路面のμの違い等によ
り前部車輪と後部車輪との間に回転数差が生じた場合に
のみ粘性継手は内燃機関の駆動力を伝達して前部車輪は
駆動されることになる。一方、後部差動機構を差動歯車
列により構成したことにより、内燃機関の駆動力は後部
差動機構の差動歯車列を介して後部車軸に伝達されるこ
ととなり、後部車輪は直接的に駆動されることになる。
According to the configuration of the present invention, the front differential mechanism is configured with a viscous joint, so that when there is no rotational speed difference between the front wheels and the rear wheels, the viscous joint transfers the driving force of the internal combustion engine to the front. Since the transmission is not transmitted to the rear axle, the front wheels are not driven, and only when there is a difference in rotational speed between the front wheels and rear wheels due to a sudden start or a difference in the μ of the road surface relative to the front and rear wheels. The viscous joint transmits the driving force of the internal combustion engine to drive the front wheels. On the other hand, by configuring the rear differential mechanism with a differential gear train, the driving force of the internal combustion engine is transmitted to the rear axle via the differential gear train of the rear differential mechanism, and the rear wheels are directly It will be driven.

〔実施例〕〔Example〕

次にこの発明の実施例を図に基づいて詳細に説明する。 Next, embodiments of the present invention will be described in detail based on the drawings.

第1〜6図は、この発明の実施例を示すものである。第
6図において、2は4輪駆動車である。
1 to 6 show embodiments of this invention. In FIG. 6, 2 is a four-wheel drive vehicle.

この4輪駆動車2は、前方に載置した内燃機関4の駆動
力を変速機6により所望のトルク・回転数に変換して取
出し、この駆動力を前部P:減速機構8から前部差動機
構10を介して前部車軸12である前部右側車軸12R
及び前部左側車軸12Lに夫々伝達し、前部車輪14で
ある前部右側車輪14R及び前部左側車輪14Lを夫々
駆動する。
This four-wheel drive vehicle 2 converts the driving force of an internal combustion engine 4 mounted at the front into desired torque and rotational speed using a transmission 6 and extracts the driving force, and transfers this driving force from a front part P: a reduction mechanism 8 to a front part. The front right axle 12R, which is the front axle 12, via the differential mechanism 10
and the front left axle 12L, and drive the front right wheel 14R and the front left wheel 14L, which are the front wheels 14, respectively.

また、この4輪駆動車2は、駆動力分配機構16により
分配した内燃機関4の駆動力を推進軸18により後部終
減速機構20から後部差動機構22を介して後部車軸2
4である後部右側車軸24R及び後部左側車軸24Lに
夫々伝達し、後部車輪26である後部右側車輪26R及
び後部左側車輪26Lを夫々駆動するものである。
The four-wheel drive vehicle 2 also transmits the driving force of the internal combustion engine 4 distributed by the driving force distribution mechanism 16 from the rear final reduction mechanism 20 to the rear axle shaft 2 through the rear differential mechanism 22 via the propulsion shaft 18.
4, respectively, to the rear right axle 24R and rear left axle 24L, respectively, and drive the rear right wheel 26R and rear left wheel 26L, which are the rear wheels 26, respectively.

詳述すると、第1図に示す如く、4輪駆動車2の前方に
載置した内燃機関4の駆動力は、クラッチ機構28を介
して変速機60入力軸30に入力され、変速歯車列32
により所望のトルク・回転数に変換されて出力軸34か
ら取出される。この出力軸34の出力端には、前部終減
速機構8の前部終減速小歯車36が固設されている。出
力軸34から取出される駆動力は、前部終減速機構8の
前部終滅速小歯車36とこの前部終減速小歯車36に噛
合する前部終減速大歯車38とにより減速されて前部差
動機構10に伝達され、この前部差動機構10により前
部右側車軸12R及び前部左側車軸12Lに夫々伝達さ
れ、前部右側車輪14R及び前部左側車輪14Lを夫々
駆動する。
More specifically, as shown in FIG. 1, the driving force of the internal combustion engine 4 mounted at the front of the four-wheel drive vehicle 2 is input to the input shaft 30 of the transmission 60 via the clutch mechanism 28,
The torque and rotational speed are converted to the desired torque and rotational speed and taken out from the output shaft 34. A front final reduction gear 36 of the front final reduction mechanism 8 is fixed to the output end of the output shaft 34 . The driving force taken out from the output shaft 34 is decelerated by the front final reduction gear 36 of the front final reduction mechanism 8 and the front final reduction large gear 38 that meshes with the front final reduction gear 36. The signal is transmitted to the front differential mechanism 10, and is transmitted by the front differential mechanism 10 to the front right axle 12R and the front left axle 12L, respectively, to drive the front right wheel 14R and the front left wheel 14L, respectively.

また、前記前部終減速機構8の前部終減速大歯車38に
は、駆動力分配機構16の入力軸40の一端に固設した
被動歯車42が噛合されている。
Furthermore, a driven gear 42 fixed to one end of the input shaft 40 of the driving force distribution mechanism 16 is meshed with the front final reduction large gear 38 of the front final reduction mechanism 8 .

この入力軸42に分配して入力された駆動力は、入力軸
42の他端に固設した入力歯車44に噛合する出力歯車
46により出力軸48に出力される。
The driving force distributed and input to the input shaft 42 is output to the output shaft 48 by an output gear 46 that meshes with an input gear 44 fixed to the other end of the input shaft 42.

駆動力分配機構16により分配され出力軸48から出力
される駆動力は、推進軸18により後部終減速機構20
の入力軸50に伝達される。入力軸50には、後部終滅
速小歯車52が固設されている。人力軸50に伝達され
た駆動力は、後部終減速小歯車52とこの後部終減速小
歯車52に噛合する後部終減速大歯車54とにより減速
されて後部差動機構22に伝達され、この後部差動機構
22により後部右側車軸24R及び後部左側車軸24L
に夫々伝達され、後部右側車輪26R及び後部左側車輪
26Lを夫々駆動する。
The driving force distributed by the driving force distribution mechanism 16 and output from the output shaft 48 is transmitted to the rear final reduction mechanism 20 by the propulsion shaft 18.
is transmitted to the input shaft 50 of. A rear terminal speed small gear 52 is fixedly attached to the input shaft 50 . The driving force transmitted to the human power shaft 50 is decelerated by a rear final reduction small gear 52 and a rear final reduction large gear 54 that meshes with this rear final reduction small gear 52, and is transmitted to the rear differential mechanism 22. The differential mechanism 22 allows the rear right axle 24R and the rear left axle 24L to
and drive the rear right wheel 26R and the rear left wheel 26L, respectively.

このように、前方に載置した内燃機関4の駆動力を前部
差動機構10を介して前部車軸12に伝達し前部車輪1
4を駆動するとともに駆動力分配機構16により分配し
た前記内燃機関4の駆動力を後部差動機構22を介して
後部車軸24に伝達し後部車輪26を駆動する4輪駆動
車2において、第1・2図に示す如く、前部差動機構1
0を粘性継手(ビスカスカップリング)56により構成
するとともに後部差動機構22を差動歯車列58により
構成している。
In this way, the driving force of the internal combustion engine 4 mounted at the front is transmitted to the front axle 12 via the front differential mechanism 10, and the driving force is transmitted to the front axle 12.
In the four-wheel drive vehicle 2, the driving force of the internal combustion engine 4 distributed by the driving force distribution mechanism 16 is transmitted to the rear axle 24 via the rear differential mechanism 22 to drive the rear wheels 26.・As shown in Figure 2, the front differential mechanism 1
0 is constituted by a viscous coupling 56, and the rear differential mechanism 22 is constituted by a differential gear train 58.

即ち、前部差動機構10は、第2図に示す如く、前部差
動ハウジング60である前部差動右側ハウジング60R
及び前部差動左側ハウジング60Lを有している。前部
差動左側ハウジング60Lは、前部終減速機構8の前部
終減速大歯車3日に固設されるとともに、前部差動左側
軸受62Lにより変速機第1ケーシング64aに軸支し
て設けている。前記前部差動右側ハウジング60Rは、
前記前部差動左側ハウジング60Lを介して前部終減速
大歯車38に固設されるとともに、前部差動右側軸受6
2Rにより変速機第2ケーシング64bに軸支して設け
ている。また、この前部右側ハウジング60Rには、第
3図に示す如く、側部及び外周の等角度位置に扇状の開
口部66が形成されている。
That is, the front differential mechanism 10 includes a front differential right housing 60R, which is a front differential housing 60, as shown in FIG.
and a front differential left housing 60L. The front differential left housing 60L is fixed to the front final reduction large gear 3 of the front final reduction mechanism 8, and is pivotally supported on the transmission first casing 64a by a front differential left bearing 62L. It is set up. The front differential right housing 60R is
It is fixed to the front final reduction large gear 38 via the front differential left housing 60L, and the front differential right bearing 6
2R to be pivotally supported on the transmission second casing 64b. Further, as shown in FIG. 3, fan-shaped openings 66 are formed in the front right housing 60R at equal angular positions on the side and outer circumference.

前記前部差動右側ハウジング60R及び前部差動左側ハ
ウジング60L内には、粘性継手56が設けられている
。粘性継手56は、右側粘性継手56R及び左側粘性継
手56Lから構成されている。即ち、粘性継手56は、
右側アウタケース68Rと中央アウタケース68Cと左
側アウタケース68Lとより構成されるアウタケース6
8を有している。
A viscous joint 56 is provided in the front differential right housing 60R and the front differential left housing 60L. The viscous joint 56 includes a right viscous joint 56R and a left viscous joint 56L. That is, the viscous joint 56 is
Outer case 6 composed of right outer case 68R, center outer case 68C, and left outer case 68L.
It has 8.

アウタケース68の右側アウタケース68Rと左側アウ
タケース68Lとは、夫々前部右側車軸12R及び前部
左側車軸12Lの一端側に回転可能に軸支して設ける。
A right outer case 68R and a left outer case 68L of the outer case 68 are rotatably supported on one end side of the front right axle 12R and the front left axle 12L, respectively.

この前部右側車軸12R及び前部左側車軸12Lの他端
側には、夫々前部右側車輪14R及び前部左側車輪14
Lが取付けられる。また、アウタケース68の右側アウ
タケース68Rの外周には、アウタケース側スプライン
70を形成して設ける。
On the other end sides of the front right axle 12R and the front left axle 12L, a front right wheel 14R and a front left wheel 14 are provided, respectively.
L is attached. Furthermore, an outer case side spline 70 is formed on the outer periphery of the right outer case 68R of the outer case 68.

前記アウタケース68の中央アウタケース68C内周の
右側アウタケース68R側には、複数枚の右側アウタプ
レート72Rの外周を固設している。また、中央アウタ
ケース68C内周の左側アウタケース68L側には、複
数枚の左側アウタプレー1−72Lの外周を固設してい
る。一方、前部右側車軸12Rの一端側の外周には、夫
々前記右側アウタプレート72Rと交互に配列される右
側インナプレート74Rの内周が固設されている。
The outer periphery of a plurality of right outer plates 72R is fixed to the inner periphery of the central outer case 68C of the outer case 68 on the right outer case 68R side. Moreover, the outer peripheries of a plurality of left outer plays 1-72L are fixedly provided on the left outer case 68L side of the inner periphery of the central outer case 68C. On the other hand, the inner peripheries of right inner plates 74R, which are arranged alternately with the right outer plates 72R, are fixed to the outer periphery of one end of the front right axle 12R.

また、前記前部左側車軸12Lの一端側の外周には、夫
々前記左側アウタプレート72Lと交互に配列される左
側インナプレート74Lの内周が固設されている。
Furthermore, the inner peripheries of left inner plates 74L, which are arranged alternately with the left outer plates 72L, are fixed to the outer periphery of one end of the front left axle 12L.

前記アウタケース68内には、これら右側アウタプレー
ト72R及び左側アウタプレート72Lと右側インナプ
レート74R及び左側インナプレート74Lとが浸され
るように、粘性流体76が充填されている。
A viscous fluid 76 is filled in the outer case 68 so that the right outer plate 72R, the left outer plate 72L, the right inner plate 74R, and the left inner plate 74L are immersed.

これにより、前記アウタケース68の中央アウタケース
68Cの右側アウタケース68R側と、右側アウタケー
ス68Rと、右側アウタプレート72Rと、右側インナ
プレート74Rと、粘性流体76とによって、右側粘性
継手56Rを構成している。また、前記アウタケース6
8の中央アウタケース68Cの左側アウタケース68L
側と、左側アウタケース68Lと、左側アウタプレート
72Lと、左側インナプレート74Lと、粘性流体76
とによって、左側粘性継手56Lを構成している。
As a result, the right side viscous joint 56R is constituted by the right side outer case 68R side of the central outer case 68C of the outer case 68, the right side outer case 68R, the right side outer plate 72R, the right side inner plate 74R, and the viscous fluid 76. are doing. Further, the outer case 6
8, left outer case 68L of center outer case 68C
side, the left outer case 68L, the left outer plate 72L, the left inner plate 74L, and the viscous fluid 76.
These constitute a left viscous joint 56L.

また、前部差動機構10には、切換機構78が設けられ
ている。切換機構78は、第4・5図に示す如く、切換
スリーブ80を有している。切換スリーブ80の内方に
は、前記前部右側ハウジング60Rの側部及び外周の等
角度位置に形成された扇状の開口部66に対応する位置
に、前記右側アウタケース68Rの外周に形成したアウ
タケース側スプライン70と保合・離脱するスリーブ側
スプライン82が形成されている。この切換スリーブ8
0の外周には、スリーブ溝84が形成されている。スリ
ーブ清84には、切換フォーク86が慴動可能に係合し
ている。
Further, the front differential mechanism 10 is provided with a switching mechanism 78. The switching mechanism 78 includes a switching sleeve 80, as shown in FIGS. 4 and 5. Inside the switching sleeve 80, there is an outer cover formed on the outer periphery of the right outer case 68R at a position corresponding to the fan-shaped opening 66 formed at equiangular positions on the side and outer periphery of the front right outer housing 60R. A sleeve-side spline 82 is formed which engages and separates from the case-side spline 70. This switching sleeve 8
A sleeve groove 84 is formed on the outer periphery of the sleeve. A switching fork 86 is slidably engaged with the sleeve cover 84.

切換フォーク86は、切換シャフト88の一端側に固設
されている。切換シャフト88は、前記変速機第2ケー
シング64bに設けた保持部90に軸方向に慴動可能に
保持して設けられている。
The switching fork 86 is fixed to one end side of the switching shaft 88. The switching shaft 88 is held in a holding portion 90 provided in the second transmission casing 64b so as to be movable in the axial direction.

切換シャフト88の他端側には、係合窪部92が形成さ
れている。この保合窪部92には、作動レハ94の回動
先端側に設けた係合突部96が係合されている。作動レ
バ94の回動基端側は、作動シャフト98の一端側に固
設されている。作動シャフト98は、両端側を変速機第
2ケーシング64b内外に夫々突出させて、前記変速機
第2ケーシング64bに設けた支持部100に回動可能
に支持して設けている。前記作動レバ94は、作動シャ
フト98の変速機第2ケーシング64b内の一端側に固
設されている。また、作動シャフト98の変速機第2ケ
ーシング64b外の他端側には、切換レバ102が取付
けられている。この切換レバ102は、手動により、あ
るいは、図示しない駆動部により動作される。
An engagement recess 92 is formed at the other end of the switching shaft 88 . An engaging protrusion 96 provided on the rotating tip side of the actuating layer 94 is engaged with the engaging recess 92 . The rotation base end side of the actuation lever 94 is fixed to one end side of the actuation shaft 98. The operating shaft 98 has both ends protruding in and out of the second transmission casing 64b, and is rotatably supported by a support portion 100 provided in the second transmission casing 64b. The operating lever 94 is fixed to one end of the operating shaft 98 inside the second transmission casing 64b. Further, a switching lever 102 is attached to the other end of the operating shaft 98 outside the transmission second casing 64b. This switching lever 102 is operated manually or by a drive unit (not shown).

これにより、切換レバ102を矢印A方向に動作させる
ことにより作動シャフト98を回転させ、作動レバ94
を揺動させて切換シャフト8日を軸方向に慴動させ、切
換フォーク86を第2図の実線に示す位置に移動させる
と、切換スリーブ80のスリーブ側スプライン82が前
部差動右側ハウジング60Rの側部及び外周の等角度位
置に形成された扇状の開口部66から前部差動右側ハウ
ジング60R内に挿入され、前記右側アウタケース68
Rの外周に形成したアウタケース側スプライン70に係
合される。このため、前部差動ハウジング60と7ウタ
ケース68とは、一体となって回転するので、4輪駆動
状態に切換られる。
Thereby, by operating the switching lever 102 in the direction of arrow A, the operating shaft 98 is rotated, and the operating lever 94 is rotated.
When the switching shaft 8 is moved in the axial direction by swinging, and the switching fork 86 is moved to the position shown by the solid line in FIG. The right outer case 68 is inserted into the front differential right housing 60R through fan-shaped openings 66 formed at equal angular positions on the side and outer circumference of the right outer case 68.
It is engaged with an outer case side spline 70 formed on the outer periphery of R. Therefore, the front differential housing 60 and the outer case 68 rotate together, so that the four-wheel drive state is switched.

また、切換レバ102を矢印B方向に動作させることに
より作動シャフト98を回転させ、作動レバ94を揺動
させて切換シャフト88を軸方向に慴動させ、切換フォ
ーク86を第2図の破線に示す位置に移動させると、切
換スリーブ80のスリーブ側スプライン82が前部差動
右側ハウジング60Rの側部及び外周の等角度位置に形
成された扇状の開口部66から前部差動右側ハウジング
60R外に抜出され、前記右側アウタケース68Rの外
周に形成したアウタケース側スプライン70から離脱さ
れる。このため、前部差動ハウジング60とアウタケー
ス68とは、別体となって相対回転可能になるので、2
輪駆動状態に切換られる。
Further, by operating the switching lever 102 in the direction of arrow B, the operating shaft 98 is rotated, and the operating lever 94 is swung to move the switching shaft 88 in the axial direction, and the switching fork 86 is moved along the broken line in FIG. When the switching sleeve 80 is moved to the position shown, the sleeve-side spline 82 of the switching sleeve 80 moves from the fan-shaped opening 66 formed at equal angular positions on the side and outer circumference of the front differential right housing 60R to the outside of the front differential right housing 60R. It is pulled out and separated from the outer case side spline 70 formed on the outer periphery of the right outer case 68R. Therefore, the front differential housing 60 and the outer case 68 are separate bodies and can rotate relative to each other.
Switched to wheel drive mode.

前記後部差動機構22は、後部終減速機構20の後部P
.減速小歯車52に噛合する後部P:減速大歯車54を
後部差動機構22の後部差動ハウジング104に固設し
ている。後部差動ハウジング104は、後部車軸ハウジ
ング106に後部差動右側軸受108R及び後部差動左
側軸受108Lにより軸支されている。後部差動ハウジ
ン104内には、差動歯車列5日が設けられている。差
動歯車列58は、歯車軸110により軸支された後部差
動第1小歯車112a及び後部差動第2小歯車112b
と、これら後部差動第1小歯車112a及び後部差動第
2小歯車112bに夫々噛合する後部差動大歯車114
である後部差動右側大歯車114R及び後部差動左側大
歯車114Lとから構成されている。
The rear differential mechanism 22 is a rear terminal P of the rear final reduction mechanism 20.
.. A rear part P meshing with the small reduction gear 52: A large reduction gear 54 is fixed to the rear differential housing 104 of the rear differential mechanism 22. The rear differential housing 104 is pivotally supported by the rear axle housing 106 by a rear differential right bearing 108R and a rear differential left bearing 108L. A differential gear train 5 is provided within the rear differential housing 104. The differential gear train 58 includes a first rear differential pinion 112a and a second rear differential pinion 112b that are pivotally supported by a gear shaft 110.
and a rear differential large gear 114 that meshes with the first rear differential pinion 112a and the second rear differential pinion 112b, respectively.
It is composed of a rear differential right-hand large gear 114R and a rear differential left-hand large gear 114L.

後部差動右側大歯車114R及び後部差動左側大歯車1
14Lには、前記後部右側車軸24R及び後部左側車軸
24Lの一端側が夫々連結されるとともに、これら後部
右側車軸24R及び後部左側車軸24Lの他端側に前記
後部右側車輪26R及び後部左側車輪26Lが取付けら
れている。
Rear differential right large gear 114R and rear differential left large gear 1
One end side of the rear right axle 24R and the rear left axle 24L are connected to the rear right axle 24R and the rear left axle 24L, respectively, and the rear right wheel 26R and the rear left wheel 26L are attached to the other end sides of the rear right axle 24R and the rear left axle 24L, respectively. It is being

次に作用を説明する。Next, the action will be explained.

4輪駆動車2の前方に載置した内燃機関4の駆動力は、
クラッチ機構28を介して変速機6の入力軸30に入力
され、変速歯車列32により所望のトルク・回転数に変
換されて出力軸34から取出される。この出力軸34か
ら取出される駆動力は、前部終滅速機構8の前部終滅速
小歯車36とこの前部柊滅速小歯車36に噛合する前部
終減速大歯車38とにより減速されて前部差動機構lO
に伝達され、この前部差動機構10により前部右側車軸
,12R及び前部左側車軸12Lに夫々伝達され、前部
右側車輪14R及び前部左側車輪l4Lを夫々駆動する
The driving force of the internal combustion engine 4 mounted in the front of the four-wheel drive vehicle 2 is
It is inputted to the input shaft 30 of the transmission 6 via the clutch mechanism 28, converted to desired torque and rotational speed by the speed change gear train 32, and taken out from the output shaft 34. The driving force taken out from the output shaft 34 is generated by the front final speed small gear 36 of the front final speed mechanism 8 and the front final reduction large gear 38 that meshes with the front final speed small gear 36. The speed is reduced and the front differential mechanism lO
The front differential mechanism 10 transmits the signal to the front right axle 12R and the front left axle 12L, respectively, to drive the front right wheel 14R and the front left wheel l4L, respectively.

このとき、切換機構78の切換レバ102を矢印A方向
に動作させることにより作動シャフト98を回転させ、
作動レバ94を揺動させて切換シャフト88を軸方向に
摺動させ、切換フォーク86を第2図の実線に示す位置
に移動させると、切換スリーブ80のスリーブ側スプラ
イン82が右側アウタケース68Rの外周に形成したア
ウタケース側スプライン70に係合される。このため、
前部差動ハウジング60とアウタケース68とは、一体
となって回転するので、4輪駆動状態に切換られる。
At this time, the operating shaft 98 is rotated by operating the switching lever 102 of the switching mechanism 78 in the direction of arrow A,
When the operating lever 94 is swung to slide the switching shaft 88 in the axial direction and the switching fork 86 is moved to the position shown by the solid line in FIG. It is engaged with an outer case side spline 70 formed on the outer periphery. For this reason,
Since the front differential housing 60 and the outer case 68 rotate together, the four-wheel drive state can be switched.

この4輪駆動状態において、前部右側車輪14R及び前
部左側車輪14Lと後部左側車輪26R及び後部左側車
輪26Lとの間に回転数差がない場合に、前部差動機構
10は、右側粘性継手56Rの右側アウタプレート72
R及び右側インナプレート74R間にも回転数差が生ぜ
ず、また、左側粘性継手56Lの左側アウタプレート7
2L及び左側インナプレート74L間にも回転数差が生
じないことにより、前部右側車軸12R及び前部左側車
軸12Lに駆動力が伝達されず、前部右側車輪14R及
び前部左側車輪14Lは駆動されない。
In this four-wheel drive state, if there is no rotational speed difference between the front right wheel 14R and front left wheel 14L and the rear left wheel 26R and rear left wheel 26L, the front differential mechanism 10 Right side outer plate 72 of joint 56R
There is no rotation speed difference between R and the right inner plate 74R, and the left outer plate 7 of the left viscous joint 56L
Since there is no rotation speed difference between the inner plate 2L and the left inner plate 74L, the driving force is not transmitted to the front right axle 12R and the front left axle 12L, and the front right wheel 14R and the front left wheel 14L are not driven. Not done.

しかし、急発進や前部右側車輪14R及び前部右側車輪
14Lと後部左側車輪26R及び後部左側車輪26Lと
に対する路面μの違い等により前部右側車輪14R及び
前部左側車輪14Lと後部右側車輪26R及び後部左側
車輪26Lとの間に回転数差が生じた場合に、前部差動
機構10は、右側粘性継手56Rの右側アウタプレート
72R及び右側インナプレート7 4R間にも回転数差
が生じ、また、左側粘性継手56Lの左側アウタプレー
ト72L及び左側インナプレート7 4L間にも回転数
差が生じることにより、前部右側車軸12R及び前部左
側車軸12Lに駆動力が伝達され、前部右側車輪14R
及び前部左側車輪14Lは駆動されることになる。
However, due to a sudden start, a difference in road surface μ between the front right wheel 14R, the front right wheel 14L, the rear left wheel 26R, and the rear left wheel 26L, etc., the front right wheel 14R, the front left wheel 14L, and the rear right wheel 26R When a rotational speed difference occurs between the front differential mechanism 10 and the rear left wheel 26L, a rotational speed difference also occurs between the right outer plate 72R and the right inner plate 74R of the right viscous joint 56R. Furthermore, since a difference in rotational speed occurs between the left outer plate 72L and the left inner plate 74L of the left viscous joint 56L, driving force is transmitted to the front right axle 12R and the front left axle 12L, and the front right wheel 14R
And the front left wheel 14L is driven.

一方、内燃機関2の駆動力は、前部終減速機構8から駆
動力分配機構16により分配されて推進軸18に伝達さ
れ、後部終減速機構20から後部差動機構22の差動歯
車列58を介して後部右側車軸24R及び後部左側車軸
24Lに伝達されることにより、後部右側車輪26R及
び後部左側車輪26Lは直接的に駆動されることになる
On the other hand, the driving force of the internal combustion engine 2 is distributed from the front final reduction mechanism 8 by the driving force distribution mechanism 16 and transmitted to the propulsion shaft 18, and from the rear final reduction mechanism 20 to the differential gear train 58 of the rear differential mechanism 22. The rear right wheel 26R and the rear left wheel 26L are directly driven by being transmitted to the rear right axle 24R and the rear left axle 24L via.

このため、前置き内燃機関前部車輪駆動方式の車両を基
にした4輪駆動車2における後部右側車輸26R及び後
部左側車輸26Lへの駆動力伝達不足を改善することが
でき、前置き内燃機関後部車輪駆動方式の車両を基にし
た4輪駆動車と同等の走破性能を発揮し得て、走行性能
や安全性を向上することができる。
Therefore, it is possible to improve the insufficient transmission of driving force to the rear right side vehicle 26R and the rear left side vehicle 26L in the four-wheel drive vehicle 2 based on a front wheel drive vehicle with a front internal combustion engine. It can exhibit running performance equivalent to a four-wheel drive vehicle based on a rear wheel drive vehicle, and can improve running performance and safety.

また、前部差動機構10を粘性継手56によって構成す
るため、従来の前置き内燃機関前部車輪駆動方式の車両
を基にしたいわゆるパートタイムの4輪駆動車の駆動力
伝達系を比較的少ない変更でいわゆるフルタイムの4輪
駆動車とすることができ、しかも、従来の推進軸部位に
粘性継手を設ける場合と異なり、粘性継手の設置スペー
スを要せず、前部差動機構の設置スペースを利用してい
ることにより、コンパクト化・コストの低減を果すこと
ができる。
In addition, since the front differential mechanism 10 is constituted by the viscous joint 56, the drive power transmission system of a so-called part-time four-wheel drive vehicle based on a conventional front-mounted internal combustion engine front wheel drive vehicle is relatively small. By changing it, you can make it a so-called full-time four-wheel drive vehicle, and unlike the conventional case where a viscous joint is installed on the propulsion shaft, there is no need for installation space for a viscous joint, and there is no installation space for a front differential mechanism. By using , it is possible to achieve downsizing and cost reduction.

さらに、比較的重量の大なる粘性継手56を比較的回転
速度の低い前部差動機構10部位に設置しているので振
動面でも有利であり、また、トランスアクスルの潤滑油
を利用して粘性継手を冷却することができる。
Furthermore, since the viscous joint 56, which is relatively heavy, is installed in the front differential mechanism 10, which has a relatively low rotational speed, it is advantageous in terms of vibration. The joint can be cooled.

更にまた、切換機構78の切換レバ102を矢印B方向
に動作させることにより作動シャフト98を回転させ、
作動レバ94を揺動させて切換シャフト88を軸方向に
摺動させ、切換フォーク86を第2図の破線に示す位置
に移動させると、切換スリーブ80のスリーブ側スプラ
イン82が右側アウタケース68Rの外周に形成したア
ウタケース側スプライン70から離脱される。このため
、前部差動ハウジング60とアウタケース68とは、別
体となって相対回転可能になるので、2輪駆動状態に切
換られる。
Furthermore, by operating the switching lever 102 of the switching mechanism 78 in the direction of arrow B, the operating shaft 98 is rotated,
When the operating lever 94 is swung to slide the switching shaft 88 in the axial direction and the switching fork 86 is moved to the position shown by the broken line in FIG. It is separated from the outer case side spline 70 formed on the outer periphery. Therefore, the front differential housing 60 and the outer case 68 become separate bodies and can rotate relative to each other, so that the two-wheel drive state is switched.

このように、切換機構78によって2輪駆動状態と4輪
駆動状態とに切換えられることにより、車検や整備時等
に4輪駆動状態から2輪駆動状態に簡単に切換操作でき
、また、その機構の一部を粘性継手に設けることにより
、部品点数を削減し得て、コスト低減に寄与し得る。
As described above, by switching between the two-wheel drive state and the four-wheel drive state by the switching mechanism 78, it is possible to easily switch from the four-wheel drive state to the two-wheel drive state at the time of vehicle inspection or maintenance. By providing a part of the viscous joint in the viscous joint, the number of parts can be reduced, which can contribute to cost reduction.

さらに、前記切換機構78を駆動部により動作させる構
成とすれば、アンチロックブレーキシステムを備えた4
輪駆動車におけるアンチロックブレーキシステム作動時
の4輪駆動状態との整合性を図ることができ、実用上有
利である。
Furthermore, if the switching mechanism 78 is configured to be operated by a drive section, a four-wheel drive system equipped with an anti-lock brake system may be used.
It is possible to achieve consistency with the four-wheel drive state when the anti-lock brake system is activated in a wheel drive vehicle, which is advantageous in practice.

〔発明の効果〕〔Effect of the invention〕

このように、この発明によれば、前部差動機構を粘性継
手により構成したことにより、前部車輪と後部車輪との
間に回転数差がない場合に、粘性継手は内燃機関の駆動
力を前部車軸に伝達しないので前部車輪は駆動されず、
急発進や前部車輪及び後部車輪に対する路面のμの違い
等により前部車輪と後部車輪との間に回転数差が生じた
場合にのみ粘性継手は内燃機関の駆動力を伝達して前部
車輪は駆動されることになる。一方、後部差動機構を差
動歯車列により構成したことにより、内燃機関の駆動力
は後部差動機構の差動歯車列を介して後部車軸に伝達さ
れることとなり、後部車輪は直接的に駆動されるこ・と
になる。
As described above, according to the present invention, the front differential mechanism is configured with a viscous joint, so that when there is no difference in rotational speed between the front wheels and the rear wheels, the viscous joint reduces the driving force of the internal combustion engine. is not transmitted to the front axle, so the front wheels are not driven.
The viscous joint transmits the driving force of the internal combustion engine to the front wheels only when there is a difference in rotational speed between the front wheels and the rear wheels due to a sudden start or a difference in the μ of the road surface for the front and rear wheels. The wheels will be driven. On the other hand, by configuring the rear differential mechanism with a differential gear train, the driving force of the internal combustion engine is transmitted to the rear axle via the differential gear train of the rear differential mechanism, and the rear wheels are directly It will be driven.

このため、前置き内燃機関前部車輪駆動方式の車両を基
にした4輪駆動車における後部車輪への駆動力伝達不足
を改善し得て、前置き内燃機関後部車輪駆動方式の車両
を基にした4輪駆動車と同等の走破性能を発揮し得て、
走行性能や安全性を向上することができる。
Therefore, it is possible to improve the insufficient power transmission to the rear wheels in a four-wheel drive vehicle based on a vehicle with a front-mounted internal combustion engine and rear wheel drive system. It can demonstrate the same running performance as a wheel drive vehicle,
Driving performance and safety can be improved.

また、前部差動機構を粘性継手によって構成するため、
従来の前置き内燃機関前部車輪駆動方式の車両を基にし
たいわゆるパートタイムの4輪駆動車の駆動力伝達系を
比較的少ない変更でいわゆるフルタイムの4輪駆動車と
することができ、しかも、従来の推進軸部位に粘性継手
を設ける場合と異なり、粘性継手の設置スペースを要せ
ず、前部差動機構の設置スペースを利用していることに
よりコンパクト化・コストの低減を果し得る。
In addition, since the front differential mechanism is configured with a viscous joint,
The drive power transmission system of a so-called part-time four-wheel drive vehicle based on a conventional front-mounted internal combustion engine front-wheel drive vehicle can be made into a so-called full-time four-wheel drive vehicle with relatively few changes. , unlike the conventional case where a viscous joint is installed on the propulsion shaft, no installation space is required for the viscous joint, and by using the installation space of the front differential mechanism, it is possible to achieve compactness and cost reduction. .

さらに、比較的重量の大なる粘性継手を比較的回転速度
の低い前部差動機構部位に設置しているので振動面でも
有利であり、また、トランスアクスルの潤滑油を利用し
て粘性継手を冷却することができる。
Furthermore, since the viscous joint, which is relatively heavy, is installed in the front differential mechanism part where the rotation speed is relatively low, it is advantageous in terms of vibration. Can be cooled.

更にまた、切換機構によって2輪駆動状態と4輪駆動状
態とに切換えられる構成とすれば、車検や整備時等に4
輪駆動状態から2輪駆動状態に簡単に切換操作でき、ま
た、その機構の一部を粘性継手に設けることにより、部
品点数を削減し得て、コスト低減に寄与し得る。さらに
、この切換機構を駆動部により動作させる構成とすれば
、アンチロックブレーキシステムを備えた4輪駆動車に
おけるアンチロックブレーキシステム作動時の4輪駆動
状態との整合性を図ることができ、実用上有利である。
Furthermore, if the configuration is such that the switching mechanism can switch between the two-wheel drive state and the four-wheel drive state, the four-wheel drive state can be switched during vehicle inspection or maintenance.
It is possible to easily switch from the wheel drive state to the two-wheel drive state, and by providing part of the mechanism in the viscous joint, the number of parts can be reduced, contributing to cost reduction. Furthermore, if this switching mechanism is configured to be operated by the drive unit, consistency with the 4-wheel drive state when the anti-lock brake system is activated in a 4-wheel drive vehicle equipped with an anti-lock brake system can be achieved, making it practical. It is advantageous.

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

第1〜6図はこの発明の実施例を示し、第1図は駆動力
伝達系の概略説明図、第2図は前部差動機構部位の拡大
説明図、第3図は前部差動機構ケーシングの側面図、第
4図は切換スリーブの側面■、第5図は切換機構の正面
図、第6図は4輪駆動車の駆動力伝達系の概略平面図で
ある。 第7〜10図は従来例を示し、第7図は変速機と前部差
動機構と駆動力分配機構との概略説明図、第8〜10図
は夫々4輪駆動車の駆動力伝達系の概略平面図である。 図において、2は4輪駆動車、4は内燃機関、6は変速
機、8は前部終減速機、10は前部差動機構、12Rは
前部右側車軸、12Lは前部左側車軸、14Rは前部右
側車輪、14Lは前部左側車輪、16は駆動力変換機構
、18は推進軸、20は後部終減速機構、22は後部差
動機構、24Rは後部右側車軸、24Lは後部左側車軸
、26Rは後部右側車輪、26Lは前部右側車輪、56
は粘性継手、58は差動歯車列、78は切換機構である
。 図面の浄書
1 to 6 show embodiments of the present invention, FIG. 1 is a schematic diagram of the driving force transmission system, FIG. 2 is an enlarged diagram of the front differential mechanism, and FIG. 3 is the front differential mechanism. 4 is a side view of the switching sleeve, FIG. 5 is a front view of the switching mechanism, and FIG. 6 is a schematic plan view of the driving force transmission system of a four-wheel drive vehicle. Figures 7 to 10 show a conventional example, Figure 7 is a schematic explanatory diagram of a transmission, front differential mechanism, and driving force distribution mechanism, and Figures 8 to 10 are respective driving force transmission systems of a four-wheel drive vehicle. FIG. In the figure, 2 is a four-wheel drive vehicle, 4 is an internal combustion engine, 6 is a transmission, 8 is a front final reduction gear, 10 is a front differential mechanism, 12R is a front right axle, 12L is a front left axle, 14R is the front right wheel, 14L is the front left wheel, 16 is the driving force conversion mechanism, 18 is the propulsion shaft, 20 is the rear final reduction mechanism, 22 is the rear differential mechanism, 24R is the rear right axle, 24L is the rear left side Axle, 26R is rear right wheel, 26L is front right wheel, 56
58 is a differential gear train, and 78 is a switching mechanism. engraving of drawings

Claims (1)

【特許請求の範囲】[Claims] 1、前方に載置した内燃機関の駆動力を前部差動機構を
介して前部車軸に伝達し前部車輪を駆動するとともに駆
動力分配機構により分配した前記内燃機関の駆動力を後
部差動機構を介して後部車軸に伝達し後部車輪を駆動す
る4輪駆動車において、前記前部差動機構を粘性継手に
より構成するとともに前記後部差動機構を差動歯車列に
より構成したことを特徴とする4輪駆動車の駆動力伝達
装置。
1. The driving force of the internal combustion engine mounted at the front is transmitted to the front axle via the front differential mechanism to drive the front wheels, and the driving force of the internal combustion engine is distributed by the driving force distribution mechanism to the rear differential. A four-wheel drive vehicle in which transmission is transmitted to a rear axle via a dynamic mechanism to drive rear wheels, characterized in that the front differential mechanism is configured by a viscous joint, and the rear differential mechanism is configured by a differential gear train. A driving force transmission device for four-wheel drive vehicles.
JP11071389A 1989-04-28 1989-04-28 Driving force transmission device for four-wheel drive vehicle Expired - Fee Related JP2906249B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP11071389A JP2906249B2 (en) 1989-04-28 1989-04-28 Driving force transmission device for four-wheel drive vehicle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP11071389A JP2906249B2 (en) 1989-04-28 1989-04-28 Driving force transmission device for four-wheel drive vehicle

Publications (2)

Publication Number Publication Date
JPH02290724A true JPH02290724A (en) 1990-11-30
JP2906249B2 JP2906249B2 (en) 1999-06-14

Family

ID=14542583

Family Applications (1)

Application Number Title Priority Date Filing Date
JP11071389A Expired - Fee Related JP2906249B2 (en) 1989-04-28 1989-04-28 Driving force transmission device for four-wheel drive vehicle

Country Status (1)

Country Link
JP (1) JP2906249B2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7309301B2 (en) 2005-10-21 2007-12-18 Ford Global Technologies, Llc Transaxle having a differential mechanism and on-demand transfer clutch
US7448977B2 (en) 2005-10-21 2008-11-11 Ford Global Technologies, Llc Motor vehicle transaxle having a differential mechanism controlled by an on-demand clutch

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9045014B1 (en) 2012-03-26 2015-06-02 Oshkosh Defense, Llc Military vehicle
USD966958S1 (en) 2011-09-27 2022-10-18 Oshkosh Corporation Grille element

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7309301B2 (en) 2005-10-21 2007-12-18 Ford Global Technologies, Llc Transaxle having a differential mechanism and on-demand transfer clutch
US7448977B2 (en) 2005-10-21 2008-11-11 Ford Global Technologies, Llc Motor vehicle transaxle having a differential mechanism controlled by an on-demand clutch

Also Published As

Publication number Publication date
JP2906249B2 (en) 1999-06-14

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