JPH07144548A - Lubricating device for differential gear bearing - Google Patents

Lubricating device for differential gear bearing

Info

Publication number
JPH07144548A
JPH07144548A JP6220735A JP22073594A JPH07144548A JP H07144548 A JPH07144548 A JP H07144548A JP 6220735 A JP6220735 A JP 6220735A JP 22073594 A JP22073594 A JP 22073594A JP H07144548 A JPH07144548 A JP H07144548A
Authority
JP
Japan
Prior art keywords
tapered roller
lubricating oil
bearing
differential
differential case
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP6220735A
Other languages
Japanese (ja)
Other versions
JP2765487B2 (en
Inventor
Takaaki Shiratani
隆明 白谷
Moichi Chiba
茂一 千葉
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.)
NSK Ltd
Original Assignee
NSK Ltd
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 NSK Ltd filed Critical NSK Ltd
Priority to JP6220735A priority Critical patent/JP2765487B2/en
Publication of JPH07144548A publication Critical patent/JPH07144548A/en
Application granted granted Critical
Publication of JP2765487B2 publication Critical patent/JP2765487B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/664—Retaining the liquid in or near the bearing
    • F16C33/6651—Retaining the liquid in or near the bearing in recesses or cavities provided in retainers, races or rolling elements
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/667—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to conditioning, e.g. cooling, filtering
    • 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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Motor Power Transmission Devices (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PURPOSE:To prevent an excessive amount of lubrication oil from flowing at the time of high speed running and to prevent lubricating oil from being insufficient at the time of low speed running. CONSTITUTION:Baffle plates 15, 17 are provided in both end opening parts of tapered roller bearings 2, 2 for supporting a pinion shaft 3. Each baffle plate 15, 17 impedes circulating an excessive amount of lubricating oil in the case of rotating the pinion shaft 3 at a high speed. In the case of rotation at a low speed, lubricating oil provided in each tapered roller bearing 2, 2 is prevented from being washed away.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】この発明に係るデファレンシャル
用軸受の潤滑装置は、自動車の駆動系に設けられるデフ
ァレンシャル（差動装置、或は最終減速機）中に組み込
まれる軸受の潤滑に関する。特に本発明は、この様な潤
滑装置による潤滑油の供給量を適正範囲内に維持する事
で、軸受部分の耐久性向上を図る。BACKGROUND OF THE INVENTION 1. Field of the Invention The lubricating device for a differential bearing according to the present invention relates to the lubrication of a bearing incorporated in a differential (differential device or final reduction gear) provided in a drive system of an automobile. In particular, the present invention aims to improve the durability of the bearing portion by maintaining the amount of lubricating oil supplied by such a lubricating device within an appropriate range.

【０００２】[0002]

【従来の技術】自動車のプロペラシャフトと車輪の駆動
軸（アクセル軸）との間には、デファレンシャルを設け
る事で、プロペラシャフトと駆動軸との間での動力伝達
を行なうと共に、進路変更に伴う左右の駆動輪の回転速
度差を吸収し、更に動力の向きを変え、最終的な減速を
行なう様にしている。この様なデファレンシャルは、例
えば図５に示す様に構成されている。2. Description of the Related Art A differential is provided between a propeller shaft of an automobile and a drive shaft (accelerator shaft) of a wheel so that power is transmitted between the propeller shaft and the drive shaft and the course is changed. The difference in rotational speed between the left and right driving wheels is absorbed, and the direction of power is further changed to achieve final deceleration. Such a differential is configured as shown in FIG. 5, for example.

【０００３】デファレンシャルケース１の一端に、１対
の円錐ころ軸受２、２により回転自在に支持されたピニ
オン軸３の端部に固設されたピニオンギヤ４と、デファ
レンシャルケース１内に回転自在に支承したリングギヤ
５とを噛合させる事で、ドライブシャフト（図示省略）
の回転力をピニオンギヤ４に伝達自在としている。更
に、このピニオンギヤ４の回転力を、リングギヤ５を介
して、別の円錐ころ軸受によりデファレンシャルケース
１に支承された左右の駆動軸（図示省略）に伝達自在と
している。この様に構成されるデファレンシャルは、自
動車の走行時には各部分が高速で回転する為、ピニオン
軸３を支承している円錐ころ軸受２、２を潤滑する必要
がある。A pinion gear 4 fixed to an end of a pinion shaft 3 which is rotatably supported by a pair of tapered roller bearings 2 and 2 at one end of a differential case 1, and a rotatably supported inside the differential case 1. Drive shaft (not shown) by meshing with the ring gear 5
The rotational force of is transmitted to the pinion gear 4. Further, the rotational force of the pinion gear 4 is freely transmitted to the left and right drive shafts (not shown) supported by the differential case 1 by another tapered roller bearing via the ring gear 5. In the differential configured as described above, since each part rotates at high speed when the vehicle is running, it is necessary to lubricate the tapered roller bearings 2, 2 supporting the pinion shaft 3.

【０００４】この為従来から、デファレンシャルケース
１の底部に溜めた潤滑油を、自動車の走行時に回転する
リングギヤ５によってデファレンシャルケース１の上部
に迄跳ね上げ、更にこの跳ね上げられた潤滑油を円錐こ
ろ軸受２、２に送り込み、各円錐ころ軸受２、２を通過
した潤滑油をデファレンシャルケース１の底部に還流さ
せる事で、各円錐ころ軸受２、２の潤滑を連続的に行な
う潤滑装置が使用されている。デファレンシャルケース
１の底部に溜めた潤滑油中に下部を浸けたリングギヤ５
を、図５に矢印ａで示す様に回転させた場合、上記潤滑
油はリングギヤ５に跳ね上げられて、同図に矢印ｂで示
す様に、２個の円錐ころ軸受２、２の間部分に送り込ま
れ、更に各円錐ころ軸受２、２内に進入する。各円錐こ
ろ軸受２、２内に進入した潤滑油は、遠心力の作用によ
って、各円錐ころ軸受２、２の小径端（図５の右側の軸
受の場合、左端）から大径端（同じく右端）に向けて流
れ（円錐ころ軸受回転時のポンプ作用）、同図に矢印ｃ
で示す様に、各円錐ころ軸受２、２から排出されて、デ
ファレンシャルケース１の底部に還流する。以下、この
作用を連続して繰り返す事により、各円錐ころ軸受２、
２を潤滑する。For this reason, conventionally, the lubricating oil accumulated at the bottom of the differential case 1 is sprung up to the upper part of the differential case 1 by the ring gear 5 which rotates when the vehicle is running, and the spoiled lubricating oil is further tapered. A lubricating device is used that continuously lubricates the tapered roller bearings 2 and 2 by feeding the lubricating oil that has passed through the bearings 2 and 2 and passed through the tapered roller bearings 2 and 2 back to the bottom of the differential case 1. ing. Ring gear 5 with the lower part immersed in the lubricating oil stored in the bottom of the differential case 1.
5 is rotated as indicated by an arrow a in FIG. 5, the lubricating oil is splashed up by the ring gear 5 and, as indicated by an arrow b in the figure, a portion between the two tapered roller bearings 2, 2. And further enters into each tapered roller bearing 2, 2. The lubricating oil that has entered the tapered roller bearings 2 and 2 is moved from the small diameter end (the left end in the case of the right bearing in FIG. 5) of the tapered roller bearings 2 and 2 to the large diameter end (also the right end) by the action of centrifugal force. ) (Pump action when the tapered roller bearing rotates), arrow c in the figure
As shown by, it is discharged from each of the tapered roller bearings 2 and and is returned to the bottom of the differential case 1. Hereinafter, by repeating this operation continuously, each tapered roller bearing 2,
Lubricate 2.

【０００５】[0005]

【発明が解決しようとする課題】ところが、上述の様に
構成され作用するデファレンシャル用軸受の潤滑装置に
於いては、従来次に述べる様な不都合を生じた。即ち、
自動車が高速で走行する場合は、ドライブシャフトに結
合されるピニオン軸３が高速で回転し、当然にリングギ
ヤ５も高速で回転する。従って、このリングギヤ５によ
って跳ね上げられ、図５に矢印ｂで示す様にして各円錐
ころ軸受２、２に送り込まれる潤滑油の量も多くなる。
一方、ピニオン軸３や駆動軸の回転数が多くなっても、
円錐ころ軸受２、２の安定した運転に必要な潤滑油の量
はあまり増えず、リングギヤ５の高速回転に伴って各円
錐ころ軸受２、２に送り込まれる潤滑油の量が増えて
も、或る程度以上の量は、潤滑性能の面からは無駄にな
る。However, in the lubricating device for a differential bearing which is constructed and operates as described above, the following disadvantages have conventionally occurred. That is,
When the vehicle travels at high speed, the pinion shaft 3 connected to the drive shaft rotates at high speed, and naturally the ring gear 5 also rotates at high speed. Therefore, the amount of lubricating oil that is sprung up by the ring gear 5 and is sent to the tapered roller bearings 2 and 2 as shown by the arrow b in FIG. 5 also increases.
On the other hand, even if the number of rotations of the pinion shaft 3 and the drive shaft increases,
The amount of lubricating oil required for stable operation of the tapered roller bearings 2 and 2 does not increase so much, and even if the amount of lubricating oil sent to each tapered roller bearing 2 and 2 increases as the ring gear 5 rotates at high speed, or If the amount is larger than that, it is wasted in terms of lubrication performance.

【０００６】各円錐ころ軸受２、２に必要以上の潤滑油
が送り込まれる事自体は、特に問題とはならない。とこ
ろが、潤滑油中にはデファレンシャルを構成する各部品
の摩耗粉や研磨剤（各部品の表面仕上後、落とし切れな
いもの。）等の異物が混入している。この為、必要以上
の潤滑油の循環は、それだけ異物と円錐ころ軸受２、２
との接触の機会が増えて、円錐ころ軸受２、２の摩耗を
促進し、予圧が減じてギヤの噛み合い音の増大を招き、
好ましくない。又、異物は、円錐ころ軸受２、２の軌道
面を傷付け、軸受から発生する音（レース音）や振動の
増大を招く。It is not a particular problem that the excess amount of lubricating oil is fed into each tapered roller bearing 2, 2. However, foreign matter such as abrasion powder and abrasives (which cannot be completely removed after finishing the surface of each component) of each component constituting the differential is mixed in the lubricating oil. For this reason, the circulation of the lubricating oil more than necessary causes the foreign matter and the tapered roller bearings 2, 2 to that extent.
The chances of contact with the bearings increase, the wear of the tapered roller bearings 2 and 2 is promoted, the preload is reduced, and the gear engagement noise increases,
Not preferable. Further, the foreign matter damages the raceway surfaces of the tapered roller bearings 2, 2 and causes an increase in noise (race noise) and vibration generated from the bearings.

【０００７】反対に、自動車が低速で走行し、リングギ
ヤ５の回転に伴って各円錐ころ軸受２、２に送り込まれ
る潤滑油の量が少なくなり、前記ポンプ作用によって各
円錐ころ軸受２、２から排出される潤滑油の量が、供給
される潤滑油の量よりも多くなると、円錐ころ軸受２、
２内の潤滑油が不足して、軸受が焼き付く原因となって
しまう。On the other hand, when the automobile runs at a low speed and the amount of lubricating oil fed to the tapered roller bearings 2 and 2 decreases as the ring gear 5 rotates, the pumping action causes the tapered roller bearings 2 and 2 to move. If the amount of lubricating oil discharged exceeds the amount of lubricating oil supplied, the tapered roller bearing 2,
Lubricating oil in 2 becomes insufficient, which causes seizure of the bearing.

【０００８】本発明のデファレンシャル用軸受の潤滑装
置は、上述の様な不都合を何れも解消するものである。The lubricating device for a differential bearing according to the present invention eliminates any of the above inconveniences.

【０００９】[0009]

【課題を解決するための手段】本発明のデファレンシャ
ル用軸受の潤滑装置は、前述した従来の潤滑装置の場合
と同様に、デファレンシャルケース内に回転自在に設け
たリングギヤの下部を、デファレンシャルケースの底部
に溜めた潤滑油中に浸ける事で、この潤滑油をデファレ
ンシャルケースの上部に迄跳ね上げて、ピニオン軸をこ
のデファレンシャルケースに支承する円錐ころ軸受に送
り込み、円錐ころ軸受を通過した潤滑油をデファレンシ
ャルケースの底部に還流させる様に構成している。As in the case of the conventional lubrication apparatus described above, the differential bearing lubrication apparatus of the present invention has a lower portion of a ring gear rotatably provided in the differential case and a bottom portion of the differential case. By soaking it in the lubricating oil stored in the differential case, it jumps up to the upper part of the differential case, sends the pinion shaft to the tapered roller bearing supported on this differential case, and the lubricating oil that passes through the tapered roller bearing is differential. It is configured to flow back to the bottom of the case.

【００１０】特に、本発明のデファレンシャル用軸受の
潤滑装置に於いては、潤滑油の流路となる円錐ころ軸受
の両端開口部の少なくとも一方に、潤滑油の流通量を制
限する邪魔板を設けている。In particular, in the differential bearing lubrication device of the present invention, a baffle plate for restricting the flow rate of the lubricating oil is provided in at least one of the opening portions at both ends of the tapered roller bearing, which serves as the lubricating oil passage. ing.

【００１１】[0011]

【作用】上述の様に構成される本発明のデファレンシャ
ル用軸受の潤滑装置の潤滑作用自体は、前述した従来の
潤滑装置と同様である。特に、本発明の潤滑装置の場合
には、高速走行に伴ってリングギヤが高速回転し、この
リングギヤから各円錐ころ軸受に送られる潤滑油の量が
増えた場合に於いても、邪魔板により、必要以上の潤滑
油が各円錐ころ軸受に送り込まれる事が阻止される。こ
の為、各円錐ころ軸受に必要以上の潤滑油が送り込まれ
る事がなく、上記各軸受の摩耗が促進される事が防止さ
れると同時に、異物によるレース音の増大を防止する。The lubricating operation of the differential bearing lubricating device of the present invention constructed as described above is the same as that of the conventional lubricating device described above. In particular, in the case of the lubricating device of the present invention, the ring gear rotates at high speed with high-speed running, and even when the amount of lubricating oil sent from this ring gear to each tapered roller bearing increases, due to the baffle plate, It is prevented that more lubricating oil than necessary is fed into each tapered roller bearing. Therefore, more lubricating oil than necessary is not sent to each tapered roller bearing, and it is possible to prevent the abrasion of each bearing from being promoted, and at the same time, to prevent an increase in race noise due to foreign matter.

【００１２】又、邪魔板は、潤滑油が円錐ころ軸受内を
流れる事に対する抵抗となって、軸受内に送り込まれた
潤滑油が短時間の間に流失するのを防止する。この為、
自動車の低速走行に伴い、リングギヤから各円錐ころ軸
受に送り込まれる潤滑油の量が減少した場合に於いて
も、各軸受が、潤滑油不足により焼き付きを起こす事が
なくなる。Further, the baffle plate serves as a resistance against the flow of the lubricating oil in the tapered roller bearing, and prevents the lubricating oil fed into the bearing from flowing out in a short time. Therefore,
Even when the amount of lubricating oil fed from the ring gear to each tapered roller bearing decreases as the vehicle runs at low speed, each bearing will not seize due to insufficient lubricating oil.

【００１３】[0013]

【実施例】図１〜３は本発明の第一実施例を示してい
る。先ず、図１で、デファレンシャルケース１内に回転
自在に設けたリングギヤ５の下部は、デファレンシャル
ケース１の底部に溜めた潤滑油中に浸漬している。従っ
て、自動車の運転に伴ってリングギヤ５が回転した場合
に、リングギヤ５に付着した潤滑油が、デファレンシャ
ルケース１の上部に迄跳ね上げられる。1 to 3 show a first embodiment of the present invention. First, in FIG. 1, the lower part of the ring gear 5 rotatably provided in the differential case 1 is immersed in the lubricating oil stored in the bottom part of the differential case 1. Therefore, when the ring gear 5 rotates with the operation of the automobile, the lubricating oil attached to the ring gear 5 is splashed up to the upper part of the differential case 1.

【００１４】デファレンシャルケース１の内部に設けた
軸受保持部９には、間隔をあけて１対の円錐ころ軸受
２、２を設けている。そして、これら両円錐ころ軸受
２、２によりピニオン軸３を、回転自在に支持してい
る。このピニオン軸３は、上記デファレンシャルケース
１の一端をシール体を介して油密に貫通し、このデファ
レンシャルケース１内に挿入されている。各円錐ころ軸
受２、２は、上記ピニオン軸３の外周面に固定の内輪１
０と、上記軸受保持部９の内側に固定の外輪１１との間
に、それぞれ複数の円錐ころ１２、１２を、保持器１３
により位置決めした状態で装着している。又、上記両円
錐ころ軸受２、２の内輪１０、１０の端面同士の間には
間座１４を設け、両軸受２、２の位置決めを図ってい
る。A bearing holding portion 9 provided inside the differential case 1 is provided with a pair of tapered roller bearings 2 and 2 with a space therebetween. The tapered roller bearings 2 and 2 rotatably support the pinion shaft 3. The pinion shaft 3 penetrates one end of the differential case 1 in an oil-tight manner via a seal body, and is inserted into the differential case 1. Each of the tapered roller bearings 2 and 2 has an inner ring 1 fixed to the outer peripheral surface of the pinion shaft 3.
0 and an outer ring 11 fixed to the inside of the bearing holding portion 9, a plurality of tapered rollers 12 and 12, respectively, are attached to the cage 13.
It is mounted in the state of being positioned by. A spacer 14 is provided between the end faces of the inner races 10 and 10 of the tapered roller bearings 2 and 2 to position the bearings 2 and 2.

【００１５】自動車の運転に伴って、上記ピニオン軸３
によりリングギヤ５が回転させられた場合、デファレン
シャルケース１の底部に貯溜された潤滑油は、図１に矢
印ｂで示す様に各円錐ころ軸受２、２に、各軸受２、２
の小径側開口端から送り込まれる。両円錐ころ軸受２、
２を構成する内輪１０と外輪１１との間を軸受のポンプ
作用に基づいて通過した潤滑油は、同図に矢印ｃで示す
様に、各軸受２、２の大径側開口端から軸受２、２外に
流出し、デファレンシャルケース１の底部に還流する。As the vehicle is driven, the pinion shaft 3 is
When the ring gear 5 is rotated by, the lubricating oil stored at the bottom of the differential case 1 is applied to the tapered roller bearings 2 and 2 and the bearings 2 and 2 as indicated by an arrow b in FIG.
It is fed from the open end of the small diameter side. Double tapered roller bearing 2,
Lubricating oil that has passed between the inner ring 10 and the outer ring 11 constituting the bearing 2 on the basis of the pumping action of the bearing, as shown by the arrow c in FIG. 2 and flow back to the bottom of the differential case 1.

【００１６】各円錐ころ軸受２、２を構成する内輪１
０、１０の、大径部側端部外周面には、円輪状の邪魔板
１５の内周縁部を固定している。この邪魔板１５の外周
側端縁１５ａは、図３に示す様に、外輪１１の端面１１
ａに近接させ、この端面１１ａとの間に適当な幅の隙間
による油の流路１８を形成している。一方、各円錐ころ
軸受２、２を構成する外輪１１、１１の、小径部側端部
内周縁部には、円輪状の邪魔板１７の外周縁部を固定し
ている。この邪魔板１７の内周側端縁１７ａは、図２に
示す様に、内輪１０の端縁部１０ａに近接させ、上記内
周側端縁１７ａとの間に適当な幅の隙間による油の流路
１６を形成している。Inner ring 1 constituting each tapered roller bearing 2, 2.
The inner peripheral edge of a ring-shaped baffle plate 15 is fixed to the outer peripheral surface of the large-diameter-side end portion of 0 and 10. The outer peripheral edge 15a of the baffle plate 15 is, as shown in FIG.
The oil flow path 18 is formed between the end face 11a and a by a gap of a suitable width. On the other hand, an outer peripheral edge portion of a ring-shaped baffle plate 17 is fixed to the inner peripheral edge portion of the outer ring 11, 11 constituting each tapered roller bearing 2, 2 on the side of the small diameter portion. As shown in FIG. 2, the inner peripheral side edge 17a of the baffle plate 17 is brought close to the end edge portion 10a of the inner ring 10 so that an oil having a proper width is provided between the inner peripheral side edge 17a and the inner peripheral side edge 17a. The flow path 16 is formed.

【００１７】上述の様に構成される本発明のデファレン
シャル用軸受の潤滑装置の潤滑作用自体は、前述した従
来の潤滑装置とほぼ同様である。即ち、デファレンシャ
ルケース１の底部に溜めた潤滑油中に下部を浸けたリン
グギヤ５を、図１に矢印ａで示す様に回転させると、上
記潤滑油はリングギヤ５に跳ね上げられる。そして、同
図に矢印ｂで示す様に、円錐ころ軸受２、２を構成する
内輪１０と外輪１１との間部分に送り込まれ、各円錐こ
ろ軸受２、２を潤滑する。The lubricating action itself of the lubricating device for a differential bearing of the present invention constructed as described above is substantially the same as that of the conventional lubricating device described above. That is, when the ring gear 5 whose lower portion is immersed in the lubricating oil stored in the bottom of the differential case 1 is rotated as shown by the arrow a in FIG. 1, the lubricating oil is splashed up by the ring gear 5. Then, as indicated by an arrow b in the figure, the taper roller bearings 2 and 2 are fed into the portion between the inner ring 10 and the outer ring 11 which form the tapered roller bearings 2 and 2, and lubricate the respective tapered roller bearings 2 and 2.

【００１８】各円錐ころ軸受２、２内に進入した潤滑油
は、内輪１０、１０の回転に伴う遠心力によるポンプ作
用によって、各円錐ころ軸受２、２の小径端から大径端
に向けて流れる。そして、同図に矢印ｃで示す様に、各
円錐ころ軸受２、２から排出されて、デファレンシャル
ケース１の底部に還流する。以下、この作用を連続して
繰り返す事により、各円錐ころ軸受２、２を潤滑する。The lubricating oil that has entered the tapered roller bearings 2 and 2 is directed from the small diameter end to the large diameter end of the tapered roller bearings 2 and 2 by the pumping action of the centrifugal force that accompanies the rotation of the inner rings 10 and 10. Flowing. Then, as indicated by an arrow c in the figure, the tapered roller bearings 2 and 2 are discharged and are returned to the bottom of the differential case 1. Hereinafter, this action is continuously repeated to lubricate the tapered roller bearings 2 and 2.

【００１９】特に、本発明の潤滑装置の場合、内輪１０
と外輪１１との間を流れて円錐ころ軸受２、２を潤滑す
る潤滑油は、必ず邪魔板１５、１７の端縁１５ａ、１７
ａと内輪１０の端縁部１０ａ、或は外輪１１の端面１１
ａとの間の流路１６、１８を通って流れる。この為、高
速走行に伴ってリングギヤ５が高速回転し、図１に矢印
ｂで示す様に、このリングギヤ５から各円錐ころ軸受
２、２に送られる潤滑油の量が増えた場合に於いても、
必要以上の潤滑油が各円錐ころ軸受２、２に送り込まれ
る事が阻止される。この結果、上記各軸受２、２の摩耗
が促進される事が防止されると共に、レース音の増大を
防ぐ。又軸受の予圧が減じてギヤの噛み合い音が増大す
る事もない。Particularly, in the case of the lubricating device of the present invention, the inner ring 10
The lubricating oil that flows between the outer ring 11 and the outer ring 11 to lubricate the tapered roller bearings 2, 2 must be the end edges 15 a, 17 of the baffles 15, 17.
a and the end edge portion 10a of the inner ring 10 or the end surface 11 of the outer ring 11
It flows through the flow paths 16 and 18 to and from a. Therefore, in the case where the ring gear 5 rotates at high speed as the vehicle travels at high speed, and the amount of lubricating oil sent from the ring gear 5 to each of the tapered roller bearings 2 and 2 increases as shown by the arrow b in FIG. Also,
It is prevented that an excessive amount of lubricating oil is sent into each tapered roller bearing 2, 2. As a result, it is possible to prevent the wear of the bearings 2 and 2 from being accelerated and prevent an increase in race noise. Also, the preload of the bearing is not reduced and the gear meshing noise is not increased.

【００２０】又、邪魔板１５、１７により形成される流
路１８、１６は、潤滑油が円錐ころ軸受２、２内を流れ
る事に対する抵抗となって、各軸受２、２の内輪１０と
外輪１１との間に送り込まれた潤滑油が短時間の間に流
失するのを防止する。この為、自動車の低速走行に伴
い、リングギヤ５から各円錐ころ軸受２、２に送り込ま
れる潤滑油の量が減少した場合に於いても、各軸受２、
２が、潤滑油不足により焼き付きを起こす事がなくな
る。The flow passages 18 and 16 formed by the baffles 15 and 17 serve as a resistance against the flow of the lubricating oil in the tapered roller bearings 2 and 2, and thus the inner ring 10 and the outer ring of the bearings 2 and 2, respectively. It prevents that the lubricating oil sent in between 11 and 11 is washed out in a short time. Therefore, even when the amount of lubricating oil fed from the ring gear 5 to the tapered roller bearings 2 and 2 decreases as the vehicle runs at low speed, the bearings 2 and
2 does not cause seizure due to lack of lubricating oil.

【００２１】次に、図４は本発明の第二実施例を示して
いる。本実施例の場合、外輪１１の端面１１ａとの間に
流路１８（図３）を形成する邪魔板１５、１５を、内輪
１０、１０の端面と、ピニオン軸３の一端部に固設した
ピニオンギヤ４、或はピニオン軸３の他端部に固着した
コンパニオンフランジ１９の端面との間で挟持してい
る。又、内輪１０、１０の端縁部１０ａ、１０ａ（図
２）との間に流路１６（図２）を形成する邪魔板１７、
１７は、外輪１１、１１の端面とデファレンシャルケー
ス１内に設けた軸受保持部９、９との間に挟持してい
る。その他の構成及び作用は、前述した第一実施例の場
合と同様である為、同等部分には同一符号を付して、重
複する説明を省略する。Next, FIG. 4 shows a second embodiment of the present invention. In the case of the present embodiment, baffle plates 15 and 15 forming a flow path 18 (FIG. 3) between the outer race 11 and the end face 11a are fixed to the end faces of the inner races 10 and 10 and one end of the pinion shaft 3. It is sandwiched between the pinion gear 4 or the end face of the companion flange 19 fixed to the other end of the pinion shaft 3. Further, a baffle plate 17 that forms a flow path 16 (FIG. 2) between the inner ring 10, 10 and the edge portions 10a, 10a (FIG. 2),
The outer ring 17 is sandwiched between the end faces of the outer rings 11 and the bearing holders 9 provided inside the differential case 1. Other configurations and operations are similar to those in the case of the first embodiment described above, and therefore, equivalent parts will be denoted by the same reference numerals and redundant description will be omitted.

【００２２】尚、以上の説明に於いては、流路１８、１
６を構成する為の邪魔板１５、１７を、潤滑油の流路と
なる内輪１０と外輪１１との間部分の入口側と出口側と
の双方に設けたが、この様な邪魔板は、入口側と出口側
との少なくとも一方に設ければ足りる。又、この様な邪
魔板１５、１７は、必ずしもデファレンシャル内に設け
た総ての円錐ころ軸受に設ける必要はなく、リングギヤ
５の回転に伴う潤滑油の供給状態に応じ、必要な円錐こ
ろ軸受に設ければ良い。In the above description, the flow paths 18 and 1 are
The baffles 15 and 17 for forming 6 are provided on both the inlet side and the outlet side of the portion between the inner ring 10 and the outer ring 11 which are the flow paths of the lubricating oil. It suffices if it is provided on at least one of the entrance side and the exit side. Further, such baffles 15 and 17 do not necessarily have to be provided on all the tapered roller bearings provided in the differential, but the required tapered roller bearings may be provided depending on the supply state of the lubricating oil accompanying the rotation of the ring gear 5. It should be provided.

【００２３】[0023]

【発明の効果】本発明のデファレンシャル用軸受の潤滑
装置は、以上に述べた通り構成され作用する為、次の
の様な効果を得られる。 自動車の高速走行時に、円錐ころ軸受に必要以上の
潤滑油を供給し、この円錐ころ軸受の摩耗を促進する事
で軸受の予圧を減じてギヤの噛み合い音を増大させた
り、或はレース音を増大させたりする不都合も防止でき
る。 逆に、低速走行時に円錐ころ軸受内に存在する潤滑
油の不足によりこの軸受が焼き付きを起こす事を確実に
防止して、デファレンシャルの耐久性を向上させる事が
できる。Since the lubricating device for a differential bearing of the present invention is constructed and operates as described above, the following effects can be obtained. When a car is traveling at high speed, supplying more oil than necessary to the tapered roller bearings and promoting wear of the tapered roller bearings reduces preload on the bearings and increases gear meshing noise, or produces race noise. Inconvenience such as increase can be prevented. On the contrary, it is possible to reliably prevent seizure of the bearing due to the lack of lubricating oil existing in the tapered roller bearing at low speed running, and it is possible to improve the durability of the differential.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明の潤滑装置の第一実施例を示す要部断面
図。FIG. 1 is a sectional view of essential parts showing a first embodiment of a lubricating device of the present invention.

【図２】図１のイ部拡大図。FIG. 2 is an enlarged view of part A in FIG.

【図３】同じくロ部拡大図。[FIG. 3] Similarly, an enlarged view of a portion B.

【図４】本発明の第二実施例を示す、図１に相当する
図。FIG. 4 is a view, corresponding to FIG. 1, showing a second embodiment of the present invention.

【図５】従来のデファレンシャルの要部断面図。FIG. 5 is a sectional view of a main part of a conventional differential.

【符号の説明】[Explanation of symbols]

１ デファレンシャルケース ２ 円錐ころ軸受 ３ ピニオン軸 ４ ピニオンギヤ ５ リングギヤ ９ 軸受保持部 １０ 内輪 １０ａ 端縁部 １１ 外輪 １１ａ 端面 １２ 円錐ころ １３ 保持器 １４ 間座 １５ 邪魔板 １５ａ 外周側端縁 １６ 流路 １７ 邪魔板 １７ａ 内周側端縁 １８ 流路 １９ コンパニオンフランジ 1 Differential Case 2 Tapered Roller Bearing 3 Pinion Shaft 4 Pinion Gear 5 Ring Gear 9 Bearing Holding Part 10 Inner Ring 10a End Edge Part 11 Outer Ring 11a End Face 12 Tapered Roller 13 Cage 14 Spacer 15 Baffle Plate 15a Outer Side Edge 16 Flow Channel 17 Obstacle Plate 17a Inner peripheral side edge 18 Flow path 19 Companion flange

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】 デファレンシャルケース内に回転自在に
設けたリングギヤの下部を、デファレンシャルケースの
底部に溜めた潤滑油中に浸ける事で、この潤滑油をデフ
ァレンシャルケースの上部に迄跳ね上げて、ピニオン軸
をこのデファレンシャルケースに支承する円錐ころ軸受
に送り込み、円錐ころ軸受を通過した潤滑油をデファレ
ンシャルケースの底部に還流させるデファレンシャル用
軸受の潤滑装置に於いて、潤滑油の流路となる円錐ころ
軸受の両端開口部の少なくとも一方に、潤滑油の流通量
を制限する邪魔板を設けた事を特徴とするデファレンシ
ャル用軸受の潤滑装置。1. A pinion shaft is provided by immersing a lower portion of a ring gear rotatably provided in a differential case in lubricating oil stored in a bottom portion of the differential case, so that the lubricating oil is splashed up to an upper portion of the differential case. In a tapered roller bearing that supports this differential case, and the lubricating oil that has passed through the tapered roller bearing is returned to the bottom of the differential case. A lubricating device for a differential bearing, characterized in that at least one of the openings at both ends is provided with a baffle plate for limiting the flow rate of the lubricating oil.
JP6220735A 1994-09-16 1994-09-16 Lubricating device for differential bearings Expired - Fee Related JP2765487B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP6220735A JP2765487B2 (en) 1994-09-16 1994-09-16 Lubricating device for differential bearings

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP6220735A JP2765487B2 (en) 1994-09-16 1994-09-16 Lubricating device for differential bearings

Related Child Applications (1)

Application Number Title Priority Date Filing Date
JP8202787A Division JPH09105450A (en) 1996-07-15 1996-07-15 Lubrication device for bearing of differencial gear

Publications (2)

Publication Number Publication Date
JPH07144548A true JPH07144548A (en) 1995-06-06
JP2765487B2 JP2765487B2 (en) 1998-06-18

Family

ID=16755712

Family Applications (1)

Application Number Title Priority Date Filing Date
JP6220735A Expired - Fee Related JP2765487B2 (en) 1994-09-16 1994-09-16 Lubricating device for differential bearings

Country Status (1)

Country Link
JP (1) JP2765487B2 (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100435589B1 (en) * 2000-12-18 2004-06-09 기아자동차주식회사 A above offset type of dipcarrier having an oil circulation structure
WO2005045269A1 (en) * 2003-11-07 2005-05-19 Jtekt Corporation Oil lubrication-type rolling bearing device
EP1717463A2 (en) * 2005-04-28 2006-11-02 JTEKT Corporation Liquid-lubricated tapered roller bearing and bearing arrangement of a vehicle pinion shaft
JP2008089040A (en) * 2006-09-29 2008-04-17 Jtekt Corp Tapered roller bearing and differential device
CN100451368C (en) * 2003-11-07 2009-01-14 株式会社捷太格特 Oil lubrication-type rolling bearing device
JP2010031901A (en) * 2008-07-25 2010-02-12 Jtekt Corp Tapered roller bearing
JP2010031902A (en) * 2008-07-25 2010-02-12 Jtekt Corp Rolling bearing
US8876397B2 (en) 2005-11-15 2014-11-04 Jtekt Corporation Liquid lubricating tapered roller bearing device
KR20190000152A (en) * 2017-06-22 2019-01-02 주식회사 베어링아트 Double row bearing for pinion shaft and differential device comprising the same

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58153682A (en) * 1982-03-08 1983-09-12 Hitachi Ltd Printer

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58153682A (en) * 1982-03-08 1983-09-12 Hitachi Ltd Printer

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100435589B1 (en) * 2000-12-18 2004-06-09 기아자동차주식회사 A above offset type of dipcarrier having an oil circulation structure
WO2005045269A1 (en) * 2003-11-07 2005-05-19 Jtekt Corporation Oil lubrication-type rolling bearing device
CN100451368C (en) * 2003-11-07 2009-01-14 株式会社捷太格特 Oil lubrication-type rolling bearing device
EP1717463A2 (en) * 2005-04-28 2006-11-02 JTEKT Corporation Liquid-lubricated tapered roller bearing and bearing arrangement of a vehicle pinion shaft
US7645074B2 (en) 2005-04-28 2010-01-12 Jtekt Corporation Fluid-lubricated type tapered roller bearing device and vehicle pinion shaft supporting assembly
EP1717463A3 (en) * 2005-04-28 2010-03-24 JTEKT Corporation Liquid-lubricated tapered roller bearing and bearing arrangement of a vehicle pinion shaft
US8876397B2 (en) 2005-11-15 2014-11-04 Jtekt Corporation Liquid lubricating tapered roller bearing device
JP2008089040A (en) * 2006-09-29 2008-04-17 Jtekt Corp Tapered roller bearing and differential device
JP4715705B2 (en) * 2006-09-29 2011-07-06 株式会社ジェイテクト Tapered roller bearings and differential devices
JP2010031901A (en) * 2008-07-25 2010-02-12 Jtekt Corp Tapered roller bearing
JP2010031902A (en) * 2008-07-25 2010-02-12 Jtekt Corp Rolling bearing
KR20190000152A (en) * 2017-06-22 2019-01-02 주식회사 베어링아트 Double row bearing for pinion shaft and differential device comprising the same

Also Published As

Publication number Publication date
JP2765487B2 (en) 1998-06-18

Similar Documents

Publication Publication Date Title
JP4151472B2 (en) Roller bearing device and lubrication method for roller bearing
JP4285017B2 (en) Differential equipment
JP2002235752A (en) Cage for roller bearing
JPH10299784A (en) Lubricating device for rolling bearing device
US8739931B2 (en) Lubricating structure of differential gear unit
WO2010073867A1 (en) Railroad vehicle drive unit
JPH07144548A (en) Lubricating device for differential gear bearing
CN114877033A (en) Transmission mechanism
JP2007321802A (en) Conical roller bearing
JPH09105450A (en) Lubrication device for bearing of differencial gear
US20200378437A1 (en) Cage for a tapered roller bearing and tapered roller bearing
JPH1151159A (en) Bearing device of pinion shaft for final reduction gear
JP2006234100A (en) Double-row angular ball bearing and pinion shaft supporting device for vehicle
JP2011038575A (en) Rolling stock driving unit
JP2006118525A (en) Lubrication device of rolling bearing
JP4003284B2 (en) Rolling bearing device with oil supply means
JPH11125260A (en) Rolling bearing
JP2010156407A (en) Railway rolling stock drive unit
JP2003042163A (en) Rolling bearing
JP2003032946A (en) Structure of oil lubrication bearing for vehicle motor
JPH08261313A (en) Lubricating structure for bevel gear type differential gear
JPH11230178A (en) Cylindrical roller bearing device
JPH0642099Y2 (en) Tapered roller bearing
JP2002061655A (en) Tapered roller bearing
JP2009041589A (en) Bearing device and differential

Legal Events

Date Code Title Description
LAPS Cancellation because of no payment of annual fees