JP4549483B2 - Gear transmission device - Google Patents

Gear transmission device Download PDF

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Publication number
JP4549483B2
JP4549483B2 JP2000091378A JP2000091378A JP4549483B2 JP 4549483 B2 JP4549483 B2 JP 4549483B2 JP 2000091378 A JP2000091378 A JP 2000091378A JP 2000091378 A JP2000091378 A JP 2000091378A JP 4549483 B2 JP4549483 B2 JP 4549483B2
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Japan
Prior art keywords
main shaft
pinion gear
gear
shaft portion
drive pinion
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Expired - Fee Related
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JP2000091378A
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Japanese (ja)
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JP2001280445A (en
Inventor
栄一 寺田
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Showa Corp
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Showa Corp
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    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
    • 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
    • F16H48/38—Constructional details
    • F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
    • F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement
    • 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
    • F16H48/38—Constructional details
    • F16H48/42—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon
    • F16H2048/423—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement
    • F16H2048/426—Constructional details characterised by features of the input shafts, e.g. mounting of drive gears thereon characterised by bearing arrangement characterised by spigot bearing arrangement, e.g. bearing for supporting the free end of the drive shaft pinion

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  • Gear Transmission (AREA)
  • Retarders (AREA)
  • Snaps, Bayonet Connections, Set Pins, And Snap Rings (AREA)
  • General Details Of Gearings (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は４輪車両の差動歯車装置及びファイナルギヤ装置等、特にピニオンギヤとヨーク部材との締結構造を改良した歯車伝達装置に関する。
【０００２】
【従来の技術】
図２は従来の差動歯車装置の一例を示す縦断面図である。
ギヤケース05は、前半部のピニオンギヤケース06と後半部の差動キャリア07が一体に形成されている。ピニオンギヤケース06は、円筒部06ａと後底端部06ｂとから成るほぼ有底円筒形状をしており、その後底端部06ｂに、偏平な円筒部07ａと中空の左底端部07ｂとから成る有底円筒形状をした差動キャリア07が、一体に延設されている。ピニオンギヤケース06と差動キャリア07は、後底端部06ｂと左底端部07ｂとが一体に連結され、ピニオンギヤケース06の円筒形状の中心軸が前後方向に指向し、差動キャリア07の円筒形状の中心軸が左右方向に指向して、両者は直交している。
【０００３】
ピニオンギヤケース06の内部にはヨーク締結機構02が納められている。また差動キャリア07の右側の円形開口を覆うようにして中空の差動キャリアカバー08が右側から合体し、その内部に差動機構03が納められる。
【０００４】
差動機構03は、差動キャリア07および差動キャリアカバー08内において、リングギヤ060と一体に左右合体した差動ケース061が左右方向に指向する中心軸の周りに回転自在に、玉軸受062，063により支持されている。
【０００５】
差動ケース061内で中心軸に直交して架設されたピニオンシャフト064に一対のピニオンギヤ065、065が回転自在に軸支されている。そして各ピニオンギヤ065、065にともにべべルギヤ式に噛み合う一対のサイドギヤ066、066がピニオンシャフト064を挟んで左右にそれぞれ回転自在に支持されている。この各サイドギヤ066、066に左右のアクスル軸がそれぞれスプライン嵌合される。
【０００６】
次にヨーク締結機構02について説明する。
【０００７】
駆動ピニオンギヤ012は軸方向にねじ部012ａ、スプライン部012ｂ、円柱部012ｃ、ギヤ部012ｄ、円柱端部012ｅが前から後へ順に形成されている。この駆動ピニオンギヤ012のギヤ部012ｄが前記差動機構03のリングギヤ060に噛み合って、動力が差動機構03に伝達されるようになっている。
【０００８】
ピニオンギヤケース06の後底端部06ｂは、外径が２段階に縮小されて後方に先細に形成されている。そしてその後端の内径が縮小された部分にころ軸受013が介装されて、駆動ピニオンギヤ012の円柱端部012ｅが軸支されている。また、アウタレースがロックナット015によりピニオンギヤケース06の円筒部06ａに固定された玉軸受014のインナレースに、駆動ピニオンギヤ012の円柱部012ｃが挿入されている。こうして駆動ピニオンギヤ012は、ころ軸受013と玉軸受014によりピニオンギヤケース06に回転自在に軸支される。駆動ピニオンギヤ012のスプライン部012ｂには外歯スプラインが形成されている。
【０００９】
017はヨーク部材であって、枝分かれした前端部には、図示しないエンジン側ヨーク部材と結合するクロスジョイントを挿入する穴017ａが設けられている。そして後部の主軸部017ｂは円筒状に延び、その円筒内面に内歯スプライン017ｄが形成されて、前記駆動ピニオンギヤ012の外歯スプライン部012ｂと係合している。また、駆動ピニオンギヤ012先端のねじ部012ａに螺合されたロックナット018によって、ヨーク部材017は駆動ピニオンギヤ012に軸受014を挟持して一体に固定される。
【００１０】
【発明が解決しようとする課題】
前記従来の差動歯車装置においては、入力の回転方向によってピニオンギヤ012の反力の心向荷重方向が変化してしまうので、ピニオンギヤ012の位置を強固に固定する必要があり、そのためヨーク部材017とロックナット018で締結していた。したがって、ねじ成形が必要であり、組立工数も多かった。
【００１１】
また、駆動ピニオンギヤ012とヨーク部材017を一体に締結するロックナット018がヨーク部材017の枝分かれする股部に位置するため、ヨーク部材017を駆動ピニオンギヤ012に取り付けた後でないと、相手側（エンジン側）のヨークやクロスジョイントの組み付けができなかった。
【００１２】
【課題を解決するための手段および効果】
前記課題を解決するために、請求項１の発明は、アウタレースがケース側に装着されたころがり軸受と、該ころがり軸受のインナレースに圧入され、先端に外歯スプラインが設けられた駆動ピニオンギヤの主軸部と、先端面に凹所を有し、同凹所に設けられた内歯スプラインが上記外歯スプラインに係合するヨーク主軸部を有するヨーク部材と、駆動ピニオンギヤと上記ヨーク部材の主軸部の軸方向摺動を阻止すべく、上記内歯スプラインと上記外歯スプラインの係合部に取り付けられたストッパーリングとを備え、上記凹所は、上記ヨーク主軸部の先端面以外に開口せず、上記駆動ピニオンギヤ主軸部の先端を密閉し、上記ころがり軸受のインナレースは、上記ヨーク主軸部の先端面と、上記駆動ピニオンギヤの主軸部の基部に形成されたつば部とで直接挟持され、上記ヨーク部材が、上記駆動ピニオンギヤの主軸部に対し軸方向に位置決めされて連結されたことを特徴とする歯車伝達装置である。
【００１３】
請求項１の発明はこのように構成されているので、ねじ成形の一部が不要になって加工費を低減でき、組立工数も削減される。請求項１の発明はまた、ヨーク部材と相手方のエンジン側ヨーク部材とをあらかじめ結合した後に、それらをピニオンギヤに取り付けることができ、組立て作業の自由度が増して、コストを低減できる。
また、ヨーク部材の後端凹所がヨーク主軸部の先端面以外には開口せず、ピニオンギヤ主軸部の先端を密閉する状態になっているので、凹所に塵等の異物が侵入する心配がなく、シール材が不要である。
【００１４】
また、請求項２の発明は、請求項１記載の歯車伝達装置において、上記ケースに、上記ヨーク部材の主軸部を囲んで円筒部が設けられ、同円筒部の内面と上記ヨーク部材の主軸部の外側面との間にシール部材が装着されることを特徴とする。
【００１６】
さらに請求項３の発明は、上記に加えて、前記駆動ピニオンギヤの従動ギヤの噛合いが、すぐ歯傘歯車（ストレートベベルギヤ）により駆動伝達されることを特徴とするものである。
【００１７】
請求項３の発明はこのように構成されているので、ギヤの心向荷重方向を一方向とすることができ、振動、耐久性に有利である。
【００１８】
【発明の実施の形態】
図１は本発明に係る歯車伝達装置の実施の一形態を示す縦断面図である。
【００１９】
ギヤケース５は、前半部のピニオンギヤケース６と後半部の差動キャリヤ７が一体に形成されている。ピニオンギヤケース６は、円筒部６ａと後底端部６ｂとから成るほぼ有底円筒形状をしており、その後底端部６ｂに、扁平な円筒部７ａと中空の左底端部７ｂとから成る有底円筒形状をした差動キャリア７が、一体に延設されている。ピニオンギヤケース６と差動キャリヤ７は、後底端部６ｂと左底端部７ｂとが一体に連結され、ピニオンギヤケース６の円筒形状の中心軸が前後方向に指向し、差動キャリヤ７の円筒形状の中心軸が左右方向に指向して、両者は直交している。
【００２０】
ピニオンギヤケース６の内部にはヨーク締結機構２が納められている。また差動キャリヤ７の右側の円形開口を覆うようにして中空の差動キャリヤカバー８が右側から合体し、その内部に差動機構３が納められる。
【００２１】
差動機構３は、差動キャリヤ７および差動キャリヤカバー８内において、リングギヤ60と一体に左右合体した差動ケース61が左右方向に指向する中心軸の周りに回転自在に、玉軸受62、63により支持されている。
差動ケース61内で中心軸に直交して架設されたピニオンシャフト64に一対のピニオンギヤ65、66が回転自在に軸支されている。そして各ピニオンギヤ65、65にともにベベルギヤ式に噛み合う一対のサイドギヤ66、66がピニオンシャフト64を挟んで左右にそれぞれ回転自在に支持されている。この各サイドギヤ66、66に左右のアクスル軸がそれぞれスプライン嵌合されている。
【００２２】
次にヨーク締結機構２について説明する。
【００２３】
駆動ピニオンギヤ12は軸方向に主軸部12ａ、つば部12ｂ、ギヤ部12ｃ、円柱端部12ｄが前から後へ順に形成されている。この駆動ピニオンギヤ12のギヤ部12ｃが前記差動機構３のリングギヤ60に噛み合って、動力が差動機構３に伝達されるようになっている。
【００２４】
ピニオンギヤケース６の後底端部６ｂは、外径が２段階に縮小されて後方に先細に形成されている。そしてその後端の内径が縮小された部分にころ軸受13が介装されて、駆動ピニオンギヤ12の円柱端部12ｄが軸支されている。また、アウタレースがロックナット15によりピニオンギヤケース６の円筒部６ａに固定された玉軸受14のインナレースに、駆動ピニオンギヤ12の主軸部12ａが圧入されている。こうして駆動ピニオンギヤ12は、ころ軸受13と玉軸受14によりピニオンギヤケース６に、間接的には車体に、回転自在に軸支される。
【００２５】
駆動ピニオンギヤ12の主軸部12ａの先端には外歯スプライン12ｅが形成されている。
【００２６】
17はヨーク部材であって、枝分かれした前端部には、図示しないエンジン側ヨーク部材と結合するクロスジョイントを挿入する穴17ａが設けられている。そして後端は主軸部17ｂが円筒状に延びて凹所17ｃを形成している。その凹所17ｃには内歯スプライン17ｄが形成され、前記駆動ピニオンギヤ12の主軸部12ａ先端の外歯スプライン12ｅと結合する。また、この両スプライン12ｅ、17ｄの結合部には、駆動ピニオンギヤ12とヨーク部材17との軸方向摺動を阻止するストッパーリング19が挿入される。
【００２７】
前記玉軸受14のインナレースは、ヨーク部材17の主軸部17ｂ先端面と駆動ピニオンギヤ12のつば部12ｂとで挟持される。またヨーク部材17の主軸部17ｂ外側面とピニオンギヤケース６の円筒部６ａ内面との間にはシール部材20が装着される。
【００２８】
本実施形態の歯車伝達装置はこのように構成されていて、駆動ピニオンギヤ12とヨーク部材17との結合を、圧入とストッパーリング19の挿入のみで行ない、従来のようなロックナット等を使用しないので、その分のねじ成形が不要になって加工費を低減でき、組立工数も削減される。さらに、駆動ピニオンギヤ12の諸元を変更することにより、たとえば、すぐ歯の傘歯車により、駆動ピニオンギヤ12の心向荷重を小さくしたり、荷重方向を一方向とすることができるから、一方向だけの強度を考慮すれば良く、圧入とストッパーリング挿入だけでも、駆動ピニオンギヤ12とヨーク部材17との軸方向摺動を十分に阻止することができる。また荷重方向が一方向のみであり振動、耐久性に有利である。
【００２９】
また本実施形態の差動歯車装置では、駆動ピニオンギヤ12とヨーク部材17との結合にロックナットを用いないので、ヨーク部材17と図示しない相手方のエンジン側ヨーク部材とをあらかじめ結合した後に、それらを駆動ピニオンギヤ12に取り付けることができ、組立作業の自由度が増して、コストを低減できる。
【００３０】
さらに本実施形態においては、ヨーク部材17の凹所17ｃがヨーク主軸部17ｂの先端面以外には開口せず、ヨーク部材17でピニオンギヤ主軸部12ａの先端を密閉する状態になっているので、凹所17ｃに塵等の異物が侵入する心配がなく、シール材が不要である。
【００３１】
【図面の簡単な説明】
【図１】図１は本発明に係る差動歯車装置の実施の一形態を示す縦断面図である。
【図２】図２は従来の差動歯車装置の一例を示す縦断面図である。
【符号の説明】
２…ヨーク締結機構、３…差動機構、５…ギヤケース、６…ピニオンギヤケース、６ａ…円筒部、６ｂ…後底端部、７…差動キャリヤ、７ａ…円筒部、７ｂ…左底端部、８…差動キャリヤカバー、12…駆動ピニオンギヤ、12ａ…主軸部、12ｂ…つば部、12ｃ…ギヤ部、12ｄ…円柱端部、12ｅ…外歯スプライン、13…ころ軸受、14…玉軸受、15…ロックナット、17…ヨーク部材、17ａ…クロスジョイント穴、17ｂ…主軸部、17ｃ…凹所、17ｄ…内歯スプライン、19…ストッパーリング、20…シール部材、60…リングギヤ、61…差動ケース、64…ピニオンシャフト、65…ピニオンギヤ、66…サイドギヤ。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a differential gear device and a final gear device for a four-wheel vehicle, and more particularly to a gear transmission device having an improved fastening structure between a pinion gear and a yoke member.
[0002]
[Prior art]
FIG. 2 is a longitudinal sectional view showing an example of a conventional differential gear device.
In the gear case 05, a pinion gear case 06 in the front half and a differential carrier 07 in the rear half are integrally formed. The pinion gear case 06 has a substantially bottomed cylindrical shape composed of a cylindrical portion 06a and a rear bottom end portion 06b. The rear bottom end portion 06b includes a flat cylindrical portion 07a and a hollow left bottom end portion 07b. A differential carrier 07 having a bottomed cylindrical shape is integrally extended. In the pinion gear case 06 and the differential carrier 07, the rear bottom end portion 06b and the left bottom end portion 07b are integrally connected, the cylindrical center axis of the pinion gear case 06 is directed in the front-rear direction, and the cylindrical portion of the differential carrier 07 The central axis of the shape is oriented in the left-right direction, and they are orthogonal to each other.
[0003]
A yoke fastening mechanism 02 is housed inside the pinion gear case 06. A hollow differential carrier cover 08 is combined from the right side so as to cover the circular opening on the right side of the differential carrier 07, and the differential mechanism 03 is accommodated therein.
[0004]
In the differential carrier 07 and the differential carrier cover 08, the differential mechanism 03 is configured such that a differential case 061 integrally joined with the ring gear 060 is rotatable around a central axis directed in the left-right direction, 063 is supported.
[0005]
A pair of pinion gears 065 and 065 are rotatably supported on a pinion shaft 064 installed perpendicularly to the central axis in the differential case 061. A pair of side gears 066 and 066 that mesh with the pinion gears 065 and 065 in a bevel gear manner are supported so as to be rotatable to the left and right with the pinion shaft 064 interposed therebetween. The left and right axle shafts are spline-fitted to the side gears 066 and 066, respectively.
[0006]
Next, the yoke fastening mechanism 02 will be described.
[0007]
The drive pinion gear 012 has a screw part 012a, a spline part 012b, a cylindrical part 012c, a gear part 012d, and a cylindrical end part 012e formed in order from the front to the rear in the axial direction. The gear portion 012d of the drive pinion gear 012 meshes with the ring gear 060 of the differential mechanism 03 so that power is transmitted to the differential mechanism 03.
[0008]
The rear bottom end portion 06b of the pinion gear case 06 has an outer diameter that is reduced in two stages and is tapered rearward. Then, a roller bearing 013 is interposed in a portion where the inner diameter of the rear end is reduced, and the cylindrical end portion 012e of the drive pinion gear 012 is pivotally supported. Further, the cylindrical portion 012c of the drive pinion gear 012 is inserted into the inner race of the ball bearing 014 in which the outer race is fixed to the cylindrical portion 06a of the pinion gear case 06 by the lock nut 015. Thus, the drive pinion gear 012 is rotatably supported by the pinion gear case 06 by the roller bearing 013 and the ball bearing 014. An external spline is formed on the spline portion 012b of the drive pinion gear 012.
[0009]
A yoke member 017 is provided with a hole 017a for inserting a cross joint to be coupled to an unillustrated engine side yoke member at a branched front end portion. The rear main shaft portion 017b extends in a cylindrical shape, and an internal spline 017d is formed on the inner surface of the cylinder, and is engaged with the external spline portion 012b of the drive pinion gear 012. Further, the yoke member 017 is fixed integrally with the drive pinion gear 012 with the bearing 014 sandwiched by the lock nut 018 screwed to the screw portion 012a at the tip of the drive pinion gear 012.
[0010]
[Problems to be solved by the invention]
In the above-described conventional differential gear device, since the direction of the center direction of the reaction force of the pinion gear 012 changes depending on the rotation direction of the input, it is necessary to firmly fix the position of the pinion gear 012. It was fastened with a lock nut 018. Therefore, screw forming is necessary and the number of assembly steps is large.
[0011]
In addition, since the lock nut 018 for integrally fastening the drive pinion gear 012 and the yoke member 017 is located at the crotch portion where the yoke member 017 branches, the other side (engine side) must be installed after the yoke member 017 is attached to the drive pinion gear 012 ) Yoke and cross joint could not be assembled.
[0012]
[Means for solving the problems and effects]
In order to solve the above-mentioned problems, the invention of claim 1 is directed to a rolling bearing having an outer race mounted on the case side, and a main shaft of a drive pinion gear press-fitted into an inner race of the rolling bearing and provided with an external spline at the tip. A yoke member having a yoke main shaft portion having a recess in the tip surface, and an internal spline provided in the recess engaging the external spline, a drive pinion gear, and a main shaft portion of the yoke member in order to prevent axial sliding, and a stopper ring attached to engaging portions of the inner spline and the outer spline, the recess does not open in addition to the distal end surface of the yoke main shaft, The tip end of the drive pinion gear main shaft portion is sealed, and the inner race of the rolling bearing is formed on the front end surface of the yoke main shaft portion and the base portion of the main shaft portion of the drive pinion gear. Is directly held between the fly section, the yoke member is a gear transmission, characterized in that connected are positioned in the axial direction relative to the main shaft portion of the driving pinion gear.
[0013]
Since the invention of claim 1 is configured as described above, a part of the screw forming is not required, the processing cost can be reduced, and the number of assembling steps can be reduced. According to the first aspect of the present invention, the yoke member and the counterpart engine-side yoke member can be connected in advance and then attached to the pinion gear, so that the degree of freedom in assembling work can be increased and the cost can be reduced.
Further, since the recess at the rear end of the yoke member does not open except for the front end surface of the yoke main shaft portion, and the tip end of the pinion gear main shaft portion is sealed, there is a concern that foreign matters such as dust may enter the recess. And no sealing material is required.
[0014]
According to a second aspect of the present invention, in the gear transmission according to the first aspect, the case is provided with a cylindrical portion surrounding the main shaft portion of the yoke member, and an inner surface of the cylindrical portion and the main shaft portion of the yoke member are provided. A seal member is mounted between the outer surface and the outer surface.
[0016]
Further, the invention of claim 3 is characterized in that, in addition to the above, the engagement of the driven gear of the drive pinion gear is immediately transmitted by the bevel gear (straight bevel gear).
[0017]
Since the invention of claim 3 is configured as described above, the gear load direction in the center can be set to one direction, which is advantageous for vibration and durability.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 is a longitudinal sectional view showing an embodiment of a gear transmission device according to the present invention.
[0019]
In the gear case 5, a pinion gear case 6 in the front half and a differential carrier 7 in the rear half are integrally formed. The pinion gear case 6 has a substantially bottomed cylindrical shape composed of a cylindrical portion 6a and a rear bottom end portion 6b. The rear bottom end portion 6b includes a flat cylindrical portion 7a and a hollow left bottom end portion 7b. A differential carrier 7 having a bottomed cylindrical shape is integrally extended. In the pinion gear case 6 and the differential carrier 7, the rear bottom end portion 6 b and the left bottom end portion 7 b are integrally connected, the cylindrical central axis of the pinion gear case 6 is directed in the front-rear direction, and the differential carrier 7 cylinder The central axis of the shape is oriented in the left-right direction, and they are orthogonal to each other.
[0020]
A yoke fastening mechanism 2 is housed inside the pinion gear case 6. Further, a hollow differential carrier cover 8 is united from the right side so as to cover the circular opening on the right side of the differential carrier 7, and the differential mechanism 3 is housed therein.
[0021]
In the differential carrier 7 and the differential carrier cover 8, the differential mechanism 3 is configured such that a differential case 61 integrally joined with the ring gear 60 is rotatable about a central axis directed in the left-right direction, Supported by 63.
A pair of pinion gears 65 and 66 are rotatably supported on a pinion shaft 64 installed perpendicularly to the central axis in the differential case 61. A pair of side gears 66 and 66 meshing with the pinion gears 65 and 65 in a bevel gear manner are supported so as to be rotatable to the left and right with the pinion shaft 64 interposed therebetween. The left and right axle shafts are spline fitted to the side gears 66, 66, respectively.
[0022]
Next, the yoke fastening mechanism 2 will be described.
[0023]
The drive pinion gear 12 has a main shaft portion 12a, a collar portion 12b, a gear portion 12c, and a cylindrical end portion 12d formed in this order from the front to the rear in the axial direction. The gear portion 12 c of the drive pinion gear 12 meshes with the ring gear 60 of the differential mechanism 3 so that power is transmitted to the differential mechanism 3.
[0024]
The rear bottom end 6b of the pinion gear case 6 has an outer diameter that is reduced in two stages and is tapered rearward. A roller bearing 13 is interposed in a portion where the inner diameter of the rear end is reduced, and the cylindrical end portion 12d of the drive pinion gear 12 is pivotally supported. Further, the main shaft portion 12a of the drive pinion gear 12 is press-fitted into the inner race of the ball bearing 14 in which the outer race is fixed to the cylindrical portion 6a of the pinion gear case 6 by the lock nut 15. Thus, the drive pinion gear 12 is rotatably supported by the roller bearing 13 and the ball bearing 14 on the pinion gear case 6 and indirectly on the vehicle body.
[0025]
An external spline 12e is formed at the tip of the main shaft portion 12a of the drive pinion gear 12.
[0026]
A yoke member 17 is provided with a hole 17a for inserting a cross joint coupled to an unillustrated engine side yoke member at a branched front end portion. At the rear end, the main shaft portion 17b extends in a cylindrical shape to form a recess 17c. An internal spline 17d is formed in the recess 17c, and is coupled to the external spline 12e at the tip of the main shaft portion 12a of the drive pinion gear 12. In addition, a stopper ring 19 that prevents the drive pinion gear 12 and the yoke member 17 from sliding in the axial direction is inserted into the connecting portion of both the splines 12e and 17d.
[0027]
The inner race of the ball bearing 14 is sandwiched between the front end surface of the main shaft portion 17 b of the yoke member 17 and the flange portion 12 b of the drive pinion gear 12. A seal member 20 is mounted between the outer surface of the main shaft portion 17 b of the yoke member 17 and the inner surface of the cylindrical portion 6 a of the pinion gear case 6.
[0028]
The gear transmission device of the present embodiment is configured as described above, and the drive pinion gear 12 and the yoke member 17 are coupled only by press-fitting and insertion of the stopper ring 19, and a conventional lock nut or the like is not used. This eliminates the need for screw forming, thereby reducing processing costs and reducing the number of assembly steps. Furthermore, by changing the specifications of the drive pinion gear 12, for example, the center load of the drive pinion gear 12 can be reduced or the load direction can be set to one direction by a bevel gear with a tooth, for example. The axial sliding between the drive pinion gear 12 and the yoke member 17 can be sufficiently prevented by only press-fitting and inserting the stopper ring. Moreover, the load direction is only one direction, which is advantageous for vibration and durability.
[0029]
Further, in the differential gear device of the present embodiment, since a lock nut is not used for coupling the drive pinion gear 12 and the yoke member 17, after coupling the yoke member 17 and the other engine side yoke member (not shown) in advance, Since it can be attached to the drive pinion gear 12, the degree of freedom in assembling work can be increased and the cost can be reduced.
[0030]
Furthermore, in the present embodiment, the recess 17c of the yoke member 17 does not open except for the tip surface of the yoke main shaft portion 17b, and the tip of the pinion gear main shaft portion 12a is sealed by the yoke member 17, there is no fear that foreign matter such as dust to enter invasion to a predetermined 17c, the sealing material is not required.
[0031]
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing an embodiment of a differential gear device according to the present invention.
FIG. 2 is a longitudinal sectional view showing an example of a conventional differential gear device.
[Explanation of symbols]
2 ... Yoke fastening mechanism, 3 ... differential mechanism, 5 ... gear case, 6 ... pinion gear case, 6a ... cylindrical portion, 6b ... rear bottom end, 7 ... differential carrier, 7a ... cylindrical portion, 7b ... left bottom end 8 ... Differential carrier cover, 12 ... Drive pinion gear, 12a ... Main shaft portion, 12b ... Collar portion, 12c ... Gear portion, 12d ... End of cylinder, 12e ... External spline, 13 ... Roller bearing, 14 ... Ball bearing, 15 ... Lock nut, 17 ... Yoke member, 17a ... Cross joint hole, 17b ... Main shaft part, 17c ... Recess, 17d ... Internal spline, 19 ... Stopper ring, 20 ... Seal member, 60 ... Ring gear, 61 ... Differential Case, 64 ... pinion shaft, 65 ... pinion gear, 66 ... side gear.

Claims (3)

アウタレースがケース(6)側に装着されたころがり軸受(14)と、該ころがり軸受(14)のインナレースに圧入され、先端に外歯スプライン(12e)が設けられた駆動ピニオンギヤ(12)の主軸部(12a)と、先端面に凹所(17c)を有し、同凹所(17c)に設けられた内歯スプライン(17d)が上記外歯スプライン(12e)に係合するヨーク主軸部(17b)を有するヨーク部材(17)と、駆動ピニオンギヤ(12)と上記ヨーク部材(17)の主軸部(17b)の軸方向摺動を阻止すべく、上記内歯スプライン(17d)と上記外歯スプライン(12e)の係合部に取り付けられたストッパーリング(19)とを備え、
上記凹所(17c)は、上記ヨーク主軸部(17b)の先端面以外に開口せず、上記駆動ピニオンギヤ主軸部(12a)の先端を密閉し、
上記ころがり軸受(14)のインナレースは、上記ヨーク主軸部(17b)の先端面と、上記駆動ピニオンギヤ(12)の主軸部(12a)の基部に形成されたつば部(12b)とで直接挟持され、
上記ヨーク部材(17)が、上記駆動ピニオンギヤ(12)の主軸部(12a)に対し軸方向に位置決めされて連結されたことを特徴とする歯車伝達装置。Roller bearing (14) with outer race mounted on the case (6) side, and main shaft of drive pinion gear (12) press-fitted into the inner race of the roller bearing (14) and provided with an external spline (12e) at the tip A yoke main shaft portion (12a) having a recess (17c) at the tip surface, and an internal spline (17d) provided in the recess (17c) engaging with the external spline (12e) ( 17b) , the inner spline (17d) and the outer teeth to prevent axial sliding of the drive pinion gear (12) and the main shaft portion (17b) of the yoke member (17). with splines (12e) stopper ring attached to the engagement portion of the (19),
The recess (17c) does not open other than the front end surface of the yoke main shaft portion (17b), and seals the front end of the drive pinion gear main shaft portion (12a),
The inner race of the rolling bearing (14) is directly sandwiched between the tip surface of the yoke main shaft portion (17b) and the flange portion (12b) formed at the base portion of the main shaft portion (12a) of the drive pinion gear (12). And
The gear transmission device, wherein the yoke member (17) is positioned and connected in the axial direction to the main shaft portion (12a) of the drive pinion gear (12) . 上記ケース(6)に、上記ヨーク部材(17)の主軸部(17b)を囲んで円筒部(6a)が設けられ、同円筒部(6a)の内面と上記ヨーク部材(17)の主軸部(17b)の外側面との間にシール部材(20)が装着されることを特徴とする請求項１記載の歯車伝達装置。The case (6) is provided with a cylindrical portion (6a) surrounding the main shaft portion (17b) of the yoke member (17), and the inner surface of the cylindrical portion (6a) and the main shaft portion of the yoke member (17) ( The gear transmission according to claim 1, wherein a sealing member (20) is mounted between the outer surface of 17b). 前記駆動ピニオンギヤ(12)の従動ギヤ(60)との噛合いは、すぐ歯傘歯車(ストレートベベルギヤ)により駆動伝達されることを特徴とする請求項１または２記載の歯車伝達装置。  The gear transmission according to claim 1 or 2, wherein the engagement of the drive pinion gear (12) with the driven gear (60) is immediately transmitted by a bevel gear (straight bevel gear).
JP2000091378A 2000-03-29 2000-03-29 Gear transmission device Expired - Fee Related JP4549483B2 (en)

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JP5703830B2 (en) * 2011-02-24 2015-04-22 スズキ株式会社 Outboard motor power transmission
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CN109866250B (en) 2019-03-01 2021-08-13 达闼科技（北京）有限公司 Robot wrist structure and robot

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6072733U (en) * 1983-10-26 1985-05-22 いすゞ自動車株式会社 Vehicle final gear
JPS6185517U (en) * 1984-11-12 1986-06-05
JPH0456922U (en) * 1990-09-26 1992-05-15
JPH04122224U (en) * 1991-04-18 1992-11-02 三菱自動車工業株式会社 sleeve yoke
JPH07286657A (en) * 1994-04-14 1995-10-31 Hino Motors Ltd Oil seal device of differential input shaft support part

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS644944U (en) * 1987-06-29 1989-01-12

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6072733U (en) * 1983-10-26 1985-05-22 いすゞ自動車株式会社 Vehicle final gear
JPS6185517U (en) * 1984-11-12 1986-06-05
JPH0456922U (en) * 1990-09-26 1992-05-15
JPH04122224U (en) * 1991-04-18 1992-11-02 三菱自動車工業株式会社 sleeve yoke
JPH07286657A (en) * 1994-04-14 1995-10-31 Hino Motors Ltd Oil seal device of differential input shaft support part

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