JPH034037A - Front-wheel drive gear for power vehicle - Google Patents
Front-wheel drive gear for power vehicleInfo
- Publication number
- JPH034037A JPH034037A JP13869089A JP13869089A JPH034037A JP H034037 A JPH034037 A JP H034037A JP 13869089 A JP13869089 A JP 13869089A JP 13869089 A JP13869089 A JP 13869089A JP H034037 A JPH034037 A JP H034037A
- Authority
- JP
- Japan
- Prior art keywords
- wheel drive
- driven cam
- ring body
- front wheel
- unit
- 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
Links
- 238000005096 rolling process Methods 0.000 claims 2
- 230000035939 shock Effects 0.000 abstract description 2
- 230000005540 biological transmission Effects 0.000 description 10
- 230000007423 decrease Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000033001 locomotion Effects 0.000 description 3
- 210000000078 claw Anatomy 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000001141 propulsive effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Landscapes
- Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
- Arrangement And Driving Of Transmission Devices (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野］
この発明は、農用トラクター等の動力車ｉｄ＋ｊのＡｒ
ｔ輪駆動装置に関する。[Detailed Description of the Invention] [Industrial Application Field] This invention provides an Ar
This invention relates to a T-wheel drive device.
［従来技術］
圃場内で農用トラクターを旋回させるとき、作業能率を
上げるためにも小半径で機体を旋回させることが望まし
い、また、地盤が軟弱なｔｉ！ｌＩｅ内で大きな推力を
得るためには二！！駆動よりも四輪駆動である方が良い
、このため、従来は、四輪駆動型トラクターにおいて、
前軸駆動系に高低連切換装置を設け、直進時には高低速
切換装置を低速状態となし、旋回時には高速側に切換え
て前輪の周速を上げ、旋回半径を小さくするように構成
した所謂倍速様構付のトラクターが出現した。[Prior Art] When turning an agricultural tractor in a field, it is desirable to turn the machine in a small radius in order to increase work efficiency. In order to obtain a large thrust in lIe, two! ! It is better to have four-wheel drive than a drive, so traditionally, in four-wheel drive tractors,
The front axle drive system is equipped with a high-low speed switching device, and when driving straight, the high-low speed switching device is set to low speed, and when turning, it is switched to the high speed side to increase the circumferential speed of the front wheels and reduce the turning radius, so-called double speed type. A built-in tractor appeared.
［発明が解決しようとするｌｌ１ｌ］
ところで、前記した従来装置にあっては、旋υ１時に前
輪の回転速度が増速されて機体の旋回半径が小さくなる
ものの、高低速切換装置が切換わるときにショックが発
生する不具合、あるいは耐記高低速切換装置が高速側に
切換えられたときに周速がにかった前輪が後１翰を引き
するようにして走行するため前輪で地面を引っ掻いて地
盤を荒すといった問題を有していたにの発明は前記した
問題点に鑑みて提案するものであって、以下のような技
術的手段を講じた。[ll1l to be solved by the invention] By the way, in the conventional device described above, the rotational speed of the front wheels is increased during turn υ1 and the turning radius of the aircraft becomes smaller, but when the high-low speed switching device switches When the high/low speed switching device is switched to the high speed side, the front wheels, which have a high circumferential speed, pull the rear wheel, causing the front wheels to scratch the ground. The invention was proposed in view of the above-mentioned problems, and the following technical measures were taken.
即ち、１輸３．３を駆動するドライブピニオン１８と同
期して回転する原動カムリング体４４と。That is, the driving cam ring body 44 rotates in synchronization with the drive pinion 18 that drives the motor 3.3.
；）；１輪ν動Φ由４５に回・耘自在に遊１在されてい
てｎｉｆ Ａ己原ｔＩｊカムリング体４４から回転ａ１
力を受けて回転する従動カム体４８と、従１）ノカム体
４８からの回ＪＰＪ−４’Ｊｊ力を受けて前輪駆動匈４
５に回転を伝える回転リング体４７とからなり、原動カ
ムリング体４４は従ｔａｆカム体４８に動力を伝達する
凸部５ｏとＵｊ力を伝達しない凹部５１とを夕Ｕえ、従
動力１１体４８は常時原動カムリング体４４に当接しが
ちに付勢して設けると共にこの従動カム体４８と回転リ
ング体４７には係脱可能で動力伝達可能な噛合歯６１．
６２を設け、この噛合歯６１．６２は前輪２，２の回転
が後輪３．３の回転よりも速くなるときは噛合歯６１．
６２が外れて後輪駆動の状態となり、遅くなると噛合歯
６１，６２が係合して四輪駆動状態となるような関係に
構成されていることを特徴とする動力車両の前輪駆動装
置とするものである。;); One wheel ν movement φ45 is freely rotatable and rotatable and rotates a1 from the cam ring body 44.
The driven cam body 48 rotates in response to the force, and the front wheel drive unit 4 receives the rotational force from the driven cam body 48.
The driving cam ring body 44 includes a convex portion 5o that transmits power to the slave cam body 48 and a concave portion 51 that does not transmit the Uj force to the driven force 11 body 48. are biased so as to be in constant contact with the driving cam ring body 44, and the driven cam body 48 and the rotary ring body 47 are provided with engaging teeth 61. that are removable and capable of transmitting power.
The meshing teeth 61.62 are provided with meshing teeth 61.62 when the rotation of the front wheels 2, 2 becomes faster than the rotation of the rear wheels 3.3.
A front wheel drive device for a power vehicle is characterized in that the front wheel drive device for a power vehicle is configured in such a relationship that when the gear teeth 62 are disengaged, a rear wheel drive condition is established, and when the gear is slowed down, the meshing teeth 61 and 62 are engaged, resulting in a four wheel drive condition. It is something.
［実施例およびその作用コ 以下、同面に基づいて、この発明の詳細な説明する。[Example and its operation code] Hereinafter, the present invention will be described in detail based on the same aspects.
まず、構成から説明すると、１はトラクターで走行装置
として機体の前後部に前輪２．２及び後４Ｑ３．３を備
え、機体１１１１部にはエンジン４を搭載し、その後部
にクラッチハウジング６を固着し。First, to explain the configuration, 1 is a tractor equipped with front wheels 2.2 and rear 4Q3.3 at the front and rear of the body as a traveling device, an engine 4 is mounted on the body 1111, and a clutch housing 6 is fixed to the rear part. death.
その後方に後述する変速装置を収容するミッションケー
ス５を７２けている。クラッチハウジング６の後部から
後方へ向けて回転自在に延出された出力＠８とミッショ
ンケース５から前方へ向けて軸架された入力軸１ｏとの
間にはユニバーサルジヨイント１１が着脱自在に連結さ
れている０入力軸１０の後端部にはギ−に７１２が一体
で設けられ、このギヤ１２は変速軸１４」二の入力ギヤ
１５と常時噛み合う、変速軸１４には１速用の摺動ギヤ
１６と２・３速用の摺動ギヤ１７が軸方向に摺動自在に
スプライン嵌合され、１速用摺動ギヤ１６はドライブピ
ニオン１８に回転自在にＭＷさ九た筒状のカウンターギ
ヤ２０の大径ギヤ２１に選択的に噛み合い、２・３速用
の摺動ギヤ１７の大径ギヤＬ７ａはカウンターギヤ２０
の中径ギヤ２２に噛み合う、前記変速軸１４に遊嵌され
た筒状の副変速用カウンターギヤ２３のＯｆ端部には内
歯２４と大径ギヤ２５が設けられ、内歯２４は摺動ギヤ
１７の小径ギヤ１７ｂと噛み合って３速を得る。また大
径ギヤ２５は前記カウンターギヤ２０の小径ギヤ２Ｇに
常時噛み合う。カウンターギヤ２３には大径ギヤ２５と
共に小径のギヤ２９が一体で設けられ、このギヤ２９は
ドライブピニオン１８にスプライン嵌合されている副変
速用摺動ギＡ１３１の大径ギヤ３２と選択的に噛み合う
、この摺ジノギヤ３１は前記カウンターギヤ２０の小径
ギヤ２６に噛み合う内歯３３がその前端部に設けられ、
内歯３３が小径ギヤ２Ｇに噛み合うと副変速（高）とな
り、摺動ギヤ８１がカウンターギヤ２３の小径ギヤ２９
に噛み合うと副変速（低）となる、３４はドライブピニ
オン１８の１′Ｊ「端側に固着された前輪υＪ力板取出
用ギヤであるにのギヤ３４は前輪駅間ｊ用のカウンター
シャフトに回転自由に遊嵌された大径ギヤ３９に噛み合
い、大径ギヤ３９の側面に設けられた爪３９ａは前記カ
ウンターシャフト３７にスプライン嵌合された慴動ギヤ
４０の爪４０ａと選択的に噛み合い、この爪３９．：１
．４０ａ同士が相互に噛み合うと前輪Ｆｇ動のための回
転動力が前輪駆動用カウンターシャフト３７に伝達され
る。Behind it is a 72-piece mission case 5 that houses a transmission, which will be described later. A universal joint 11 is removably connected between the output @ 8 rotatably extended rearward from the rear of the clutch housing 6 and the input shaft 1o mounted forward from the transmission case 5. A gear 712 is integrally provided at the rear end of the 0 input shaft 10, and this gear 12 always meshes with the input gear 15 of the transmission shaft 14. The moving gear 16 and the sliding gear 17 for 2nd and 3rd speeds are spline-fitted to be slidable in the axial direction. The large diameter gear L7a of the sliding gear 17 for 2nd and 3rd speeds selectively meshes with the large diameter gear 21 of the gear 20, and the large diameter gear L7a of the sliding gear 17 for 2nd and 3rd speeds is the counter gear 20
An internal tooth 24 and a large-diameter gear 25 are provided at the off end of the cylindrical auxiliary transmission counter gear 23 that is loosely fitted on the transmission shaft 14 and meshes with the medium-diameter gear 22, and the internal tooth 24 is a sliding gear. It meshes with the small diameter gear 17b of the gear 17 to obtain third speed. Further, the large diameter gear 25 is always meshed with the small diameter gear 2G of the counter gear 20. The counter gear 23 is integrally provided with a small diameter gear 29 together with a large diameter gear 25, and this gear 29 is selectively connected to the large diameter gear 32 of the auxiliary transmission sliding gear A131 spline-fitted to the drive pinion 18. The sliding gear 31 that meshes with the small diameter gear 26 of the counter gear 20 is provided with internal teeth 33 at its front end that mesh with the small diameter gear 26 of the counter gear 20.
When the internal teeth 33 mesh with the small diameter gear 2G, the sub-shift (high) occurs, and the sliding gear 81 becomes the small diameter gear 29 of the counter gear 23.
34 is a gear for taking out the front wheel υJ force plate fixed to the end side of the drive pinion 18. The gear 34 is a countershaft for the front wheel station j. A claw 39a provided on the side surface of the large diameter gear 39 is selectively engaged with a claw 40a of a sliding gear 40 spline-fitted to the countershaft 37. This nail 39.:1
．． When 40a are engaged with each other, the rotational power for front wheel Fg movement is transmitted to the front wheel drive countershaft 37.
このカウンターシャフト３７の前端部には断面コ字型で
前側が開口された回転ドラム４２がスプライン結合され
ている。回転ドラム４２の開［］側側周面には後述する
原動カムリング体４４が前後移動不能な状態で止着され
、 Ｍｉｉ輸駆動用カウンターシャフト３７側の回転動
力をこの原動力ムリング体４４に伝達すべく構成してい
る。４５は前記カウンターシャフト３７と同芯かつその
延長線上に設けられた前輪駆動軸であって、この前輪駆
動軸４５には回転リング体４７がスプライン嵌合されて
いる。前記原動カムリング体４４と回転リング体４７と
の間であって前輪駆動軸４５の同一軸芯上には従動カム
体４８がリニアベアリング４９を介して前後移動可能か
つ遊転自在に受けられている。原動カムリング体４４の
後端外周部には。A rotating drum 42 having a U-shaped cross section and an open front side is connected to the front end of the countershaft 37 by splines. A motive power cam ring body 44, which will be described later, is fixed to the circumferential surface of the open side of the rotating drum 42 in a state that it cannot move back and forth, and the rotational power of the Mii transportation drive countershaft 37 side is transmitted to the motive power cam ring body 44. It is structured as possible. A front wheel drive shaft 45 is provided coaxially with and on an extension of the countershaft 37, and a rotary ring body 47 is spline-fitted to the front wheel drive shaft 45. A driven cam body 48 is supported between the driving cam ring body 44 and the rotary ring body 47 and on the same axis of the front wheel drive shaft 45 via a linear bearing 49 so as to be movable back and forth and freely rotatable. . At the outer periphery of the rear end of the driving cam ring body 44.
従動カム体４８に回転動力を伝える傾斜面４４ａを有す
る凸部５０と１回転動力を伝達しない四部５１が交互に
設けられ、一方、対向する従動カム体４８側にも原動カ
ムリング体４４から回転動力を受ける傾斜受面４８ａと
、動力伝達に関与しない突状平坦部５５が交互に設けら
れている。また、前記原動カムリング体４４には逆回転
方向の回転動力を従動カム体４８に伝えるべく傾斜面４
４ｂが設けられ５対する従動カム体４８側にも動力を受
ける傾斜面４８ｂが設けられている。従動カム体４８の
外周部位に設けられた円形鍔部５７と回転ドラム４２の
内側面間にはスプリング６０が介装され、常時原動カム
リング体４４と従動カム体４８とが係合して正転あるい
は逆転方向の回転動力を従動カム体４８へ伝達するよう
に構成している。従動カム体４８と回転リング体４７の
対向する側の外周部位には回転動力を伝達する歯の断面
が台形状をなす噛合歯６１．６２が設けられ１両噛合歯
６１．６２が噛み合っているときは従動カム体４８の回
転が回転リング体４７に伝えられ、従動カム体４８が前
側へ僅かに移動してその噛合が解けると回転リング体４
７の回転が停止する関係に構成されている。即ち５回転
リング体４７が回転するときは前後１１＋！２，３とも
駆動される四輪駆動状態となり、回転リング体４７が停
止しているときには後軸３，３のみが駆動される二輪ｌ
ψ動の状態となる１図中符号６５は従動カム体４８に軽
い制動を与えるシールゴムで固定側の受部６６と従動カ
ム体４８の円筒部６８との間に介装されている。このシ
ールゴム６５の制動作用が強いときには前記原動カムリ
ング体４４側の傾斜面４４ａ、４４ｂの傾斜をきつくし
、制ｆｔＪｒ作用が弱いときには傾斜を浅くする。７０
は従動カム体４８の噛合歯６１と回転リング体４７の噛
合歯６２との噛合状態を保持するためのシフターであっ
て、このシフター７０を後方へ回動して従動カム体４８
の円筒部６８前部に配設されたスラストベアリング７１
を後方へ押すと従動カム体４８と回転リング体４７が常
時噛み合った状態を保持することができる。即ち、常時
四輪駆動状態となる。シフター７０の回動操作は図示外
の操作レバーで動かしてもよいが、ソレノイド等により
電気的に回動させる形態としてもよい。Convex portions 50 having sloped surfaces 44a that transmit rotational power to the driven cam body 48 and four portions 51 that do not transmit one rotational power are alternately provided, and on the other hand, rotational power is also transmitted from the driving cam ring body 44 to the opposing driven cam body 48 side. Receiving inclined receiving surfaces 48a and projecting flat portions 55 that do not participate in power transmission are alternately provided. The driving cam ring body 44 also has an inclined surface 44 for transmitting rotational power in the reverse rotation direction to the driven cam body 48.
4b is provided, and an inclined surface 48b that receives power is also provided on the side of the driven cam body 48 opposite to 5. A spring 60 is interposed between the circular flange 57 provided on the outer periphery of the driven cam body 48 and the inner surface of the rotating drum 42, so that the driving cam ring body 44 and the driven cam body 48 are constantly engaged to rotate in the normal direction. Alternatively, the rotational power in the reverse direction is transmitted to the driven cam body 48. Meshing teeth 61, 62, each of which transmits rotational power and has a trapezoidal cross section, are provided on the outer periphery of the opposing sides of the driven cam body 48 and the rotary ring body 47, and both meshing teeth 61, 62 mesh with each other. At this time, the rotation of the driven cam body 48 is transmitted to the rotating ring body 47, and when the driven cam body 48 moves slightly forward and its meshing is released, the rotating ring body 4
7 stops rotating. That is, when the 5-rotation ring body 47 rotates, 11+ in the front and back! The two wheels are in a four-wheel drive state in which both wheels 2 and 3 are driven, and when the rotating ring body 47 is stopped, only the rear axles 3 and 3 are driven.
Reference numeral 65 in FIG. 1, which is in the ψ motion state, is a seal rubber that provides light braking to the driven cam body 48 and is interposed between the receiving portion 66 on the fixed side and the cylindrical portion 68 of the driven cam body 48. When the braking action of the seal rubber 65 is strong, the slopes of the inclined surfaces 44a and 44b on the drive cam ring body 44 side are made steeper, and when the braking action of the seal rubber 65 is weak, the inclinations are made shallower. 70
is a shifter for maintaining the meshing state between the meshing teeth 61 of the driven cam body 48 and the meshing teeth 62 of the rotary ring body 47;
A thrust bearing 71 disposed at the front of the cylindrical portion 68 of
By pushing backward, the driven cam body 48 and the rotating ring body 47 can be kept in a state in which they are always engaged. In other words, the vehicle is always in four-wheel drive mode. The shifter 70 may be rotated by an operation lever not shown, but it may also be rotated electrically by a solenoid or the like.
なお、図中符号７５は操縦ハンドル、７６はフェンダ−
１７７はフロン１−アクスルハウジングである。フロン
トアクスルハウジング７７内には前軸デフ装置（図示省
略）が設けられ、前ｉｌ＋！駆動軸４５の回転動力が前
軸デフ装置に伝えられ、さらにフロン１−アクスルハウ
ジング７７内において水平横向きに回転軸架された即動
軸（図示省略）を介して前軸２．２を回転駆動する。In addition, the reference numeral 75 in the figure is a control handle, and 76 is a fender.
177 is a front 1-axle housing. A front axle differential device (not shown) is provided in the front axle housing 77, and the front il+! The rotational power of the drive shaft 45 is transmitted to the front shaft differential device, which further rotationally drives the front shaft 2.2 via a quick-acting shaft (not shown) mounted horizontally and horizontally within the front 1-axle housing 77. do.
次に上側の作用を説明する。まず、トラクター１を四Ｉ
！駆動の状態として圃場に乗り入れ、操縦ハンドル７５
を回動操作して機体を旋回させると、後軸３．３に押さ
れて前軸２，２は速く回転しようとする。すると、前輪
駆動軸４５と一体で回転している回転リング体４７に噛
み合っている従動カム体４８が原動カムリング体４４よ
りも速く回転される結果となり、動力を伝達している原
動カムリング体４４の傾斜面４４ａから従動カム体４８
の傾斜受面４８ａが離れ、従動カムリング体４４の円形
鍔部５７と回転ドラム４２間に介装されたスプリング６
０の抑圧作用を受けて、従動カム体４４の突状平坦部５
５が原動カムリング体４４の凹部５１内に収まる。この
ため、従動カム体４８と回転リング体４７との噛合が外
れ、回転リング体４７を固着している前輪駆動軸４５に
は動力が伝達されず、この瞬間二輪駆動の状態に切り換
えられる。そして、旋回の途中で前軸２．２の回転が落
ちてくると原動カムリング体４４の回転の方が速くなっ
て原動カムリング体４４の凸部に設けた傾斜面４４ａが
従動カム体４８の傾斜受面４８ａを押圧し、再びドライ
ブピニオン１８の回転と同期した回転動力が前輪駆動軸
４５に伝達される。Next, the operation of the upper side will be explained. First, tractor 1
! Enter the field as a driving state, and press the control handle 75.
When the machine is turned by rotating the front axle 3.3, the front axles 2, 2 try to rotate quickly due to the push of the rear axle 3.3. As a result, the driven cam ring 48 meshing with the rotating ring 47 rotating integrally with the front wheel drive shaft 45 rotates faster than the driving cam ring 44, causing the driving cam ring 44 transmitting power to rotate faster than the driving cam ring 44. From the inclined surface 44a to the driven cam body 48
The inclined receiving surface 48a of the spring 6 is separated, and the spring 6 interposed between the circular flange 57 of the driven cam ring body 44 and the rotating drum 42
0, the protruding flat portion 5 of the driven cam body 44
5 fits into the recess 51 of the driving cam ring body 44. As a result, the driven cam body 48 and the rotating ring body 47 are disengaged, no power is transmitted to the front wheel drive shaft 45 to which the rotating ring body 47 is fixed, and the state is switched to two-wheel drive at this moment. Then, when the rotation of the front shaft 2.2 decreases during turning, the rotation of the driving cam ring body 44 becomes faster, and the inclined surface 44a provided on the convex part of the driving cam ring body 44 becomes the slope of the driven cam body 48. By pressing the receiving surface 48a, rotational power synchronized with the rotation of the drive pinion 18 is again transmitted to the front wheel drive shaft 45.
なお、前記した作用の説明は機体が前進している場合で
あるが、機体が後進する場合は、原動カムリング体４４
の傾斜面４４ｂからｕ ｉｐ＋カム体４８の傾斜受面４
８Ｉ）へ回転動力が伝達される。この場合前輪２．２側
の回転が強制駆ＩＡノする側の回転よりも速くなると二
＠駆動の状態となり、前輪２．２の回転が落ちると再び
四ＩＩ＋！駆動の状態に切換えられるものである。Note that the above explanation of the action is based on the case where the aircraft is moving forward, but when the aircraft is moving backward, the driving cam ring body 44
from the inclined surface 44b of the u ip + inclined receiving surface 4 of the cam body 48
Rotational power is transmitted to 8I). In this case, when the rotation of the front wheel 2.2 side becomes faster than the rotation of the forced drive IA side, the state becomes 2 @ drive, and when the rotation of the front wheel 2.2 decreases, it returns to 4 II +! It can be switched to a driving state.
また、この発明に係る前輪駆動装置は機体が直進しでい
る場合においても有効に作用するものであって、下り坂
で１１１ｆ輸２．２の回転数が強制駆動力を受けて回転
する速さよりも大きくなるときは。Further, the front wheel drive system according to the present invention works effectively even when the aircraft is traveling straight, and the rotation speed of 111f x 2.2 on a downhill slope is faster than the rotation speed due to the forced driving force. When it gets bigger too.
二輪駆動状ｆふとなり、逆に（メリ坂で後ｅＱ３．３が
スリップを起こし、前輪２，２の回転数が所定の同転数
までダウンすると再び四＠駆動の状態に復帰して推進力
を向１−させる。When the rear eQ3.3 slips on a steep slope and the rotation speed of the front wheels 2 and 2 decreases to the predetermined same rotation speed, it returns to the four-wheel drive state and provides propulsion. Direction 1-.
第６図は第３図に記載した従動カム体４８の型状を変更
した変形例を示すものである。前輪駆動軸４５の大径部
８０に形成したスプライン溝部８１と従動カム体４８の
円筒部６８に設けた孔部８４間にスチールボール８２を
介在させてここにボールクラッチを構成し、内周にボー
ル抑圧面を有する円筒状のシフター８５を軸方向に移動
させることによってクラッチを入切する形態としている
。FIG. 6 shows a modification in which the shape of the driven cam body 48 shown in FIG. 3 is changed. A ball clutch is constructed by interposing a steel ball 82 between a spline groove 81 formed in the large diameter portion 80 of the front wheel drive shaft 45 and a hole 84 provided in the cylindrical portion 68 of the driven cam body 48. The clutch is turned on and off by moving a cylindrical shifter 85 having a ball suppressing surface in the axial direction.
クラッチを入状態に保持すると原動カムリング体４４の
回転動力は従動カム体４８に直接伝達されて常時四輪駆
動状態に保たれ、））ランチを切状態にすると、原動カ
ムリング体４７の回転動力は、従動カム体４８、回転リ
ング体４７を順次介して前輪駆動軸４５に伝達される。When the clutch is held in the engaged state, the rotational power of the driving cam ring body 44 is directly transmitted to the driven cam body 48, and the four-wheel drive state is maintained at all times. , the driven cam body 48, and the rotating ring body 47 in order to be transmitted to the front wheel drive shaft 45.
なお、」二記２つの実施例に記載された前ＩＩ＋！駆動
装置は、原動カムリング体４４と、従シＪカム体４８と
、回転リング体４７とからなり、これらは４；ｉ方が開
口した回転ドラム４２内に近接させて収納されているの
で前後方向及びＪ〕下方向の長さが短くなって全体的に
コンパクトに設計でき、この結髪、地−１−高も高くな
って畝を跨いで作業を行なうトラクターに最適となる。In addition, the previous II+! The drive device consists of a driving cam ring body 44, a slave J cam body 48, and a rotating ring body 47, which are housed close to each other in a rotating drum 42 whose 4; and J] The length in the downward direction is shortened so that the overall design can be made compact, and the height from the ground is also increased, making it ideal for tractors that work across ridges.
この発明は、＾？ｊ記の如く構成したので１次のような
作用・効果を奏する。This invention is ^? Since it is configured as described in J., it has the following first-order functions and effects.
即ち、後＠３．３をｌ［ｔｌ＋するドライブピニオン１
８と同期して回転する原動カムリング体４４と、前輪駆
ＩＥＩＪ軸４５に回転自在に遊嵌されていて前記原動カ
ムリング体４４から回転ω」力を受けて回転する従動カ
ム体４８と、従ｙｌＪカム体４８からの回転動力を受け
て前輪駆υＪ軸４５に回転を伝える回転リング体４７と
からなり、原動カムリング体４４は従動カム体４８に動
力を伝達する凸部５０と動力を伝達しない凹部５１とを
備え、従動カム体４８は常時原動カムリング体４４に当
接しがちに付勢して設けると共にこの従動カム体４８と
回転リング体４７には係脱可能で動力伝達可能な噛合歯
６１．６２を設け、この噛合にｉ ６１．６２は前輪２
．２の回転が後輪３．３の回転よりも速くなるときは噛
合歯６１．６２が外れて後輪駆動の状態となり、遅くな
ると噛合ｉ６１．６２が係合して四輪駆動状態となるよ
うな関係に構成されているので、機体の旋回時のように
前輪２．２が後軸３．３から押され戴味となる場合は前
記噛合歯６１．６２の係合が解かれて二軸駆動の状態に
なり、また、旋回途中で後軸３．３がスリップしたりし
て推進力の不足から眞ｆＱ２．２の回転数がダウンした
ようなときには再び噛合歯６１．６２が係合して四輪駆
動状態となるものであるから、常にルク：！正な回転動
力が前後＠２，２．３．３に伝達されることになり、倍
速機構奈設けた従来装７５のように高低速切換時にショ
ックを生じることもなく、機体を円滑に、かつ小半径で
旋回させることができる。In other words, the drive pinion 1 which makes the rear @3.3 l[tl+
a driving cam ring body 44 that rotates in synchronization with the driving cam ring body 44, a driven cam ring body 48 that is rotatably loosely fitted to the front wheel drive IEIJ shaft 45 and rotates by receiving a rotational force ω'' from the driving cam ring body 44; It consists of a rotating ring body 47 that receives rotational power from a cam body 48 and transmits rotation to the front wheel drive υJ shaft 45, and the driving cam ring body 44 has a convex portion 50 that transmits power to the driven cam body 48 and a concave portion that does not transmit power. 51, and the driven cam body 48 is always biased to be in contact with the driving cam ring body 44, and the driven cam body 48 and the rotary ring body 47 are provided with engaging teeth 61. 62 is provided, and i 61.62 is the front wheel 2.
．． When the rotation of the rear wheels 3 and 2 becomes faster than the rotation of the rear wheels 3 and 3, the meshing teeth 61 and 62 disengage, resulting in a rear wheel drive state, and when it slows down, the meshing teeth i61 and 62 engage, resulting in a four-wheel drive state. Therefore, when the front wheels 2.2 are pushed from the rear axle 3.3 as when the aircraft turns, the engagement of the meshing teeth 61, 62 is released and the two axles are rotated. When the engine is in a driving state and the rotational speed of the fQ2.2 decreases due to lack of propulsive force due to the rear axle 3.3 slipping during turning, the meshing teeth 61.62 engage again. Since it is in four-wheel drive mode, it is always in a four-wheel drive state. Positive rotational power is transmitted to the front and rear @ 2, 2, 3, 3, and unlike the conventional 75 equipped with a speed doubler mechanism, there is no shock when switching between high and low speeds, and the aircraft operates smoothly. Can be turned in a small radius.
図はこの発明の実施例をし、第１図は全体側面図、第２
図はミッション全体の側断面図、第３図は要部の拡大側
断面図、第４図は従動カム体４８と回転リング体４７と
が噛み合っている作用状態を示す断面図、第５図は噛み
合いが外れている作用状態を示す断面図、第６図は一部
を改良した伝動部の断面図である。
符号の説明
■ トラクター
２．２ 前輪
３．３ 後軸
１８ ドライブピニオン
４４ 原動カムリング体
４５ 前槽駆動軸
４７ 回転リング体
４８ 捉動カム体
６１．６２ 噛合歯The figures show an embodiment of the invention, with Figure 1 being an overall side view and Figure 2 being an overall side view.
The figure is a side sectional view of the entire transmission, FIG. 3 is an enlarged side sectional view of the main parts, FIG. 4 is a sectional view showing the operating state in which the driven cam body 48 and the rotating ring body 47 are engaged, and FIG. 5 is a sectional view of the transmission. FIG. 6 is a cross-sectional view showing a working state in which the mesh is disengaged, and FIG. 6 is a cross-sectional view of a partially improved transmission section. Explanation of symbols■ Tractor 2.2 Front wheel 3.3 Rear shaft 18 Drive pinion 44 Drive cam ring body 45 Front tank drive shaft 47 Rotating ring body 48 Capture moving cam body 61.62 Meshing tooth
Claims (1)
して回転する原動カムリング体４４と、前輪駆動軸４５
に回転自在に遊嵌されていて前記原動カムリング体４４
から同転動力を受けて回転する従動カム体４８と、従動
カム体４８からの同転動力を受けて前輪駆動軸４５に回
転を伝える回転リング体４７とからなり、原動カムリン
グ体４４は従動カム体４８に動力を伝達する凸部５０と
動力を伝達しない凹部５１とを備え、従動カム体４８は
常時原動カムリング体４４に当接しがちに付勢して設け
ると共にこの従動カム体４８と回転リング体４７には係
脱可能で動力伝達可能な噛合歯６１、６２を設け、この
噛合歯６１、６２は前輪２、２の回転が後輪３、３の回
転よりも速くなるときは噛合歯６１、６２が外れて後輪
駆動の状態となり、遅くなると噛合歯６１、６２が係合
して四輪駆動状態となるような関係に構成されているこ
とを特徴とする動力車両の前輪駆動装置。1) A driving cam ring body 44 that rotates in synchronization with the drive pinion 18 that drives the rear wheels 3, 3, and a front wheel drive shaft 45
The drive cam ring body 44 is rotatably loosely fitted into the drive cam ring body 44.
The driving cam ring body 44 consists of a driven cam body 48 that rotates by receiving the same rolling force from the driven cam body 48, and a rotating ring body 47 that receives the same rolling force from the driven cam body 48 and transmits rotation to the front wheel drive shaft 45. The driven cam body 48 is provided with a convex portion 50 that transmits power to the body 48 and a concave portion 51 that does not transmit power. The body 47 is provided with meshing teeth 61 and 62 that can be engaged and disengaged and that can transmit power. , 62 are disengaged to enter a rear wheel drive state, and when the gears slow down, meshing teeth 61 and 62 engage to enter a four-wheel drive state.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1138690A JP2560835B2 (en) | 1989-05-30 | 1989-05-30 | Front-wheel drive device for power vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1138690A JP2560835B2 (en) | 1989-05-30 | 1989-05-30 | Front-wheel drive device for power vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH034037A true JPH034037A (en) | 1991-01-10 |
| JP2560835B2 JP2560835B2 (en) | 1996-12-04 |
Family
ID=15227838
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1138690A Expired - Lifetime JP2560835B2 (en) | 1989-05-30 | 1989-05-30 | Front-wheel drive device for power vehicle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2560835B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8333154B2 (en) | 2007-08-09 | 2012-12-18 | Toyota Jidosha Kabushiki Kaisha | Inflator |
-
1989
- 1989-05-30 JP JP1138690A patent/JP2560835B2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8333154B2 (en) | 2007-08-09 | 2012-12-18 | Toyota Jidosha Kabushiki Kaisha | Inflator |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2560835B2 (en) | 1996-12-04 |
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