JP4803871B2 - Lubrication structure of differential case and its processing method - Google Patents

Lubrication structure of differential case and its processing method Download PDF

Info

Publication number
JP4803871B2
JP4803871B2 JP2000345560A JP2000345560A JP4803871B2 JP 4803871 B2 JP4803871 B2 JP 4803871B2 JP 2000345560 A JP2000345560 A JP 2000345560A JP 2000345560 A JP2000345560 A JP 2000345560A JP 4803871 B2 JP4803871 B2 JP 4803871B2
Authority
JP
Japan
Prior art keywords
differential case
differential
pinion
gear
oil
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP2000345560A
Other languages
Japanese (ja)
Other versions
JP2002147580A (en
Inventor
栄一 寺田
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.)
Showa Corp
Original Assignee
Showa 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 Showa Corp filed Critical Showa Corp
Priority to JP2000345560A priority Critical patent/JP4803871B2/en
Publication of JP2002147580A publication Critical patent/JP2002147580A/en
Application granted granted Critical
Publication of JP4803871B2 publication Critical patent/JP4803871B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0483—Axle or inter-axle differentials
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
  • Turning (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、自動車の差動装置において特に差動ケースの内周面に摺接するピニオンギヤの潤滑に関する。
【０００２】
【従来の技術】
差動装置は、一般に差動ケースの回転駆動力がピニオンギヤとサイドギヤの噛合いを介して一対の出力軸にトルク配分して伝達される。
【０００３】
一対の出力軸に一体に回転可能に支持されたサイドギヤと噛合う一対のピニオンギヤは、差動ケースの回転軸に直交し該差動ケースに両端を支持されたピニオン軸に軸支され、差動ケースの内面に摺接して又は介装されたスラストワッシャに摺接して回転する。
【０００４】
このピニオンギヤの回転による焼き付けを防止して円滑に回転を行わせる潤滑構造として特開平９−４９５５７号公報には、差動ケースの内周面に摺接する各ピニオンギヤの背面に螺旋状の油溝を刻設している。
【０００５】
【発明が解決しようとする課題】
油溝はピニオンギヤの背面に刻設されて油溝全体が差動ケース内周面により溝開口を塞がれているので、この油溝にオイルが入り難く出難い構造となっていてオイルの循環が円滑に行われない。
【０００６】
したがってピニオンギヤの潤滑性に問題があるとともに、オイルの循環に伴う冷却性能も劣る。
また各ピニオンギヤに螺旋状の油溝を刻設することも面倒な作業である。
【０００７】
本発明は、斯かる点に鑑みなされたもので、その目的とする処は、ピニオンギヤと差動ケースとの摺接部分におけるオイルの循環を良くし潤滑性と冷却性の向上を図るとともに加工も容易な差動ケースの潤滑構造及び加工方法を供する点にある。
【０００８】
【課題を解決するための手段及び作用効果】
上記目的を達成するために、本発明は、差動ケースの回転軸に直交して前記差動ケースに両端を支持されたピニオン軸に回転可能に軸支された一対のピニオンギヤが、前記差動ケースの内周面に摺接して設けられ、前記差動ケースの回転軸上にあって前記差動ケースに軸支された一対の出力軸がそれぞれサイドギヤを一体に回転可能に支持し、前記差動ケースの回転駆動力が前記ピニオンギヤと前記サイドギヤの噛合いを介して一対の出力軸にトルク配分して伝達される差動装置において、前記差動ケースの前記ピニオンギヤの背面を支持する環状部分の球面をなす内周面に差動ケースの回転軸を中心軸とした円環状の油溝が、前記ピニオン軸から前記差動ケースの回転軸方向に離れた位置に前記ピニオンギヤの背面が摺接する部分を通って形成されている差動ケースの潤滑構造とした。
【０００９】
差動ケースの回転軸を中心軸とした円環状の油溝が、ピニオンギヤの背面の摺接する部分を通って形成されているので、差動ケースの内周面のオイルは回転による遠心力により油溝に集まり同油溝に案内されて流れ、ピニオンギヤの背面が摺接する部分におけるオイルの循環が円滑になされるので、十分なオイルの供給により常に良好な潤滑性が保たれるとともに、オイルの循環に伴う冷却効果も図ることができる。
【００１０】
良好な潤滑性によりピニオンギヤの背面と差動ケースの内周面との間に別途別部材を介装させる必要はなく、その組付け工程を省略できる。
【００１１】
請求項２記載の発明は、請求項１記載の差動ケースの潤滑構造において、前記油溝が複数本形成されたことを特徴とする。
油溝を複数本形成することで、ピニオンギヤの背面が摺接する部分におけるオイルの循環が益々良くなり、潤滑性及び冷却性ともに向上する。
【００１３】
差動ケースの内周面を球面状に切削加工する際にピニオンギヤの背面が摺接する部分を通る移動位置でバイトを遠心方向に所定量送り込む簡単な方法により、円環状の油溝を同時に形成することができ、作業効率が良い。
また種々の差動ケースに対して容易に適用することができ、汎用性に優れる。
【００１４】
【発明の実施の形態】
以下本発明に係る一実施の形態について図１ないし図６に基づいて説明する。
自動車の駆動伝達機構に適用された差動装置10及び差動装置10を収納して支持するギヤハウジング１とカバーハウジング２等が組付けられた状態の断面図を図１に示す。
【００１５】
推進軸３の回転を差動装置10のリングギヤ13に動力伝達するギヤ機構を支持するギヤハウジング１は、中央に軸受円孔を有する椀状側壁部１ａの一部が前方に膨出して推進軸３がベアリング４を介して嵌入軸支される軸受円筒部１ｂを形成している。
【００１６】
このギヤハウジング１の椀状側壁部１ａの開口端縁のフランジとカバーハウジング２の開口端縁が合わされてボルト５により締結され、ギヤハウジング１とカバーハウジング２が差動装置10を内部に収納して覆う。
【００１７】
差動装置10は、図１において椀状をした差動ケース11の右側開口を差動キャップ12が覆っており、差動ケース11と差動キャップ12との合わせ面に形成されたフランジ11ａ，12ａを複数のボルト14が締結するとともに、さらにリングギヤ13をも一緒にボルト14が共締めしている。
リングギヤ13は、環状のベベルギヤであり、前記推進軸３の端部に形成されたドライブピニオンギヤ３ａと噛合する。
【００１８】
差動ケース11と差動キャップ12には、それぞれ左右のアクスル軸６，７の端部が挿入される軸受円筒部11ｂ，12ｂを有し、同軸受円筒部11ｂ，12ｂにアクスル軸６，７が同軸に挿入され、内部に挿入されたアクスル軸６，７の端部にはサイドギヤ15，16がスプライン嵌合され一体に回転するようになっている。
【００１９】
左右のアクスル軸６，７の間を直交する形でピニオン軸17が椀状をした差動ケース11に両端を支持されて差動ケース11とともに一体に回転するようになっており、このピニオン軸17の両側部に一対のピニオンギヤ18，19が回転自在に軸支され、同ピニオンギヤ18，19が前記サイドギヤ15，16に互いに噛合して差動ギヤ機構を構成している。
【００２０】
この差動装置10における差動ケース11の軸受円筒部11ｂがカバーハウジング２の中央の軸受円孔にベアリング８を介して軸支され、差動キャップ12の軸受円筒部12ｂがギヤハウジング１の椀状側壁部１ａの中央軸受円孔にベアリング９を介して軸支され、合体した差動ケース11と差動キャップ12がアクスル軸６，７を中心軸に回転自在に支持されている。
【００２１】
すなわち差動装置10は、ギヤハウジング１とカバーハウジング２のハウジングによって覆われ、左右の軸受円筒部11ｂ、12ｂがベアリング８，９を介してハウジングに回動自在に支持されるとともに、左右の軸受円筒部11ｂ、12ｂに左右のアクスル軸６，７が挿入されて独立に回動自在に支持される。
【００２２】
したがって推進軸３の回転駆動力がドライブピニオンギヤ３ａとリングギヤ13の噛合を介して差動装置10の差動ケース11と差動キャップ12を回転させ、同差動ケース11と差動キャップ12の回転は、共に回転するピニオン軸17の回転がピニオンギヤ18，19とサイドギヤ15，16の噛合を介して一対のアクスル軸６，７にトルク配分されて伝達される。
【００２３】
ここに椀状をした差動ケース11は、ピニオン軸17の両端を支持する部分の内周面に、ピニオン軸17に軸支されるピニオンギヤ18，19の背面を摺接させてピニオンギヤ18，19を回転自在に支持している。
【００２４】
このピニオンギヤ18，19の回転を円滑に行わせるために、ピニオンギヤ18，19の背面と差動ケース11の内周面との間にオイルを供給する２本の油溝20，21が差動ケース11の内周面に形成されている。
【００２５】
２本の油溝20，21は、差動ケース11のピニオン軸17の両端を支持する環状部分の内周面にピニオンギヤ18，19の背面が摺接する部分を通る円環状をなして形成されている。
【００２６】
この差動ケース11の単体を図３ないし図５に図示する。
椀状をした差動ケース11の円筒部11ｃの一方の開口端縁にフランジ11ａが設けられ、他方の底壁中央に軸受円筒部11ｂが形成されており、円筒部11ｃの中心軸に直交する相対向した部分にピニオン軸17の両端がそれぞれ嵌入する円孔22，23が穿設されている。
【００２７】
なお円孔22，23と直角の角度をなす円筒部11ｃの部分には矩形孔25，26が形成されている。
差動ケース11の円筒部11ｃにおける円孔22，23を含んで軸方向所定幅の環状部分の内周面は球面を形成しており、図３および図５にその球面部分24を点模様で表示している。
【００２８】
球面部分24の球面は、差動ケース11の回転中心軸とピニオン軸17の交点を中心とする球面であり、この球面部分24の円孔22，23の周辺は、ピニオンギヤ18，19の背面が摺接するところであり、ピニオンギヤ18，19の背面も球面部分24と略同じ球面をなしてピニオンギヤ18，19がピニオン軸17を中心に球面部分24に摺接保持されながら回転することができる。
【００２９】
この環状の球面部分24に円孔22，23を挟んで２本の油溝20，21が、差動ケース11の回転中心軸を中心とする円環状に形成されている。
２本の油溝20，21は円孔22，23の周辺のピニオンギヤ18，19の背面が摺接する部分を通っている。
【００３０】
差動ケース11は、以上のような形状をしており、内部にピニオン軸17及びピニオンギヤ18，19を組付けると、図２に示すように差動ケース11の球面部分24のピニオンギヤ18，19の背面が摺接する部分を油溝20が通っている。
【００３１】
このように差動ケース11の回転方向に連続した油溝20，21が形成されているので、差動ケース11の内周面のオイルは回転による遠心力により油溝20，21に集まり、同油溝20，21に案内されてピニオンギヤ18，19の背面が摺接する部分におけるオイルの循環が円滑になされるので、十分なオイルの供給により常に良好な潤滑性が保たれる。
またオイルの循環に伴う冷却効果も期待できる。
【００３２】
良好な潤滑性が確保されるので、ピニオンギヤ18，19の背面と差動ケース11の内周面との間にスラストワッシャなどの部材を介装する必要はなく、その組付け工程を省略でき作業性もよい。
【００３３】
なお差動ケース11には円筒部11ｃに一対の矩形孔25，26が形成されているので、同矩形孔25，26より差動ケース11内にオイルが入り易いこともピニオンギヤ18，19の摺接部分におけるオイルの循環を良くするのに寄与している。
【００３４】
この差動ケース11の製造に際しては、まず鋳造により略形状が形成された後、図６に示すように旋盤チャック30が差動ケース11の軸受円筒部11ｂを挟持して軸受円筒部11ｂの軸を回転軸として回転するように保持され、円筒部11ｃ内にバイト31が挿入されて、刃部32が円筒部11ｃの内周面を切削加工する。
【００３５】
差動ケース11の内周面の前記球面部分24において、回転する内周面にバイト31の刃部32を軸方向に移動しながら径方向に所定の曲率で変位制御して球面を形成する。
この球面を形成する途中の軸方向所定位置で刃部32を遠心方向に所定量送り込むことにより油溝20，21を形成することができる。
【００３６】
このように油溝20，21を形成することが球面加工の途中で簡単に行うことができ、作業効率が格段に優れる。
油溝20，21を形成する位置も冷却性を考慮して最適位置に形成することが容易にできる。
【００３７】
また本実施の形態では差動ケース11の内周面に２本の油溝20，21を形成したが、１本でもよく、また３本以上設けることも簡単にできる。
【００３８】
この切削加工装置は、大小種々の差動ケースに対しても対応して球面加工することができるが、油溝を形成する位置も適当に変えることができるので、油溝形成についても簡単に対応することができ、汎用性に優れている。
【図面の簡単な説明】
【図１】本発明の一実施の形態に係る差動ケースを適用した差動装置の組付けられた状態を示す断面図である。
【図２】図１の要部拡大図である。
【図３】差動ケースの斜視図である。
【図４】同側面図である。
【図５】図４においてＶ−Ｖ線に沿って切断した断面図である。
【図６】差動ケースの加工の様子を示す断面図である。
【符号の説明】
１…ギヤハウジング、２…カバーハウジング、３…推進軸、４…ベアリング、５…ボルト、６，７…アクスル軸、８，９…ベアリング、
10…差動装置、11…差動ケース、12…差動キャップ、13…リングギヤ、14…ボルト、15，16…サイドギヤ、
20，21…油溝、22，23…円孔、24…球面部分、25，26…矩形孔、
30…旋盤チャック、31…バイト、32…刃部。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to lubrication of a pinion gear that is slidably contacted with an inner peripheral surface of a differential case, particularly in an automobile differential device.
[0002]
[Prior art]
In the differential device, the rotational driving force of the differential case is generally transmitted by distributing torque to a pair of output shafts through the engagement of the pinion gear and the side gear.
[0003]
A pair of pinion gears that mesh with side gears that are rotatably supported integrally with a pair of output shafts are pivotally supported by a pinion shaft that is orthogonal to the rotation shaft of the differential case and supported at both ends by the differential case. It rotates in sliding contact with the inner surface of the case or sliding contact with the interposed thrust washer.
[0004]
Japanese Laid-Open Patent Publication No. 9-49557 discloses a lubrication structure for preventing the seizure caused by the rotation of the pinion gear and smoothly rotating the pinion gear. Engraved.
[0005]
[Problems to be solved by the invention]
The oil groove is engraved on the back of the pinion gear and the entire oil groove is closed by the inner circumferential surface of the differential case. Is not done smoothly.
[0006]
Therefore, there is a problem in the lubricity of the pinion gear, and the cooling performance accompanying the oil circulation is also inferior.
It is also troublesome to engrave a spiral oil groove in each pinion gear.
[0007]
The present invention has been made in view of such points, and the object of the present invention is to improve the lubrication and cooling performance by improving the oil circulation in the sliding contact portion between the pinion gear and the differential case. It is in the point which provides the lubricating structure and processing method of an easy differential case.
[0008]
[Means for solving the problems and effects]
To achieve the above object, the present invention includes a pair of pinion gears rotatably supported on a pinion shaft supported at both ends to the differential case perpendicular to the axis of rotation of the differential case, the differential A pair of output shafts, which are provided in sliding contact with the inner peripheral surface of the case and are supported on the rotation shaft of the differential case and are pivotally supported by the differential case, respectively, support the side gears so as to be integrally rotatable. In the differential device in which the rotational driving force of the moving case is transmitted by distributing torque to a pair of output shafts through the engagement of the pinion gear and the side gear, an annular portion of the differential case that supports the back surface of the pinion gear An annular oil groove centering on the rotational axis of the differential case on the inner peripheral surface forming a spherical surface is a portion where the back surface of the pinion gear is in sliding contact with the position away from the pinion shaft in the rotational axis direction of the differential case Through It was a lubrication structure of a differential case that have been made.
[0009]
An annular oil groove centered on the rotation shaft of the differential case is formed through the sliding contact portion on the back of the pinion gear, so that the oil on the inner peripheral surface of the differential case is oiled by the centrifugal force of rotation. Since the oil circulates smoothly in the part where the back surface of the pinion gear slides and gathers in the groove and is guided by the oil groove, good lubricity is always maintained by supplying sufficient oil, and the oil circulation The cooling effect accompanying this can also be achieved.
[0010]
Due to good lubricity, it is not necessary to separately provide a separate member between the back surface of the pinion gear and the inner peripheral surface of the differential case, and the assembly process can be omitted.
[0011]
According to a second aspect of the present invention, in the lubricating structure for a differential case according to the first aspect, a plurality of the oil grooves are formed.
By forming a plurality of oil grooves, the circulation of oil in the portion where the back surface of the pinion gear is in sliding contact is improved, and both lubricity and cooling properties are improved.
[0013]
When cutting the inner peripheral surface of the differential case into a spherical shape, an annular oil groove is simultaneously formed by a simple method of feeding a predetermined amount of the cutting tool in the centrifugal direction at a moving position passing through the portion where the back surface of the pinion gear slides. Can work efficiently.
Moreover, it can be easily applied to various differential cases, and is excellent in versatility.
[0014]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, an embodiment according to the present invention will be described with reference to FIGS.
FIG. 1 shows a cross-sectional view of a state in which a differential device 10 applied to a drive transmission mechanism of an automobile and a gear housing 1 that houses and supports the differential device 10 and a cover housing 2 are assembled.
[0015]
A gear housing 1 that supports a gear mechanism for transmitting the rotation of the propulsion shaft 3 to the ring gear 13 of the differential device 10 has a portion of a bowl-shaped side wall portion 1a having a bearing circular hole in the center and bulges forward to propulsion shaft. 3 forms a bearing cylindrical portion 1 b that is fitted and supported via a bearing 4.
[0016]
The flange of the opening edge of the bowl-shaped side wall 1a of the gear housing 1 and the opening edge of the cover housing 2 are combined and fastened by a bolt 5, and the gear housing 1 and the cover housing 2 accommodate the differential device 10 inside. Cover.
[0017]
In the differential device 10, a differential cap 12 covers the right opening of the bowl-shaped differential case 11 in FIG. 1, and flanges 11a formed on the mating surfaces of the differential case 11 and the differential cap 12 are provided. A plurality of bolts 14 are fastened to 12a, and the bolts 14 are fastened together with the ring gear 13.
The ring gear 13 is an annular bevel gear and meshes with a drive pinion gear 3 a formed at the end of the propulsion shaft 3.
[0018]
The differential case 11 and the differential cap 12 have bearing cylindrical portions 11b and 12b into which the ends of the left and right axle shafts 6 and 7 are inserted, respectively. The axle shafts 6 and 7 are connected to the cylindrical bearing portions 11b and 12b. Are inserted coaxially, and side gears 15 and 16 are spline-fitted to end portions of the axle shafts 6 and 7 inserted therein so as to rotate together.
[0019]
Both ends of the pinion shaft 17 are supported by a saddle-shaped differential case 11 that is orthogonal to the left and right axle shafts 6 and 7 and rotates together with the differential case 11. This pinion shaft A pair of pinion gears 18 and 19 are rotatably supported on both side portions of 17, and the pinion gears 18 and 19 mesh with the side gears 15 and 16 to constitute a differential gear mechanism.
[0020]
In the differential device 10, the bearing cylindrical portion 11 b of the differential case 11 is pivotally supported through a bearing circular hole in the center of the cover housing 2 via the bearing 8, and the bearing cylindrical portion 12 b of the differential cap 12 is supported by the flange of the gear housing 1. A differential case 11 and a differential cap 12 which are pivotally supported by a central bearing circular hole of the side wall portion 1a via a bearing 9 are rotatably supported around the axle shafts 6 and 7 as a central axis.
[0021]
That is, the differential device 10 is covered by the housings of the gear housing 1 and the cover housing 2, and the left and right bearing cylindrical portions 11 b and 12 b are rotatably supported by the housing via the bearings 8 and 9, and the left and right bearings The left and right axle shafts 6 and 7 are inserted into the cylindrical portions 11b and 12b and are supported so as to be independently rotatable.
[0022]
Therefore, the rotational driving force of the propulsion shaft 3 rotates the differential case 11 and the differential cap 12 of the differential device 10 through the engagement of the drive pinion gear 3a and the ring gear 13, and the differential case 11 and the differential cap 12 rotate. The rotation of the pinion shaft 17 that rotates together with the pinion gears 18 and 19 and the side gears 15 and 16 is transmitted through torque distribution to the pair of axle shafts 6 and 7.
[0023]
Here, the bowl-shaped differential case 11 is configured such that the back surfaces of the pinion gears 18 and 19 supported by the pinion shaft 17 are in sliding contact with the inner peripheral surface of the portion supporting both ends of the pinion shaft 17. Is supported rotatably.
[0024]
In order to smoothly rotate the pinion gears 18, 19, two oil grooves 20, 21 for supplying oil between the back surfaces of the pinion gears 18, 19 and the inner peripheral surface of the differential case 11 are provided in the differential case. 11 is formed on the inner peripheral surface.
[0025]
The two oil grooves 20 and 21 are formed in an annular shape that passes through the portion where the rear surfaces of the pinion gears 18 and 19 are in sliding contact with the inner peripheral surface of the annular portion that supports both ends of the pinion shaft 17 of the differential case 11. Yes.
[0026]
A single unit of the differential case 11 is shown in FIGS.
A flange 11a is provided at one opening edge of the cylindrical portion 11c of the bowl-shaped differential case 11, and a bearing cylindrical portion 11b is formed at the center of the other bottom wall, and is orthogonal to the central axis of the cylindrical portion 11c. Circular holes 22 and 23 into which both ends of the pinion shaft 17 are respectively fitted are formed in the opposed portions.
[0027]
In addition, rectangular holes 25 and 26 are formed in a portion of the cylindrical portion 11c that forms an angle perpendicular to the circular holes 22 and 23.
The inner peripheral surface of the annular portion having a predetermined axial width including the circular holes 22 and 23 in the cylindrical portion 11c of the differential case 11 forms a spherical surface, and the spherical portion 24 is shown in a dotted pattern in FIGS. it's shown.
[0028]
The spherical surface of the spherical surface portion 24 is a spherical surface centered on the intersection of the rotation center axis of the differential case 11 and the pinion shaft 17, and the back surfaces of the pinion gears 18 and 19 are located around the circular holes 22 and 23 of the spherical surface portion 24. The back surfaces of the pinion gears 18 and 19 also have substantially the same spherical surface as the spherical portion 24, and the pinion gears 18 and 19 can rotate while being held in sliding contact with the spherical portion 24 about the pinion shaft 17.
[0029]
Two oil grooves 20 and 21 are formed in an annular shape around the rotation center axis of the differential case 11 with the annular spherical portions 24 sandwiching the circular holes 22 and 23.
The two oil grooves 20 and 21 pass through portions where the rear surfaces of the pinion gears 18 and 19 around the circular holes 22 and 23 are in sliding contact.
[0030]
The differential case 11 has the shape as described above, and when the pinion shaft 17 and the pinion gears 18 and 19 are assembled inside, the pinion gears 18 and 19 of the spherical surface portion 24 of the differential case 11 as shown in FIG. The oil groove 20 passes through the portion where the back surface of the oil slidably contacts.
[0031]
Since the oil grooves 20 and 21 that are continuous in the rotation direction of the differential case 11 are formed in this way, the oil on the inner peripheral surface of the differential case 11 gathers in the oil grooves 20 and 21 due to the centrifugal force caused by the rotation. Since the oil is smoothly circulated in the portion where the back surfaces of the pinion gears 18 and 19 are slidably contacted by the oil grooves 20 and 21, good lubricity is always maintained by supplying sufficient oil.
Moreover, the cooling effect accompanying oil circulation can also be expected.
[0032]
Since good lubricity is ensured, there is no need to insert a member such as a thrust washer between the back surface of the pinion gears 18 and 19 and the inner peripheral surface of the differential case 11, and the assembly process can be omitted. Good.
[0033]
Since the differential case 11 is formed with a pair of rectangular holes 25 and 26 in the cylindrical portion 11c, oil can easily enter the differential case 11 through the rectangular holes 25 and 26. It contributes to improving the oil circulation in the contact area.
[0034]
In manufacturing the differential case 11, first, after a substantial shape is formed by casting, a lathe chuck 30 sandwiches the bearing cylindrical portion 11b of the differential case 11 as shown in FIG. Is held so as to rotate about the rotation axis, the cutting tool 31 is inserted into the cylindrical portion 11c, and the blade portion 32 cuts the inner peripheral surface of the cylindrical portion 11c.
[0035]
In the spherical surface portion 24 of the inner peripheral surface of the differential case 11, a spherical surface is formed by controlling displacement with a predetermined curvature in the radial direction while moving the blade portion 32 of the cutting tool 31 in the axial direction on the rotating inner peripheral surface.
The oil grooves 20 and 21 can be formed by feeding the blade portion 32 by a predetermined amount in the centrifugal direction at a predetermined position in the axial direction in the course of forming the spherical surface.
[0036]
Thus, the formation of the oil grooves 20 and 21 can be easily performed during the spherical processing, and the working efficiency is remarkably excellent.
The positions where the oil grooves 20 and 21 are formed can be easily formed at the optimum positions in consideration of cooling performance.
[0037]
In the present embodiment, the two oil grooves 20 and 21 are formed on the inner peripheral surface of the differential case 11, but one or three or more oil grooves can be easily provided.
[0038]
This cutting device can be used for spherical machining in response to large and small differential cases, but the position to form the oil groove can also be changed appropriately, so it can be easily adapted to oil groove formation. Can be excellent in versatility.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing an assembled state of a differential device to which a differential case according to an embodiment of the present invention is applied.
FIG. 2 is an enlarged view of a main part of FIG.
FIG. 3 is a perspective view of a differential case.
FIG. 4 is a side view of the same.
5 is a cross-sectional view taken along line VV in FIG. 4. FIG.
FIG. 6 is a cross-sectional view showing how the differential case is processed.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Gear housing, 2 ... Cover housing, 3 ... Propulsion shaft, 4 ... Bearing, 5 ... Bolt, 6, 7 ... Axle shaft, 8, 9 ... Bearing
10 ... Differential gear, 11 ... Differential case, 12 ... Differential cap, 13 ... Ring gear, 14 ... Bolt, 15, 16 ... Side gear,
20, 21 ... Oil groove, 22, 23 ... Round hole, 24 ... Spherical part, 25, 26 ... Rectangular hole,
30 ... Lathe chuck, 31 ... Bite, 32 ... Blade.

Claims (2)

差動ケースの回転軸に直交して前記差動ケースに両端を支持されたピニオン軸に回転可能に軸支された一対のピニオンギヤが、前記差動ケースの内周面に摺接して設けられ、
前記差動ケースの回転軸上にあって前記差動ケースに軸支された一対の出力軸がそれぞれサイドギヤを一体に回転可能に支持し、
前記差動ケースの回転駆動力が前記ピニオンギヤと前記サイドギヤの噛合いを介して一対の出力軸にトルク配分して伝達される差動装置において、
前記差動ケースの前記ピニオンギヤの背面を支持する環状部分の球面をなす内周面に差動ケースの回転軸を中心軸とした円環状の油溝が、前記ピニオン軸から前記差動ケースの回転軸方向に離れた位置に前記ピニオンギヤの背面が摺接する部分を通って形成されていることを特徴とする差動ケースの潤滑構造。 A pair of pinion gears rotatably supported by pinion shafts supported at both ends by the differential case perpendicular to the rotation axis of the differential case are provided in sliding contact with the inner peripheral surface of the differential case,
A pair of output shafts on the rotation shaft of the differential case and supported by the differential case support the side gears so as to be integrally rotatable,
In the differential device in which the rotational driving force of the differential case is transmitted by distributing torque to a pair of output shafts through the engagement of the pinion gear and the side gear,
An annular oil groove centering on the rotational axis of the differential case is formed on the inner peripheral surface of the annular portion that supports the back surface of the pinion gear of the differential case, and the differential case rotates from the pinion shaft. 2. A lubricating structure for a differential case, wherein the lubricating structure is formed through a portion where the back surface of the pinion gear is slidably contacted at a position separated in the axial direction . 前記油溝は複数本形成されたことを特徴とする請求項１記載の差動ケースの潤滑構造。  The differential case lubricating structure according to claim 1, wherein a plurality of the oil grooves are formed.
JP2000345560A 2000-11-13 2000-11-13 Lubrication structure of differential case and its processing method Expired - Fee Related JP4803871B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2000345560A JP4803871B2 (en) 2000-11-13 2000-11-13 Lubrication structure of differential case and its processing method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2000345560A JP4803871B2 (en) 2000-11-13 2000-11-13 Lubrication structure of differential case and its processing method

Publications (2)

Publication Number Publication Date
JP2002147580A JP2002147580A (en) 2002-05-22
JP4803871B2 true JP4803871B2 (en) 2011-10-26

Family

ID=18819572

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2000345560A Expired - Fee Related JP4803871B2 (en) 2000-11-13 2000-11-13 Lubrication structure of differential case and its processing method

Country Status (1)

Country Link
JP (1) JP4803871B2 (en)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015224052A1 (en) 2014-12-03 2016-06-09 Musashi Seimitsu Industry Co., Ltd. differential gear
DE102015224050A1 (en) 2014-12-03 2016-06-09 Musashi Seimitsu Industry Co., Ltd. differential gear
DE102015224892A1 (en) 2014-12-12 2016-06-16 Musashi Seimitsu Industry Co., Ltd. differential gear
DE102016205228A1 (en) 2015-03-31 2016-10-06 Musashi Seimitsu Industry Co., Ltd. differential device
DE102016205231A1 (en) 2015-03-31 2016-10-06 Musashi Seimitsu Industry Co., Ltd. Vehicle differential device
DE102016210694A1 (en) 2015-06-18 2016-12-22 Musashi Seimitsu Industry Co., Ltd. differential device
DE102016210699A1 (en) 2015-06-18 2016-12-22 Musashi Seimitsu Industry Co., Ltd. differential device
DE102016218689A1 (en) 2015-10-07 2017-04-13 Musashi Seimitsu Industry Co., Ltd. differential device
US9810306B2 (en) 2014-10-22 2017-11-07 Musashi Seimitsu Industry Co., Ltd. Differential device
US9903464B2 (en) 2014-10-22 2018-02-27 Musashi Seimitsu Industry Co., Ltd. Differential device
US10006532B2 (en) 2014-10-22 2018-06-26 Musashi Seimitsu Industry Co., Ltd. Differential device
US10221928B2 (en) 2015-12-18 2019-03-05 Musashi Seimitsu Industry Co., Ltd. Differential device

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2004036088A1 (en) * 2002-10-21 2006-02-16 株式会社音戸工作所 Vehicle differential
JP4572133B2 (en) * 2005-03-28 2010-10-27 富士機械製造株式会社 Internal processing equipment for hollow workpieces
JP2007002885A (en) * 2005-06-22 2007-01-11 Aisin Takaoka Ltd Differential gear
JP6847874B2 (en) * 2018-01-18 2021-03-24 武蔵精密工業株式会社 Differential device
JP2019173914A (en) * 2018-03-29 2019-10-10 武蔵精密工業株式会社 Differential gear

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58116847U (en) * 1982-02-03 1983-08-09 三菱自動車工業株式会社 differential gear
JPH062078Y2 (en) * 1986-05-31 1994-01-19 スズキ株式会社 Differential gear lubricator
JPH0949557A (en) * 1995-08-07 1997-02-18 Tochigi Fuji Ind Co Ltd Differential limit device
JP2000135602A (en) * 1998-10-30 2000-05-16 Riken Seiko Kk Curved surface cutting method and piston

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10006532B2 (en) 2014-10-22 2018-06-26 Musashi Seimitsu Industry Co., Ltd. Differential device
DE102015220521B4 (en) * 2014-10-22 2021-06-02 Musashi Seimitsu Industry Co., Ltd. Narrow bevel gear differential with large side gears
US9903464B2 (en) 2014-10-22 2018-02-27 Musashi Seimitsu Industry Co., Ltd. Differential device
DE102015220518B4 (en) * 2014-10-22 2021-06-02 Musashi Seimitsu Industry Co., Ltd. Differential gear with oil retention parts
US9810306B2 (en) 2014-10-22 2017-11-07 Musashi Seimitsu Industry Co., Ltd. Differential device
DE102015220522B4 (en) * 2014-10-22 2021-07-01 Musashi Seimitsu Industry Co., Ltd. Narrow differential gear with large side gears
DE102015224052A1 (en) 2014-12-03 2016-06-09 Musashi Seimitsu Industry Co., Ltd. differential gear
US9897188B2 (en) 2014-12-03 2018-02-20 Musashi Seimitsu Industry Co., Ltd. Differential device
DE102015224050A1 (en) 2014-12-03 2016-06-09 Musashi Seimitsu Industry Co., Ltd. differential gear
DE102015224892B4 (en) 2014-12-12 2021-10-14 Musashi Seimitsu Industry Co., Ltd. Oil supply to a narrow differential gear
US9739364B2 (en) 2014-12-12 2017-08-22 Musashi Seimitsu Industry Co., Ltd. Differential device
DE102015224892A1 (en) 2014-12-12 2016-06-16 Musashi Seimitsu Industry Co., Ltd. differential gear
CN106015510A (en) * 2015-03-31 2016-10-12 武藏精密工业株式会社 Vehicle differential device
DE102016205231A1 (en) 2015-03-31 2016-10-06 Musashi Seimitsu Industry Co., Ltd. Vehicle differential device
DE102016205228A1 (en) 2015-03-31 2016-10-06 Musashi Seimitsu Industry Co., Ltd. differential device
US9856972B2 (en) 2015-03-31 2018-01-02 Musashi Seimitsu Industry Co., Ltd. Differential device
DE102016210694A1 (en) 2015-06-18 2016-12-22 Musashi Seimitsu Industry Co., Ltd. differential device
US9863519B2 (en) 2015-06-18 2018-01-09 Musashi Seimitsu Industry Co., Ltd. Differential device
DE102016210699A1 (en) 2015-06-18 2016-12-22 Musashi Seimitsu Industry Co., Ltd. differential device
US10167940B2 (en) 2015-10-07 2019-01-01 Musashi Seimitsu Industry Co., Ltd. Differential device
DE102016218689A1 (en) 2015-10-07 2017-04-13 Musashi Seimitsu Industry Co., Ltd. differential device
US10221928B2 (en) 2015-12-18 2019-03-05 Musashi Seimitsu Industry Co., Ltd. Differential device

Also Published As

Publication number Publication date
JP2002147580A (en) 2002-05-22

Similar Documents

Publication Publication Date Title
JP4803871B2 (en) Lubrication structure of differential case and its processing method
US10871091B2 (en) Power system
EP1130288B1 (en) Differential apparatus with oil lubrication passages
US20200282828A1 (en) Vehicle driving apparatus
JP4981694B2 (en) Power transmission device
EP0289610B1 (en) Bearing structure of high speed motor
JP2016191418A (en) Differential device
JPH11351360A (en) Lubricating structure in differential device
US20180172130A1 (en) Power system and method of manufacturing the same
JP4581578B2 (en) Rotating shaft support device
JP2004090181A (en) Manufacturing method of differential case of differential gear
US20230272851A1 (en) Power transmission unit
JP6547620B2 (en) Lubrication structure of differential gear device
JP2019173914A (en) Differential gear
JPH0271946A (en) Spindle-unit for milling-drilling machine
JP2018100748A (en) Power device
US10760676B2 (en) Differential apparatus
JP2007100821A (en) Reduction gear with clutch
JP6350572B2 (en) Differential device and manufacturing method thereof
CN215806130U (en) Differential gear
JP7317455B2 (en) stiffening structure of the case
JP3217622B2 (en) Differential device
JP2004286194A (en) Differential case and differential device
JP7309292B2 (en) Case oil passage structure
JPH1178561A (en) Lubricating structure for differential limiting device

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20070821

RD04 Notification of resignation of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7424

Effective date: 20090421

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20100415

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20100420

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20100610

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20101221

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20110215

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20110809

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20110809

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20140819

Year of fee payment: 3

LAPS Cancellation because of no payment of annual fees