JPS63275430A - Power transmission device for tractor - Google Patents
Power transmission device for tractorInfo
- Publication number
- JPS63275430A JPS63275430A JP10942587A JP10942587A JPS63275430A JP S63275430 A JPS63275430 A JP S63275430A JP 10942587 A JP10942587 A JP 10942587A JP 10942587 A JP10942587 A JP 10942587A JP S63275430 A JPS63275430 A JP S63275430A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- differential
- input shaft
- pinion
- ring gear
- 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
- 230000005540 biological transmission Effects 0.000 title claims description 6
- 230000005484 gravity Effects 0.000 description 4
- 238000005495 investment casting Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000005520 cutting process Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000003754 machining Methods 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 150000003951 lactams Chemical class 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
- F16H2048/085—Differential gearings with gears having orbital motion comprising bevel gears characterised by shafts or gear carriers for orbital gears
Landscapes
- Motor Power Transmission Devices (AREA)
- Retarders (AREA)
Abstract
Description
【発明の詳細な説明】
（イ）産業上の利用分野
本発明は車輪式走行車両において左右の車軸間に配置す
る差動歯車装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION (a) Field of Industrial Application The present invention relates to a differential gear device disposed between left and right axles in a wheeled vehicle.
（ロ）従来技術
トラクターにおいて、前輪駆動ケース内の差動歯車装置
へ動力を入力する入力軸の位置を下方に配置することに
より、ｆｆ１ｆｆｉの大きなエンジンの位置を下方に移
し、重心の低い安定した１〜ラクターとすることは実開
昭５２−１４４５３１号で公知である。(b) In conventional tractors, by locating the input shaft that inputs power to the differential gear device in the front wheel drive case downward, the position of the large ff1ffi engine was moved downward, resulting in a stable and low center of gravity. It is known from Utility Model Application Publication No. 52-144531 that the number of lactams is 1 to 1.
また、当該公報には省略されているか差動装置は、左右
の車軸に係合する一対のデフリングギアとそれらに噛合
う一対のピニオンギアをデフケース内に収容し、入力軸
上のベベルギヤと噛合うデフリングギアを該デフケース
に固設するのが慣用技術である。Also, the differential device, which is omitted in the publication, houses a pair of differential ring gears that engage the left and right axles and a pair of pinion gears that mesh with them in a differential case, and meshes with a bevel gear on the input shaft. It is a common technique to securely attach a differential ring gear to the differential case.
（ハ）発明゛が解決しようとする問題点前記実開昭５２
−１４４５３１号では、前輪駆勅ケースに対し入力軸を
下方に下げる構成として、入力軸端のヘヘル−ＦＡ−と
デフリングギアにハイポイドへヘルギャを用いて行なっ
ているのである。(c) Problems to be solved by the invention
In No. 144531, the input shaft is lowered downward relative to the front wheel drive case, and this is done by using Heheru-FA- at the end of the input shaft and Hypoid Helga for the differential ring gear.
減速比を大きくとる手段として、ハイポイドベベルギヤ
用いることは有効ではあるが、素材を切削加工すること
により製作されるものである為製作コストが高くつき、
またギア噛合い精度も要求され、ジム調整などの調整手
段をデフケースと前輪駆動ケースとの軸受部において設
ける必要がある等の欠点を持っているのである。Although it is effective to use a hypoid bevel gear as a means of increasing the reduction ratio, the manufacturing cost is high because it is manufactured by cutting the material.
Furthermore, gear meshing precision is required, and adjustment means such as gym adjustment must be provided at the bearings of the differential case and the front wheel drive case.
また上記の如き差動歯車装置とした場合には、デフケー
スが大きな容積を占めるので、狭小な軸受間隔内に設置
する上で障害となり、デフケース内の潤滑も不充分で、
また各歯車を収容する為に２つ割りにする必要がある為
に製作費が高＜、組立・分解が面倒となっていたのであ
る。In addition, in the case of a differential gear device such as the one described above, the differential case occupies a large volume, which becomes an obstacle when installing within a narrow bearing spacing, and the lubrication inside the differential case is insufficient.
Furthermore, since it had to be divided into two parts to accommodate each gear, the manufacturing cost was high and assembly and disassembly were troublesome.
（ニ）問題を解決するための手段
本発明は以−りの不都合を解消して、差動歯車装置を製
作費が安価でかつ小型で耐久性の良いもとすると同時に
、機体に対するエンジンの位置を低くして低重心のトラ
クターを構成することが目的であり、次に該目的を達成
する為の構成を説明すると。(d) Means for Solving the Problems The present invention solves the above-mentioned disadvantages and makes the differential gear device inexpensive to manufacture, compact, and durable, and at the same time, the position of the engine with respect to the aircraft body can be improved. The purpose is to construct a tractor with a low center of gravity by lowering the center of gravity.Next, the configuration for achieving this purpose will be explained.
エンジンにより駆動される第１入力軸５の上段に第２入
力軸６を設け、減速山車列を介して連動連結すると共に
、第２人刃軸６端のヘールギヤ６ａとこれに噛合うデフ
リングギア８とをストレートベヘルギャにより構成し、
該デフリングギア８を椀状に形状してその端部をケース
側に軸支する一方、椀状の開口端面にピニオンギア２６
・２７を枢支するピニオンピン７の端部が係合される四
部８ａ・８ｂを形成し・たちのである。A second input shaft 6 is provided on the upper stage of the first input shaft 5 driven by the engine, and is interlocked and connected via a reduction gear train, and a differential ring gear 8 that meshes with a hel gear 6a at the end of the second human blade shaft 6 and is composed of straight behergya,
The differential ring gear 8 is shaped like a bowl and its end is pivotally supported on the case side, while a pinion gear 26 is provided on the open end surface of the bowl shape.
・It forms four parts 8a and 8b to which the ends of the pinion pin 7 that pivotally support the pinion pin 27 are engaged.
また、ピニオンピン７の中央部に、左右の車軸３Ｌ・３
Ｒを突き合せ状に支持する軸受部７ａを形成し、その両
端面をサイドギア２５Ｌ・２５Ｒの内側面に接当させた
ものである。In addition, the left and right axles 3L and 3 are placed in the center of the pinion pin 7.
A bearing portion 7a is formed to support R in an abutting manner, and both end surfaces of the bearing portion 7a are brought into contact with the inner surfaces of the side gears 25L and 25R.
（ホ）実施例
本発明の目的・構成は以上の如くであり、次に添付の図
面に示した実施例の構成を説明すると。(E) Embodiment The object and structure of the present invention are as described above. Next, the structure of the embodiment shown in the attached drawings will be explained.
第１図はトラクターの全体側面図、第２図は本発明の差
動歯車装置をｉ’Ｑ輪駆輪部動部いた実施例の側面断面
図、第３図は同じく後面断面図、第４図は差動歯車装置
のみを取り出した状態の側面図、第５図はリングギアゲ
ース８の斜視図、第６図はピニオンピン７の斜視図であ
る。Fig. 1 is an overall side view of the tractor, Fig. 2 is a side sectional view of an embodiment in which the differential gear device of the present invention is applied to the i'Q wheel drive section, Fig. 3 is a rear sectional view of the same, and Fig. 4 The figure is a side view of only the differential gear device taken out, FIG. 5 is a perspective view of the ring gear gauge 8, and FIG. 6 is a perspective view of the pinion pin 7.
まず第１図において本発明の差動歯車装置を前輪駆動部
に用いたトラクターの全体的な構成を説明すると。First, with reference to FIG. 1, the overall structure of a tractor using the differential gear device of the present invention in the front wheel drive section will be explained.
エンジンＥとミッションケースＭの左右の側面に固設し
て機体フレーム２２・２２を配置し、該機体フレーム２
２・２２を主たる機体支持部材としている。The fuselage frames 22 are fixedly installed on the left and right sides of the engine E and the mission case M, and the fuselage frames 2
2.22 is the main fuselage support member.
そしてエンジンＥの後面より突出したクランクシャフト
の後端にユニバーサルジヨイント軸１９を介装し、該ユ
ニバーサルジヨイント軸１９の後端を油圧ポンプＡの軸
に連結している。A universal joint shaft 19 is interposed at the rear end of the crankshaft protruding from the rear surface of the engine E, and the rear end of the universal joint shaft 19 is connected to the shaft of the hydraulic pump A.
ミッションケースＭの前面壁部より油圧ポンプ取付台２
を突出し、該油圧ポンプ取付台２により油圧ポンプＡを
支持し、口形に構成した油圧ポンプ取付台２の内部に主
クラツチ装置Ｂを配置している。Hydraulic pump mounting base 2 from the front wall of mission case M
The hydraulic pump A is supported by the hydraulic pump mounting base 2, and the main clutch device B is disposed inside the hydraulic pump mounting base 2 which is configured in the shape of a mouth.
またミッションケースＭの上面に油圧ケース２０を載置
して、該油圧ケース２０よりリフトアームを上下に回動
自在に突出しているのである。Further, a hydraulic case 20 is placed on the upper surface of the transmission case M, and a lift arm protrudes from the hydraulic case 20 so as to be freely rotatable up and down.
そして該油圧ポンプＡヘミッションケースＭ内のストレ
ーナ−より低圧パイプ９を介装し、高圧化された圧油は
高圧パイプ１０により油圧ケース２０に送油してリフト
アームの上昇に使用しているものである。A low-pressure pipe 9 is interposed from a strainer in the hemi-mission case M of the hydraulic pump A, and the high-pressure oil is sent to the hydraulic case 20 through the high-pressure pipe 10 and used to lift the lift arm. It is something.
また該ミッションケースＭの前方下部より前輪駆動軸装
置２３を突出して、前輪を駆動する動力を伝達している
のである。Further, a front wheel drive shaft device 23 protrudes from the front lower part of the transmission case M to transmit power for driving the front wheels.
該前輪駆動軸装置２３の先端が、フロント減速ケース４
と差動歯車装置を具備したフロントデフケースｌとの結
合された前輪駆動装置に動力を伝達しているのである。The tip of the front wheel drive shaft device 23 is connected to the front deceleration case 4.
The power is transmitted to a front wheel drive system which is connected to a front differential case l equipped with a differential gear system.
１６が前輪であり、１７が後輪である。16 is a front wheel, and 17 is a rear wheel.
次に第２図においてフロントデフケース４の構成につい
て説明すると。Next, the configuration of the front differential case 4 will be explained with reference to FIG.
従来の構成においては、前輪駆動軸装置２３の軸が直接
に差動歯車装置の入力軸に連結されていたのである。そ
して、差動山車装置のデフリングギアを機械加工により
、ハイポイドギア切削加工し歯数を増やし、他方入力軸
端のへヘルギャもハイポイドギアにして歯数を凍らし、
両者の比率により大きく減速させながら、入力軸を下方
に配置していたのである。In the conventional configuration, the shaft of the front wheel drive shaft device 23 was directly connected to the input shaft of the differential gear device. Then, the differential ring gear of the differential float device was machined to increase the number of teeth by cutting a hypoid gear, and the gear at the end of the input shaft was also made into a hypoid gear to reduce the number of teeth.
The input shaft was placed at the bottom while significantly reducing the speed depending on the ratio of the two.
本構成においては、従来の入力軸を第１入力軸５と第２
入力軸６の２軸に構成し２）、前輪駆動軸装置２３に連
結される第１入力軸５の上の平歯車３１と第２入力軸６
の上の平歯車３０により１段の減速を行なって第２入力
軸端のベベルギヤ６ａにより、差動歯車装置のデフリン
グギア８へ動力伝達を行なうことで第１入力軸を機体下
方へ配置することになるのである。In this configuration, the conventional input shaft is connected to the first input shaft 5 and the second input shaft.
The input shaft 6 is composed of two shafts 2), a spur gear 31 on the first input shaft 5 connected to the front wheel drive shaft device 23, and a second input shaft 6.
The first input shaft is placed below the fuselage by performing one-stage deceleration using the spur gear 30 on the top of the input shaft, and transmitting power to the differential ring gear 8 of the differential gear device using the bevel gear 6a at the end of the second input shaft. It becomes.
そして該構成が、逆にエンジンＥの位置を低くすること
が出来ることより重心位置は低くて地上高の高い安定し
たトラクターに構成することが出来るという効果を発揮
しているものである。Moreover, this configuration has the effect of being able to lower the position of the engine E, thereby making it possible to construct a stable tractor with a low center of gravity and high ground clearance.
このように第１入力軸５の位置が下がったとしても、従
来からの技術においても存在していたフ［１ントデフケ
ース１の下端の位置よりも下方とならないように、第３
図の鎖線で示すように斜め下方位置に配置しているので
、フロント減速ケース４の下端の位置が最低地上高を規
定することは無いのである。Even if the position of the first input shaft 5 is lowered in this way, the position of the third input shaft 5 is adjusted so that it does not become lower than the position of the lower end of the first differential case 1, which existed in conventional technology.
Since it is disposed diagonally downward as shown by the chain line in the figure, the position of the lower end of the front deceleration case 4 does not determine the minimum ground clearance.
２８はフロン１−デフケース１を支持するセンターピン
である。28 is a center pin that supports the freon 1 and the differential case 1.
次に第３１１２１・第４図・第５図により、差動１お車
装置の構成を説明すると。Next, the configuration of the differential 1 vehicle device will be explained with reference to Figs. 31, 121, 4, and 5.
前記したように、第１入力軸５の回転は波速１力車列に
より第２入力軸６へ至るので、ハイポイドベベルギヤで
得られる減速比と略同率に減速させることができる為、
デフリングギア８と第２入力軸端のベベルギヤ６ａにス
トレートベヘルギャを用いることが可能となり、差動歯
車装置のピニオンギア２６・２７やピニオンピン７やサ
イドギア２５Ｌ・２５Ｒと同様、全て精密鋳造により機
械加工なしで製作することができるように構成されてい
るのである。As mentioned above, since the rotation of the first input shaft 5 is transmitted to the second input shaft 6 by the wave speed single force train, the speed can be reduced to approximately the same rate as the reduction ratio obtained by the hypoid bevel gear.
It is now possible to use straight bevel gears for the differential ring gear 8 and the bevel gear 6a at the end of the second input shaft, and like the pinion gears 26 and 27 of the differential gear, the pinion pin 7, and the side gears 25L and 25R, they are all made of precision casting. It is constructed so that it can be manufactured without machining.
そして従来はデフケースに鍔部を構成し、該鍔部にデフ
リングギアを固定していたのであるが、本発明において
は１、デフケースを半一体化したデフリングギア８とす
べく、精密鋳造時にデフリングギア８を椀状に形成し、
従来のデフケースと同様、デフサイドギア２５Ｒの収容
とピニオンピン７の支持を行なわせている。Conventionally, a flange was formed on the differential case, and the differential ring gear was fixed to the flange, but in the present invention, 1. In order to create a differential ring gear 8 in which the differential case is semi-integrated, the differential ring gear is formed during precision casting. 8 into a bowl shape,
Like the conventional differential case, the differential side gear 25R is accommodated and the pinion pin 7 is supported.
そしてデフリングギア８の支持は、その椀状終端の筒状
部を、フロントアクスルケース２９から内方に突出した
軸受突部の軸受１２により行ない、デフリングギア８が
ベベルギヤ６ａとの噛合いで発生するスラスト力を受け
るようにしている。The differential ring gear 8 is supported by a cylindrical portion at the bowl-shaped end thereof by a bearing 12 of a bearing protrusion protruding inward from the front axle case 29, and the thrust generated when the differential ring gear 8 meshes with the bevel gear 6a. I try to receive power.
デフリングギア８の椀状開口部の内周壁は、ピニオンギ
ア２６・２７の凸型球面状の背部に対応して凹型球面に
形成され、該ピニオンギア２６・２７の背部が接当され
て収容されている。また椀状開口部の端面には一対の凹
部８ａ・８ｂが形成されている。The inner circumferential wall of the bowl-shaped opening of the differential ring gear 8 is formed into a concave spherical surface corresponding to the convex spherical back portions of the pinion gears 26 and 27, and is housed with the back portions of the pinion gears 26 and 27 in contact with each other. ing. Furthermore, a pair of recesses 8a and 8b are formed on the end face of the bowl-shaped opening.
次に、ピニオンギア２６・２７を枢支するピニオンピン
７の形状は次の通りである。Next, the shape of the pinion pin 7 that pivotally supports the pinion gears 26 and 27 is as follows.
即ち、左右の出力軸３Ｌ・３Ｒを突き合わせ状に支持す
る軸受部７ａとこれより一体に、ピニオンギア２６・２
７を枢支する枢支部７ｂを形成し、その外端面を前記ピ
ニオンギア２６・２７の背面凸型球面状と合致する凸型
球面形状７ｍに＋１４成している。That is, the pinion gears 26 and 2 are integrally connected to the bearing portion 7a that supports the left and right output shafts 3L and 3R in an abutted manner.
7 is formed, and its outer end surface is formed into a convex spherical shape 7m that matches the convex spherical shape of the back surface of the pinion gears 26 and 27.
この外端面に、前記デフリングギア８の凹部８ａ・８ｂ
に係合可能な突起７Ｃを形成している。Concave portions 8a and 8b of the differential ring gear 8 are provided on this outer end surface.
A protrusion 7C that can be engaged with is formed.
そして、デフリングギア８の顛きは、その軸受部７ａで
もって出力軸３Ｌ・３［ン上に安定支持されているピニ
オンピン７の突起７Ｃを、該デフリングギア８の椀状開
口部の端面に形成の凹部８ａ・８ｂに係合させ、凸型球
面の枢支部７ｂ外端面をデフリングギア８の椀状開口部
の内周壁に接当させることで防止できる。The structure of the differential ring gear 8 is such that the protrusion 7C of the pinion pin 7, which is stably supported on the output shafts 3L and 3 by its bearing portion 7a, is attached to the end surface of the bowl-shaped opening of the differential ring gear 8. This can be prevented by engaging the concave portions 8a and 8b of the differential ring gear 8 and bringing the outer end surface of the convex spherical pivot portion 7b into contact with the inner circumferential wall of the bowl-shaped opening of the differential ring gear 8.
出力軸３Ｒ上にスブラ・イン係合のサイトギア２５Ｒは
その外側面にデフリングギア８の内壁面を接当させるこ
とで図示左方向への移動を阻止し、同様に出力軸３Ｌ上
のサイドギア２５Ｌの外側面はフロントデフケース１の
軸受１３の内輪に接当させ図示右方向の移動を阻止して
いる。The sight gear 25R, which is engaged in a sub-in engagement on the output shaft 3R, is prevented from moving to the left in the drawing by bringing the inner wall surface of the differential ring gear 8 into contact with its outer surface, and the side gear 25L on the output shaft 3L is similarly prevented from moving to the left in the drawing. The outer surface of the front differential case 1 is brought into contact with the inner ring of the bearing 13 to prevent movement in the right direction in the drawing.
この両サイトギア２５Ｌ・２５Ｒ間に、前述の出力軸３
Ｌ・３Ｒを突き合せ状に支持するピニオンピン７の軸受
部７ａを配置し、その側面にサイドギア２５Ｌ・２５１
ンの内側面を接当させて、サイドギア２５Ｒ１ピニオン
ピン７、サイドギア２５Ｌの軸方向移動を阻止している
。Between these two sight gears 25L and 25R, the above-mentioned output shaft 3
The bearing part 7a of the pinion pin 7 that supports L and 3R in abutting manner is arranged, and the side gears 25L and 251 are mounted on the side of the bearing part 7a.
The inner surfaces of the pins are brought into contact with each other to prevent the side gear 25R1 pinion pin 7 and the side gear 25L from moving in the axial direction.
フロントデフケース１とフロントアクスルケース２９を
接合することにより全体的な前輪駆動ケースを構成して
いるものである。The front differential case 1 and the front axle case 29 are joined together to form an overall front wheel drive case.
第５図に示す如く、デフリングギア８を椀状に構成し、
該椀状の開口部側の側面に凹部８ａ・８ｂを、デフリン
グギア８の精密鋳造時に同時形成゛あるいは切削加工に
て形成している。該凹部８ａ・８ｂ内にピニオンピン７
の両端面を係合させているものである。As shown in FIG. 5, the differential ring gear 8 is configured in a bowl shape,
Concave portions 8a and 8b are formed on the side surface of the bowl-shaped opening at the same time during precision casting of the differential ring gear 8, or by cutting. A pinion pin 7 is placed in the recesses 8a and 8b.
Both end surfaces of the two are engaged with each other.
該デフリングギア８の凹部８ａ・８ｂ内にピニオンピン
７を係合することにより、デフリングギア８とピニオン
ピン７が一体的に公転すべく構成しているものである。By engaging the pinion pin 7 in the recesses 8a and 8b of the differential ring gear 8, the differential ring gear 8 and the pinion pin 7 are configured to revolve integrally.
デフリングギア８の椀状開口部内に、出力軸３Ｒと一体
のサイドギア２５Ｒを収容し、該サイドギア２５Ｒに噛
合させるピニオンギア２６・２７を枢支したピニオンピ
ン７を凹部８ａ・８ｂに係合するごとにより、ピニオン
ギア２６・２７とサイドギア２５Ｒを噛合させて、更に
ピニオンギア２６・２７の外側に、出力軸３Ｌと一体の
サイト′ギア２５Ｌを噛合させた状態で、サイドギア２
５Ｌの外側面を軸受１３の内輪側面に接当させて、フロ
ントアクスルケース２９とフロントデフケース１を締め
付は一体化し、デフリングギア８とサイドギア２５Ｌ・
２５Ｒとピニオンピン７を一体化して差動歯車装置を完
成するのである。A side gear 25R integrated with the output shaft 3R is housed in the bowl-shaped opening of the differential ring gear 8, and each time the pinion pin 7, which pivotally supports pinion gears 26 and 27 to be meshed with the side gear 25R, is engaged with the recesses 8a and 8b. With this, the side gear 25R is engaged with the pinion gears 26 and 27, and the sight gear 25L, which is integrated with the output shaft 3L, is engaged with the outside of the pinion gears 26 and 27.
The outer surface of 5L is brought into contact with the inner ring surface of bearing 13, and the front axle case 29 and front differential case 1 are tightened together, and the differential ring gear 8 and side gear 25L.
25R and the pinion pin 7 are integrated to complete the differential gear device.
（へ）発明の効果
本発明は以上の如く構成したので、次のような効果を奏
するものである。(F) Effects of the Invention Since the present invention is constructed as described above, it has the following effects.
第１に、前輪駆動ケースに対して、減速歯車列を用いて
入力軸の位置を下げることによりエンジン位置を低位置
に置くことができる上、差動歯車ｖｔ置へはその前段で
既に減速されて動力伝達される為、入力軸端のベベルギ
ヤ及びデフリングギアには従来の如くハイポイドベベル
ギヤを用いる必要がなく、ストレートベヘルギャに構成
することができて、精密鋳造でもって機械加工なしで安
価に製作でき、差動歯車装置の製作コストを低減するこ
とができる。First, for the front-wheel drive case, by lowering the position of the input shaft using a reduction gear train, the engine position can be placed at a lower position, and the engine position is already reduced before reaching the differential gear VT position. Because the power is transmitted through the input shaft, there is no need to use hypoid bevel gears for the bevel gear and differential ring gear at the end of the input shaft as in the past, and they can be configured as straight bevel gears, making it possible to reduce the cost by using precision casting without machining. The manufacturing cost of the differential gear device can be reduced.
第２にデフリングギアは椀状に形成されて、その端部を
ケース側に軸支することにより、デフリングギアにかか
るスラスト力を受けさせることができ、差動歯車装置が
、従来のデフケースを不要としながらも、安定支持され
る。Second, the differential ring gear is formed into a bowl shape, and by having its end pivotally supported on the case side, the thrust force applied to the differential ring gear can be received, and the differential gear system eliminates the need for a conventional differential case. However, it is stably supported.
第３にデフリングギアの椀状の開口端面に、ピニオンギ
アを枢支するピニオンピン７の端部が係合される凹部を
形成したことにより、デフリングギアの開口内部にまん
べんなく潤滑油をゆきわたらせることができ、サイドギ
アとピニオンギアの噛合い部分、ピニオンギアとピニオ
ンピンの枢支部分への潤滑が確実に行なわれる。Third, by forming a recess in the bowl-shaped opening end surface of the differential ring gear, into which the end of the pinion pin 7 that pivotally supports the pinion gear is engaged, lubricating oil can be spread evenly inside the opening of the differential ring gear. This ensures that the meshing portion between the side gear and the pinion gear and the pivot portion between the pinion gear and the pinion pin are reliably lubricated.
第４に、ピニオンピンはデフリングギアの椀状の開口端
面の凹部に側方から係合させているだけであり、フロン
Ｉ・デフケースとフロントアクスルケースの接合を解く
だけでピニオンピンはデフリングギアより容易に外すこ
とができて、差動歯車装置の分解・組立が非常に簡単と
なっている。Fourth, the pinion pin is only engaged from the side with the recess in the bowl-shaped opening end of the differential ring gear, and by simply uncoupling the front I/differential case and the front axle case, the pinion pin can be moved from the differential ring gear. It can be easily removed, making disassembly and assembly of the differential gear very easy.
第５に、ピニオンピンの中央部に左右の車軸を突き合わ
せ状に支持する軸受部を形成したので、ここでピニオン
ピン７が安定に支持されて、ピニオンピン７に係合され
るラブリングギア８も安定に支持されると共に、軸受部
の両側面を両サイドギアの内側面に接当させたので、サ
イドギアとピニオンピンの位置決めが正確になされて、
ピニオンギアとサイドギアの夫々の噛合いが確実となっ
てデフリングギアの回転を正確に該ピニオンピンを介し
てピニオンギアからサイドギアへ伝達することができる
。Fifth, since a bearing part is formed in the center of the pinion pin to support the left and right axles in abutting manner, the pinion pin 7 is stably supported here, and the love ring gear 8 engaged with the pinion pin 7 is provided. In addition to being stably supported, both sides of the bearing are in contact with the inner surfaces of both side gears, allowing accurate positioning of the side gears and pinion pins.
The engagement between the pinion gear and the side gear is ensured, and the rotation of the differential ring gear can be accurately transmitted from the pinion gear to the side gear via the pinion pin.
第１図はトラクターの全体側面図、第２図は本発明の差
動歯車装置を前輪駆動部に用いた実施例の側面断面図、
第３図は同じ（後面断面図、第４図は差動歯車装置のみ
を取り出した状態の側面図、第５図はデフリングギア８
の斜視図、第６図はピニオンピン７の斜視図である。
■・・・フロントデフケース
４・・・フロン１−減速ケース
５・・・入力軸
７・・・・ピニオンピン
８・・・・デフリングギア
１２．１３・・・軸受
２５Ｌ、２５Ｒ・・・サイドギア
２６．２７・・・・ピニオンギア
出願人 株式会社神崎高級工機製作所
代理人 弁理士 矢 野 寿 −部
第５図FIG. 1 is an overall side view of a tractor, and FIG. 2 is a side sectional view of an embodiment in which the differential gear device of the present invention is used in a front wheel drive section.
Figure 3 is the same (rear sectional view, Figure 4 is a side view with only the differential gear device removed, Figure 5 is the differential ring gear 8).
FIG. 6 is a perspective view of the pinion pin 7. ■... Front differential case 4... Freon 1 - Reduction case 5... Input shaft 7... Pinion pin 8... Differential ring gear 12.13... Bearings 25L, 25R... Side gear 26 .27...Pinion gear applicant Kanzaki Kokyukoki Seisakusho Co., Ltd. Agent Patent attorney Hisashi Yano - Part 5
Claims (3)
に第２入力軸６を設け、減速歯車列を介して連動連結す
ると共に、第２入力軸６端のベベルギヤ６ａとこれに噛
合う差動歯車装置のデフリングギア８とをストレートベ
ベルギヤにより構成したことを特徴とするトラクターの
動力伝達装置。(1) A second input shaft 6 is provided on the upper stage of the first input shaft 5 driven by the engine, and is interlocked and connected via a reduction gear train, and meshes with the bevel gear 6a at the end of the second input shaft 6. A power transmission device for a tractor, characterized in that a differential ring gear 8 of a differential gear device is constituted by a straight bevel gear.
の該デフリングギア８を椀状に形状してその端部をケー
ス側に軸支する一方、椀状の開口端面に、ピニオンギア
２６・２７を枢支するピニオンピン７の端部が係合され
る凹部８ａ・８ｂを形成したことを特徴とするトラクタ
ーの動力伝達装置。(2) In claim 1, the differential ring gear 8 of the differential gear device is shaped like a bowl and the end thereof is pivotally supported on the case side, while a pinion gear is provided on the open end surface of the bowl shape. A power transmission device for a tractor, characterized in that recesses 8a and 8b are formed in which the ends of pinion pins 7 that pivotally support pinion pins 26 and 27 are engaged.
７の中央部に、左右の車軸３Ｌ・３Ｒを突き合せ状に支
持する軸受部７ａを形成し、その両端面をサイドギア２
５Ｌ・２５Ｒの内側面に接当させたことを特徴とするト
ラクターの動力伝達装置。(3) In claim 2, a bearing part 7a is formed in the center of the pinion pin 7 to support the left and right axles 3L and 3R in an abutting manner, and both end surfaces of the bearing part 7a are attached to the side gear 2.
A power transmission device for a tractor characterized by being brought into contact with the inner surfaces of 5L and 25R.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62109425A JPH0814307B2 (en) | 1987-05-01 | 1987-05-01 | Differential gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62109425A JPH0814307B2 (en) | 1987-05-01 | 1987-05-01 | Differential gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS63275430A true JPS63275430A (en) | 1988-11-14 |
| JPH0814307B2 JPH0814307B2 (en) | 1996-02-14 |
Family
ID=14509918
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62109425A Expired - Fee Related JPH0814307B2 (en) | 1987-05-01 | 1987-05-01 | Differential gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0814307B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1291557A3 (en) * | 2001-09-07 | 2004-08-04 | Bayerische Motoren Werke Aktiengesellschaft | Power divider for vehicles |
| JP2020066269A (en) * | 2018-10-22 | 2020-04-30 | 株式会社 神崎高級工機製作所 | Mobile body drive unit and mobile body |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5923145A (en) * | 1982-07-06 | 1984-02-06 | テクムゼ・プロダクツ・カンパニ− | Improved transmission shaft |
-
1987
- 1987-05-01 JP JP62109425A patent/JPH0814307B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5923145A (en) * | 1982-07-06 | 1984-02-06 | テクムゼ・プロダクツ・カンパニ− | Improved transmission shaft |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1291557A3 (en) * | 2001-09-07 | 2004-08-04 | Bayerische Motoren Werke Aktiengesellschaft | Power divider for vehicles |
| US6814176B2 (en) | 2001-09-07 | 2004-11-09 | Bayerische Motoren Werke Aktiengesellschaft | Differential case for motor vehicles |
| JP2020066269A (en) * | 2018-10-22 | 2020-04-30 | 株式会社 神崎高級工機製作所 | Mobile body drive unit and mobile body |
| US11541749B2 (en) | 2018-10-22 | 2023-01-03 | Kanzaki Kokyukoki Mfg. Co., Ltd. | Moving body drive unit and moving body |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0814307B2 (en) | 1996-02-14 |
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