JP2765487B2 - Lubricating device for differential bearings - Google Patents
Lubricating device for differential bearingsInfo
- Publication number
- JP2765487B2 JP2765487B2 JP6220735A JP22073594A JP2765487B2 JP 2765487 B2 JP2765487 B2 JP 2765487B2 JP 6220735 A JP6220735 A JP 6220735A JP 22073594 A JP22073594 A JP 22073594A JP 2765487 B2 JP2765487 B2 JP 2765487B2
- Authority
- JP
- Japan
- Prior art keywords
- lubricating oil
- tapered roller
- differential
- roller bearings
- bearing
- 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
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)
- Rolling Contact Bearings (AREA)
- Motor Power Transmission Devices (AREA)
- Retarders (AREA)
- General Details Of Gearings (AREA)
Abstract
Description
【発明の詳細な説明】
【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）中に組み込む軸
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により、
軸受部分の耐久性向上を図る。
【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
る事により、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に示す様に構成している。
【０００３】デファレンシャルケース１の一端にはピニ
オン軸３を、１対の円錐ころ軸受２、２により回転自在
に支持している。そして、このピニオン軸３の端部に固
設したピニオンギヤ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とを噛合させる事に
より、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に支承した左右の
駆動軸（図示省略）に伝達自在としている。この様に構
成したデファレンシャルの構成各部は、自動車の走行時
に高速で回転する。従って、ピニオン軸３を支承してい
る上記各円錐ころ軸受２、２を潤滑する必要がある。
【０００４】この為従来から、上記各円錐ころ軸受２、
２の潤滑を連続的に行なう潤滑装置を使用している。こ
の潤滑装置は、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。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により上部デフ
ァレンシャルケース１の上部に迄跳ね上げられる。そし
て、この潤滑油は、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。この様にして各円錐ころ軸
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）る。更に、上記潤
滑油は、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。
【０００５】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ない。
従って、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。
【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。従って、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
との接触の機会を増大させ、円錐ころ軸受２、２の摩耗
を促進し、これら円錐ころ軸受２、２の予圧を減じさせ
てギヤの噛み合い音の増大を招く為、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。
【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。
【０００８】高速走行時に上記各円錐ころ軸受２、２内
を流れる潤滑油の量が過剰になったり、或は低速走行時
にこれら各円錐ころ軸受２、２内の潤滑油が不足する事
を防止する為には、円錐ころ軸受の両端開口部の少なく
とも一方の開口部に、潤滑油の流通量を制限する邪魔板
を設ける事が考えられる。例えば、実願昭５８−１５３
６８２号（実開昭６０−６１５５８号）のマイクロフィ
ルムには、円錐ころ軸受の大径側開口部に、邪魔板とし
て機能するデフレクタを設ける構造が記載されている。
デフレクタを設けたドライブギヤは、上記円錐ころ軸受
を構成する内輪とボス部との間で挟持している。この様
なデフレクタを設けた構造では、円錐ころ軸受から流失
する潤滑油の量を制限して、この円錐ころ軸受内を流通
する潤滑油の量を或る程度規制できる。
【０００９】
【発明が解決しようとする課題】ところが、上記マイク
ロフィルムに記載された構造の場合には、上記デフレク
タの先端部をハウジングの内面に対し、スラスト方向に
対向させている為、上記円錐ころ軸受内を流通する潤滑
油の量を厳密に規制する事が難しい。この理由は、デフ
ァレンシャルに組み込む円錐ころ軸受に予圧を付与する
為である。即ち、円錐ころ軸受に予圧を付与すべく、こ
の円錐ころ軸受を構成する外輪と内輪とを軸方向に亙っ
て互いに近づける方向に押圧すると、これら外輪と内輪
との軸方向に亙る相対位置関係がずれる。この様に外輪
と内輪との位置関係がずれる量を厳密に規制する事は難
しいので、上記デフレクタの先端縁と相手部材の表面と
の間にスラスト方向に亙って存在するラビリンス隙間の
寸法を厳密に規制する事は難しい。この結果、上記ラビ
リンス隙間を通って流れる潤滑油の量を所望値に規制す
る事が難しく、円錐ころ軸受の摩耗防止や焼き付き防止
を確実に図る事が難しくなる。本発明のデファレンシャ
ル用軸受の潤滑装置は、この様な事情に鑑みて発明した
もので、円錐ころ軸受を流通する潤滑油の量を所望値通
り正確に規制すべく、邪魔板により構成されるラビリン
ス隙間の寸法を厳密に規制できる構造を実現するもので
ある。
【００１０】
【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により、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ものである。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
なくとも一方の開口部に、潤滑油の流通量を制限する邪
魔板を設けている。そして、この邪魔板の周縁部とこの
周縁部が対向する他の部材の周面との間に、ラジアル方
向に亙るラビリンス隙間を設けている。
【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、本発明のデファレンシャ
ル用軸受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
まれる事を阻止する。即ち、上記各円錐ころ軸受を流れ
る潤滑油は、上記邪魔板の周縁部とこの周縁部が対向す
る他の部材の周面との間にラジアル方向に亙って設けら
れたラビリンス隙間を通じて流れるので、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なる。こ
の結果、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できる。
【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。即ち、上
記円錐ころ軸受内に存在する潤滑油は、上記ラビリンス
隙間を通じてのみ流れるので、潤滑油の量が少ない場合
でも、この潤滑油が上記円錐ころ軸受内に滞留する時間
が長くなる。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。
【００１３】更に、本発明のデファレンシャル用軸受の
潤滑装置の場合には、上記円錐ころ軸受内を流通する潤
滑油の量を規制する為のラビリンス隙間は、邪魔板の周
縁部とこの周縁部が対向する他の部材の周面との間に、
ラジアル方向に亙って設けられているので、上記ラビリ
ンス隙間の寸法を正確に規制できる。即ち、上記円錐こ
ろ軸受に予圧を付与すべく、この円錐ころ軸受を構成す
る内輪と外輪とを軸方向に亙り互いに近づけ合う方向に
押圧しても、上記ラビリンス隙間の寸法が変化する事は
ない。従って、このラビリンス隙間の寸法を厳密に規制
して、円錐ころ軸受を流通する潤滑油の量を所望値通り
正確に規制し、円錐ころ軸受の摩耗防止や焼き付き防止
を確実に図れる。
【００１４】
【実施例】図１〜３は本発明の第一実施例を示してい
る。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、図１に示す様に、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
合には、このリングギヤ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。
【００１５】一方、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内に挿入している。上記各円錐ころ
軸受２、２は、上記ピニオン軸３の外周面に固定の内輪
１０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１
３により位置決めした状態で設けて成る。又、上記両円
錐ころ軸受２、２の内輪１０、１０の互いに対向する端
面同士の間には間座１４を設け、これら両円錐ころ軸受
２、２に所望の予圧を付与すると共に、これら両円錐こ
ろ軸受２、２の位置決めを図っている。
【００１６】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が回転すると、デファレンシャルケ
ース１の底部に貯溜された潤滑油が、図１に矢印ｂで示
す様に上記各円錐ころ軸受２、２内に、これら各円錐こ
ろ軸受２、２の小径側開口端から送り込まれる。次いで
上記潤滑油は、両円錐ころ軸受２、２を構成する内輪１
０と外輪１１との間を円錐ころ軸受２、２のポンプ作用
に基づいて流れ、これら各円錐ころ軸受２、２内を通過
する。更に、これら各円錐ころ軸受２、２内を通過した
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。
【００１７】上記各円錐ころ軸受２、２を構成する内輪
１０、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１
１ａに近接させ、この端面１１ａとの間に適当な幅の、
スラスト方向に亙るラビリンス隙間による、油の流路１
８を形成している。一方、上記各円錐ころ軸受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１
７ａとの間に適当な幅の、ラジアル方向に亙るラビリン
ス隙間による油の流路１６を形成している。
【００１８】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により、上記デファレンシャル
ケース１の上部に迄跳ね上げられる。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１
０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。
【００１９】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
用により、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。
【００２０】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。
【００２１】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。
【００２２】特に、上記各円錐ころ２、２の小径側開口
端に設けた邪魔板１７の内周側端縁１７ａを内輪１０の
端縁部１０ａの外周面に近接させ、これら内周側端縁１
７ａと内輪１０の端縁部１０ａの外周面との間に適当な
幅の、ラジアル方向に亙るラビリンス隙間である流路１
６を形成しているので、このラビリンス隙間の寸法を正
確に規制できる。即ち、上記各円錐ころ軸受２、２に予
圧を付与すべく、これら各円錐ころ軸受２、２を構成す
る内輪１０、１０と外輪１１、１１とを軸方向に亙り互
いに近づけ合う方向に押圧しても、上記流路１６の寸法
が変化する事はない。従って、この流路１６の寸法を厳
密に規制して、上記各円錐ころ軸受２、２を流通する潤
滑油の量を所望値通り正確に規制し、上記円錐ころ軸受
２、２の摩耗防止や焼き付き防止を確実に図れる。
【００２３】尚、図示の例では、大径側開口端に設けた
邪魔板１５の端縁が外輪１１の端面１１ａに、スラスト
方向に亙るラビリンス隙間である流路１８を介して対向
している。この流路１８の寸法は、上記各円錐ころ軸受
２、２に予圧を付与するのに伴って変化するが、高速走
行時に上記円錐ころ軸受２、２を流通する潤滑油の量
は、上記小径側開口端に設けた邪魔板１７により所望通
り規制できるので、上記流路１８の寸法を或る程度以上
確保すれば、この寸法が多少変化しても、実用上問題を
生じる事はない。
【００２４】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。
【００２５】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
の双方に設けているが、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。
【００２６】
【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を防止でき
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。
円錐ころ軸受を流通する潤滑油の量を規制する為の
流路の寸法を厳密に規制できるので、上記潤滑油の量を
所望値通り正確に規制して、上記の効果を確実に得
られる。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The lubricating device for a differential bearing according to the present invention is incorporated in a differential (differential device or final reduction gear) provided in a drive system of an automobile. Related to bearing lubrication. In particular, the present invention, by maintaining the lubricating oil supply amount by such a lubricating device within an appropriate range,
Improve the durability of the bearing. 2. Description of the Related Art By providing a differential between a propeller shaft of an automobile and a drive shaft (accelerator shaft) of wheels, power is transmitted between the propeller shaft and the drive shaft, and at the same time, The difference between the rotational speeds of the left and right drive wheels due to the change is absorbed, the direction of the power is further changed, and final deceleration is performed. Such a differential is configured, for example, as shown in FIG. A pinion shaft 3 is rotatably supported at one end of a differential case 1 by a pair of tapered roller bearings 2 and 2. The pinion gear 4 fixed to the end of the pinion shaft 3 and the ring gear 5 rotatably supported in the differential case 1 are meshed with each other to transmit the torque of a drive shaft (not shown) to the pinion gear 4. It is free. Further, the rotational force of the pinion gear 4 can be transmitted via a ring gear 5 to left and right drive shafts (not shown) supported on the differential case 1 by another tapered roller bearing. Each component of the differential configured as described above rotates at a high speed when the vehicle is running. Therefore, it is necessary to lubricate each of the tapered roller bearings 2 supporting the pinion shaft 3. For this reason, conventionally, each of the above tapered roller bearings 2,
A lubricating device that continuously performs the lubrication of No. 2 is used. This lubricating device jumps up the lubricating oil stored at the bottom of the differential case 1 to the upper portion of the differential case 1 by a ring gear 5 that rotates when the vehicle is running.
Further, the splashed-up lubricating oil is sent to the tapered roller bearings 2 and 2, and the lubricating oil passing through the tapered roller bearings 2 and 2 is returned to the bottom of the differential case 1. That is, when the ring gear 5 whose lower part is immersed in the lubricating oil stored at the bottom of the differential case 1 is rotated as shown by an arrow a in FIG. 5, the lubricating oil is applied to the upper part of the upper differential case 1 by the ring gear 5. You can jump up to it. Then, the lubricating oil is fed into a portion between the two tapered roller bearings 2, as shown by an arrow “b” in FIG. The lubricating oil that has entered the tapered roller bearings 2, 2 in this way is subjected to centrifugal force to cause the lubricating oil to move from the small-diameter end (left end in the case of the right-hand bearing in FIG. It flows toward the end (also the right end) (pump action when the tapered roller bearing rotates). Further, the lubricating oil is supplied to each of the tapered roller bearings 2, 2 as shown by an arrow c in FIG.
And is returned to the bottom of the differential case 1. Hereinafter, by repeating this action continuously,
Each tapered roller bearing 2, 2 is lubricated. [0005] However, the lubricating device for a differential bearing constructed and operated as described above has the following disadvantages. That is, when the automobile runs at high speed, the pinion shaft 3 connected to the drive shaft rotates at high speed, and the ring gear 5 naturally rotates at high speed. Therefore, it is jumped up by this ring gear 5,
As shown by an arrow b in FIG. 5, the amount of the lubricating oil fed into each of the tapered roller bearings 2, 2 also increases. On the other hand, the pinion shaft 3
Roller bearings 2 and 2
The amount of lubricating oil required for stable operation of the vehicle does not increase much.
Therefore, even if the amount of lubricating oil sent to each tapered roller bearing 2, 2 increases with the high-speed rotation of the ring gear 5, a certain amount or more is wasted in terms of lubrication performance. [0006] The fact that more lubricating oil than necessary is supplied to the tapered roller bearings 2 and 2 does not cause any particular problem. However, foreign substances such as abrasion powder of each component constituting the differential and an abrasive (which cannot be completely removed after finishing the surface of each component) are mixed in the lubricating oil. Therefore, the circulation of the lubricating oil more than necessary is corresponding to the foreign matter and the tapered roller bearings 2 and 2.
This increases the chances of contact with the tapered roller bearings 2, 2 and promotes the wear of the tapered roller bearings 2, 2, and reduces the preload of these tapered roller bearings 2, 2, thereby causing an increase in gear meshing noise.
In addition, the foreign matter damages the raceway surfaces of the tapered roller bearings 2 and 2, and causes an increase in noise (race noise) and vibration generated from the bearings. Conversely, when the automobile runs at a low speed, the amount of lubricating oil fed to each tapered roller bearing 2, 2 decreases with the rotation of the ring gear 5, and the pumping action causes the tapered roller bearings 2, 2 to rotate. When the amount of lubricating oil discharged is larger than the amount of lubricating oil supplied, the tapered roller bearing 2,
Insufficient lubricating oil in 2 causes the bearing to seize. It is possible to prevent the amount of lubricating oil flowing through the tapered roller bearings 2 and 2 from becoming excessive during high-speed running, or from running out of lubricating oil in the tapered roller bearings 2 and 2 during low-speed running. In order to do so, it is conceivable to provide a baffle plate for restricting the flow rate of the lubricating oil in at least one of the two end openings of the tapered roller bearing. For example, Japanese Utility Model Application No. 58-153
No. 682 (Japanese Utility Model Application Laid-Open No. 61558/1985) describes a structure in which a deflector functioning as a baffle plate is provided at a large-diameter side opening of a tapered roller bearing.
The drive gear provided with the deflector is sandwiched between the inner ring and the boss constituting the tapered roller bearing. In the structure provided with such a deflector, the amount of lubricating oil flowing out of the tapered roller bearing can be limited, and the amount of lubricating oil flowing through the tapered roller bearing can be regulated to some extent. [0009] However, in the case of the structure described in the microfilm, the tip of the deflector is opposed to the inner surface of the housing in the thrust direction, so that the conical shape is formed. It is difficult to strictly control the amount of lubricating oil flowing in the roller bearing. The reason for this is to apply a preload to the tapered roller bearing incorporated in the differential. That is, when the outer ring and the inner ring constituting the tapered roller bearing are pressed in a direction approaching each other in the axial direction in order to apply a preload to the tapered roller bearing, the relative positional relationship between the outer ring and the inner ring in the axial direction is increased. Shifts. Since it is difficult to strictly control the amount of deviation of the positional relationship between the outer ring and the inner ring in this manner, the size of the labyrinth gap existing in the thrust direction between the leading edge of the deflector and the surface of the mating member is determined. It is difficult to regulate strictly. As a result, it is difficult to regulate the amount of lubricating oil flowing through the labyrinth gap to a desired value, and it is difficult to reliably prevent wear and seizure of the tapered roller bearing. The lubricating device for a differential bearing of the present invention has been devised in view of such circumstances, and has a labyrinth constituted by a baffle plate to accurately regulate the amount of lubricating oil flowing through the tapered roller bearing as desired. This realizes a structure capable of strictly regulating the size of the gap. The lubricating device for a differential bearing according to the present invention is, like the conventional lubricating device described above, provided with a lower portion of a ring gear rotatably provided in a differential case. By immersing the lubricating oil in the lubricating oil stored at the bottom of the case, the lubricating oil jumps up to the top of the differential case, sends the pinion shaft to the tapered roller bearing that supports the differential case, and lubrication passes through the tapered roller bearing. The oil is returned to the bottom of the differential case. Especially,
In the lubricating device for a differential bearing according to the present invention, at least one of the two end openings of the tapered roller bearing serving as a lubricating oil flow passage is provided with a baffle plate for restricting the flow of lubricating oil. . A labyrinth gap extending in the radial direction is provided between the peripheral portion of the baffle plate and the peripheral surface of another member facing the peripheral portion. The lubricating action of the lubricating device for a differential bearing of the present invention constructed as described above is the same as that of the aforementioned conventional lubricating device. In particular, in the case of the lubricating device for differential bearings of the present invention, even when the ring gear rotates at high speed with high speed running and the amount of lubricating oil sent from the ring gear to each tapered roller bearing increases, The baffle plate prevents excessive lubricating oil from being fed into each tapered roller bearing. That is, the lubricating oil flowing through each of the tapered roller bearings flows through a labyrinth gap provided in the radial direction between the peripheral portion of the baffle plate and the peripheral surface of another member facing the peripheral portion. Therefore, it is possible to prevent the lubricating oil from being supplied to each tapered roller bearing more than necessary. As a result, it is possible to prevent the wear of the bearings from being promoted, and to prevent an increase in race noise due to foreign matter. Further, the baffle plate serves as a resistance to the lubricating oil flowing in the tapered roller bearing, and prevents the lubricating oil sent into the bearing from flowing away in a short time. That is, since the lubricating oil existing in the tapered roller bearing flows only through the labyrinth gap, even when the amount of the lubricating oil is small, the lubricating oil stays in the tapered roller bearing for a longer time. For this reason, even when the amount of lubricating oil sent from the ring gear to each tapered roller bearing decreases as the vehicle travels at a low speed, the bearings do not seize due to insufficient lubricating oil. Further, in the lubricating device for a differential bearing according to the present invention, the labyrinth gap for regulating the amount of lubricating oil flowing in the tapered roller bearing is formed by the peripheral edge of the baffle plate and the peripheral edge. Between the peripheral surface of the other member facing
Since they are provided in the radial direction, the dimensions of the labyrinth gap can be accurately regulated. That is, even if the inner ring and the outer ring constituting the tapered roller bearing are pressed in a direction approaching each other in the axial direction in order to apply a preload to the tapered roller bearing, the dimension of the labyrinth gap does not change. . Therefore, the size of the labyrinth gap is strictly regulated, the amount of lubricating oil flowing through the tapered roller bearing is accurately regulated as desired, and wear and seizure of the tapered roller bearing can be reliably prevented. 1 to 3 show a first embodiment of the present invention. The lower part of the ring gear 5 rotatably provided in the differential case 1 is immersed in lubricating oil stored at the bottom of the differential case 1 as shown in FIG. Therefore, when the ring gear 5 rotates with the operation of the automobile, the lubricating oil attached to the ring gear 5 jumps up to the upper part of the differential case 1. On the other hand, a pair of tapered roller bearings 2 and 2 are provided at intervals in a bearing holding portion 9 provided inside the differential case 1. The pinion shaft 3 is rotatably supported by these double tapered roller bearings 2 and 2. The pinion shaft 3 penetrates one end of the differential case 1 in an oil-tight manner through a seal body, and is inserted into the differential case 1. Each of the tapered roller bearings 2, 2 has a plurality of tapered rollers 12, 12 between an inner ring 10 fixed to the outer peripheral surface of the pinion shaft 3 and an outer ring 11 fixed inside the bearing holding portion 9. , Cage 1
3 is provided in a state where it is positioned. Further, a spacer 14 is provided between the end faces of the inner rings 10 and 10 of the double tapered roller bearings 2 and 2 facing each other to apply a desired preload to the double tapered roller bearings 2 and 2. The positioning of the tapered roller bearings 2 and 2 is achieved. As the vehicle is driven, the pinion shaft 3
When the ring gear 5 rotates, the lubricating oil stored at the bottom of the differential case 1 is introduced into the tapered roller bearings 2 and 2 as shown by an arrow b in FIG. It is fed in from the side opening end. Next, the lubricating oil is supplied to the inner ring 1 forming the double tapered roller bearings 2, 2.
It flows between 0 and the outer ring 11 based on the pumping action of the tapered roller bearings 2, 2, and passes through these tapered roller bearings 2, 2. Further, the lubricating oil that has passed through each of these tapered roller bearings 2 and 2 flows out of the bearings 2 and 2 from the large-diameter opening end of each of the bearings 2 and 2 as shown by an arrow c in FIG. Reflux to the bottom of case 1. An inner peripheral edge of a ring-shaped baffle plate 15 is fixed to the outer peripheral surface of the large-diameter portion-side end of the inner rings 10 and 10 constituting the tapered roller bearings 2 and 2. The outer peripheral edge 15a of the baffle plate 15 is, as shown in FIG.
1a, and an appropriate width between the end face 11a and
Oil flow path 1 due to labyrinth clearance in the thrust direction
8 are formed. On the other hand, the outer peripheral edge of a ring-shaped baffle plate 17 is fixed to the inner peripheral edge of the outer ring 11, 11 constituting each of the tapered roller bearings 2, 2 at the small diameter side end. The inner peripheral edge 17a of the baffle plate 17 is, as shown in FIG.
The inner peripheral edge 1 is brought close to the edge 10 a of the inner race 10.
An oil passage 16 having an appropriate width and a labyrinth gap extending in the radial direction is formed between the oil passage 16 and the oil passage 7a. The lubricating action of the lubricating device for a differential bearing of the present invention configured as described above is substantially the same as that of the above-described conventional lubricating device. That is, when the ring gear 5 whose lower part is immersed in the lubricating oil stored at the bottom of the differential case 1 is rotated as shown by the arrow a in FIG. 1, the lubricating oil is moved to the upper part of the differential case 1 by the ring gear 5. You can jump up to it. As shown by an arrow b in FIG.
It is fed into a portion between the outer ring 11 and the outer ring 11 to lubricate each tapered roller bearing 2. The lubricating oil that has entered the tapered roller bearings 2, 2 is directed from the small-diameter end to the large-diameter end of each tapered roller bearing 2, 2 by a pumping action due to centrifugal force accompanying rotation of the inner rings 10, 10. Flows. Then, as shown by an arrow c in the figure, the fluid is discharged from each tapered roller bearing 2, 2 and returns to the bottom of the differential case 1. Hereinafter, by repeating this operation continuously, each tapered roller bearing 2, 2 is lubricated. In particular, in the case of the lubrication device of the present invention, the inner race 10
The lubricating oil which flows between the outer ring 11 and lubricates the tapered roller bearings 2, 2 always has the edges 15 a, 17 of the baffle plates 15, 17.
a and the edge 10a of the inner race 10 or the end face 11 of the outer race 11
a. For this reason, when the ring gear 5 rotates at a high speed as the vehicle travels at a high speed, and the amount of the lubricating oil sent from the ring gear 5 to each of the tapered roller bearings 2 increases as shown by an arrow b in FIG. Also,
Unnecessary lubricating oil is prevented from being fed into the tapered roller bearings 2,2. As a result, the wear of the bearings 2 and 2 is prevented from being promoted, and the race noise is prevented from increasing. Also, there is no increase in the gear meshing noise due to the reduced preload of the bearing. The flow paths 18 and 16 formed by the baffle plates 15 and 17 provide resistance to the flow of the lubricating oil through the tapered roller bearings 2 and 2, and the inner ring 10 and the outer ring of each bearing 2 and 2. 11 to prevent the lubricating oil fed between them from flowing away in a short time. For this reason, even when the amount of lubricating oil sent from the ring gear 5 to each of the tapered roller bearings 2 and 2 decreases as the vehicle travels at a low speed, each of the bearings 2 and
2 does not cause seizure due to lack of lubricating oil. In particular, the inner peripheral edge 17a of the baffle plate 17 provided at the small-diameter opening end of each of the tapered rollers 2, 2 is brought close to the outer peripheral surface of the edge 10a of the inner race 10, and these inner peripheral end Edge 1
A flow path 1 which is a labyrinth gap extending in the radial direction and having an appropriate width between the inner ring 10 and the outer peripheral surface of the edge 10a of the inner ring 10.
6, the dimensions of the labyrinth gap can be accurately regulated. That is, in order to apply a preload to each of the tapered roller bearings 2, 2, the inner rings 10, 10 and the outer rings 11, 11, which constitute the respective tapered roller bearings 2, 2, are pressed in a direction approaching each other in the axial direction. However, the dimension of the flow path 16 does not change. Therefore, the size of the flow path 16 is strictly controlled, and the amount of lubricating oil flowing through each of the tapered roller bearings 2, 2 is accurately controlled as desired. Prevention of image sticking can be ensured. In the illustrated example, the edge of the baffle plate 15 provided at the large-diameter side opening end faces the end surface 11a of the outer race 11 via a flow path 18 which is a labyrinth gap extending in the thrust direction. . The size of the flow path 18 changes as a preload is applied to each of the tapered roller bearings 2, 2, but the amount of lubricating oil flowing through the tapered roller bearings 2, 2 during high-speed running is reduced by the small diameter. Since it can be regulated as desired by the baffle plate 17 provided at the side opening end, if the dimensions of the flow path 18 are secured to a certain degree or more, even if this dimension slightly changes, there is no practical problem. FIG. 4 shows a second embodiment of the present invention. In the case of the present embodiment, baffle plates 15, 15 forming a flow path 18 (FIG. 3) between the end surface 11 a of the outer ring 11 and the end surfaces of the inner rings 10, 10 and one end of the pinion shaft 3 are fixed. It is held between the pinion gear 4 and an end face of a companion flange 19 fixed to the other end of the pinion shaft 3. In addition, a baffle plate 17 that forms a flow path 16 (FIG. 2) between the inner ring 10 and the edge portions 10a, 10a (FIG. 2) of the inner rings 10, 10.
17 is sandwiched between the end faces of the outer races 11 and the bearing holding portions 9 provided in the differential case 1. Other configurations and operations are the same as those of the first embodiment described above, and therefore, the same parts are denoted by the same reference numerals, and redundant description will be omitted. In the above description, the flow paths 18, 1
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 to provide at least one of the inlet side and the outlet side. Further, such baffle plates 15 and 17 do not necessarily need to be provided on all tapered roller bearings provided in the differential, and may be provided on required tapered roller bearings according to the supply state of lubricating oil accompanying rotation of the ring gear 5. It may be provided. The lubricating device for a differential bearing according to the present invention is constructed and operates as described above, so that the following effects can be obtained. During high-speed running of the car, lubricating oil is supplied to the tapered roller bearings more than necessary, and by promoting the wear of the tapered roller bearings, the preload of the bearings is reduced to increase the gear meshing noise or reduce the race noise. The inconvenience of increase can be prevented. Conversely, seizure of the bearing due to lack of lubricating oil existing in the tapered roller bearing during low-speed running can be reliably prevented, and the durability of the differential can be improved. Since the dimensions of the flow path for regulating the amount of lubricating oil flowing through the tapered roller bearing can be strictly regulated, the amount of the lubricating oil can be regulated exactly as desired and the above-mentioned effects can be obtained reliably.
【図面の簡単な説明】
【図１】本発明の潤滑装置の第一実施例を示す要部断面
図。
【図２】図１のイ部拡大図。
【図３】同じくロ部拡大図。
【図４】本発明の第二実施例を示す、図１に相当する
図。
【図５】従来のデファレンシャルの要部断面図。
【符号の説明】
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BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view showing a main part of a first embodiment of a lubricating device according to the present invention. FIG. 2 is an enlarged view of a part A of FIG. FIG. 3 is an enlarged view of the same part. FIG. 4 is a view showing a second embodiment of the present invention and corresponding to FIG. 1; FIG. 5 is a sectional view of a main part of a conventional differential. [Description of Signs] 1 Differential case 2 Tapered roller bearing 3 Pinion shaft 4 Pinion gear 5 Ring gear 9 Bearing holding portion 10 Inner ring 10a Edge 11 Outer ring 11a End face 12 Tapered roller 13 Cage 14 Spacer 15 Baffle plate 15a Outer edge 16 flow path 17 baffle plate 17a inner peripheral edge 18 flow path 19 companion flange
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.6，ＤＢ名) B60K 17/16 F16H 57/04 F16C 33/66──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int. Cl. 6 , DB name) B60K 17/16 F16H 57/04 F16C 33/66
Claims (1)
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により、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の開口部に、潤滑油の流通
量を制限する邪魔板を設け、この邪魔板の周縁部とこの
周縁部が対向する他の部材の周面との間に、ラジアル方
向に亙るラビリンス隙間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。(57) [Claims] The lower portion of the ring gear which is provided rotatably within the differential case, by immersing in the lubricating oil accumulated in the bottom portion of the differential case, flipped up until the lubricating oil to the top of the differential case, the pinion shaft to the differential case In a lubricating device for differential bearings, in which lubricating oil is fed to the bearing and conveyed to the bottom of the differential case, the lubricating oil flows through the conical roller bearing. A baffle plate for restricting the amount of lubricating oil is provided in one of the openings , and a peripheral portion of the baffle plate is
Radial direction between the peripheral surface of the other member whose peripheral edge faces
A lubricating device for differential bearings, characterized by having a labyrinth gap extending in the direction .
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 JPH07144548A (en) | 1995-06-06 |
| JP2765487B2 true 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) |
Families Citing this family (9)
| 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 |
| CN100451368C (en) * | 2003-11-07 | 2009-01-14 | 株式会社捷太格特 | Oil lubrication-type rolling bearing device |
| EP1693584A4 (en) * | 2003-11-07 | 2008-05-07 | Jtekt Corp | Oil lubrication-type rolling bearing device |
| JP4449815B2 (en) | 2005-04-28 | 2010-04-14 | 株式会社ジェイテクト | Liquid lubricated tapered roller bearing device and vehicle pinion shaft support device |
| JP4635838B2 (en) | 2005-11-15 | 2011-02-23 | 株式会社ジェイテクト | Liquid lubricated tapered roller bearing 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 |
| JP5234263B2 (en) * | 2008-07-25 | 2013-07-10 | 株式会社ジェイテクト | Tapered roller bearings |
| JP5126678B2 (en) * | 2008-07-25 | 2013-01-23 | 株式会社ジェイテクト | Rolling bearing |
| KR101982224B1 (en) * | 2017-06-22 | 2019-05-24 | 주식회사 베어링아트 | Differential device comprising the double row bearing for pinion shaft |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58153682A (en) * | 1982-03-08 | 1983-09-12 | Hitachi Ltd | Printer |
-
1994
- 1994-09-16 JP JP6220735A patent/JP2765487B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH07144548A (en) | 1995-06-06 |
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|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |