JP4411831B2

JP4411831B2 - Assembly for double row ball bearing and assembly method of apparatus using the assembly

Info

Publication number: JP4411831B2
Application number: JP2002286372A
Authority: JP
Inventors: 英雄上田; 敏弘川口
Original assignee: JTEKT Corp
Current assignee: JTEKT Corp
Priority date: 2002-09-30
Filing date: 2002-09-30
Publication date: 2010-02-10
Anticipated expiration: 2022-09-30
Also published as: JP2004124996A

Description

【０００１】
【発明の属する技術分野】
本発明は、例えば車両に搭載されるディファレンシャル装置等に用いられる複列玉軸受を構成する組品および複列玉軸受用組品を用いる装置の組立方法に関する。
【０００２】
【従来の技術】
従来のディファレンシャル装置には、ピニオン軸の両側（ヘッド側とテール側）を円錐ころ軸受で回転自在に支持したものがある（例えば、特許文献１参照）。
【０００３】
以下図１１に基づいて、従来のディファレンシャル装置６０の構成を説明する。図１１は、ディファレンシャル装置の断面構造を示している。このディファレンシャル装置６０は、そのディファレンシャルケース６１内に、ピニオン軸（ドライブピニオン）６３を有する。このピニオン軸６３は、軸心方向に離間して配置される一対単列の円錐ころ軸受６５，６６によって、軸心回りに回転自在に支持されている。ピニオン軸６３の端部に、不図示のプロペラシャフトに連結されるコンパニオンフランジ６４が設けられている。
【０００４】
このようなディファレンシャル装置６０を組立てる際は、概略次のようにして行う。
（１）ディファレンシャルケース６１内に形成されている環状壁６７，６８に、両側の円錐ころ軸受６５，６６の外輪部材６９，７０を圧入する。
（２）ピニオン軸６３のピニオンギヤ６２側に、円錐ころ軸受６５の内輪部材７１およびころ７３の組品における、内輪部材７１を圧入する。
（３）ピニオン軸６３をディファレンシャルケース６１の一側から挿入し、一側の円錐ころ軸受６５の外輪部材６９の軌道面に、組品のころ７３を嵌め込む。
（４）他側の円錐ころ軸受６６の外輪部材７０に、他側の内輪部材７２および７４の組品におけるころ７４が、外輪部材７０の外輪軌道面に嵌合するよう、内輪部材７２をピニオン軸６３に圧入する。
（５）ピニオン軸６３の外端部にナット７５を螺合し、ピニオンギヤ６２とコンパニオンフランジ６４の間で両側の円錐ころ軸受６５，６６の各ころ７３，７４に対して所定の予圧を付与する。
【０００５】
上記ディファレンシャル装置６０では、ピニオン軸６３を回転自在に支持する軸受が円錐ころ軸受６５，６６からなっている。特に、スラスト荷重の大きなピニオンギヤ６２側の円錐ころ軸受６５には大きな摩擦抵抗が働く。このため回転トルクが大きくなり、ディファレンシャル装置６０の効率が低下するといった課題がある。そこで、ピニオンギヤ６２側の軸受を、円錐ころ軸受６５に代えてタンデム型の複列玉軸受（例えば複列アンギュラ玉軸受）を用いることが考えられる。
【０００６】
【特許文献１】
特開平１１−４８８０５号（第３頁，第１図）
【０００７】
【発明が解決しようとする課題】
ところで、例えば一側（ピニオンギヤ６２側）の円錐ころ軸受６５を複列玉軸受に代えて用いる場合であっても、円錐ころ軸受６５を用いた組立ての場合と同様の工程でもってディファレンシャル装置６０を組立てられるよう、上記（１）〜（５）で述べた工程は変更しないことが望ましい。このため、外輪部材に組込まれる、複数の玉を有する組品が必要となる。
【０００８】
【課題を解決するための手段】
本発明の複列玉軸受用組品は、大径内輪軌道面と、前記大径内輪軌道面に対して軸方向に離隔した位置に形成された小径内輪軌道面を含む内輪部材と、大径保持器と、前記大径保持器に円周方向等配位置に保持されるとともに、該大径保持器に形成された抜止め部によって径方向外側に抜出るのを防止された状態で前記大径内輪軌道面に嵌合される大径軌道側の玉と、小径保持器と、前記小径保持器に円周方向等配位置に保持されるとともに、該小径保持器に形成された抜止め部によって径方向外側に抜出るのを防止された状態で、前記大径側の玉を前記大径内輪軌道面に嵌合した後に前記小径内輪軌道面に嵌合される小径軌道側の玉とを含み、前記内輪部材に、前記小径保持器に保持された玉が前記小径内輪軌道面から軸方向に抜出るのを防止するための、前記小径内輪軌道面よりも大径の肩部が形成され、前記大径保持器および小径保持器は、各玉を装着して保持するための複数のポケットが環体の円周数ヶ所に形成されるものであって、各ポケットのピッチ円径を軸方向に延長して得られる仮想円筒面よりも外径側に形成された大輪部と、前記仮想円筒面よりも内径側に形成された小輪部と、前記大輪部と前記小輪部との円周数ヶ所を連接する複数の架橋部とから形成され、前記ポケットは、前記大輪部と周方向で隣り合う２つの前記架橋部で形成される略半円状の第１凹部と、前記小輪部と周方向で隣り合う２つの前記架橋部で形成される略半円状の第２凹部とを組み合わせて構成され、前記第１凹部の外径側の開口縁の間隔Ｗ３は第２凹部の内径側の開口縁の間隔Ｗ４より小に設定されているとともに、前記各架橋部の外周面は、前記大輪部につながるとともに軸方向に沿う平面と、前記小輪部につながるとともに該小輪部側ほど縮径する斜面とでなり、この平面と斜面とが架橋部の軸方向中央で連続して形成されており、その接合部を、前記大輪部における前記第１凹部の内面の径方向外端箇所と前記小輪部における前記第２凹部の内面の径方向外端箇所とを直線で結ぶ仮想円錐面よりも外径側に配置させ、前記各架橋部の内周面は、前記小輪部につながるとともに軸方向に沿う平面と、前記大輪部につながるとともに該大輪部側ほど拡径する斜面とでなり、この平面と斜面とが架橋部の軸方向中央で連続して形成されており、その接合部を、前記大輪部における前記第１凹部の内面の径方向内端箇所と前記小輪部における前記第２凹部の内面の径方向内端箇所とを直線で結ぶ仮想円錐面よりも内径側に配置させている。
【０００９】
上記構成において、大径保持器に玉を組付けた状態で玉を内輪部材の大径内輪軌道面に嵌合させ、小径保持器に玉を組付けた状態で玉を内輪軌道面の小径内輪軌道面に嵌合させることで、複列玉軸受用組品とする。
【００１０】
このような複列玉軸受用組品を用いて複列玉軸受を組立てる場合は、例えばハウジングの内面に予め外輪部材を組付けておき、軸を複列玉軸受用組品の内輪部材に挿通しておき、この軸をハウジングに挿通するようにして、複列玉軸受用組品における小径保持器に保持された玉を外輪部材の小径外輪軌道面に嵌合するよう、また複列玉軸受における大径保持器に保持された玉を外輪部材の大径外輪軌道面に嵌合するよう組付ける。
【００１１】
この際、複列玉軸受用組品における両列の玉は、径方向外側および軸方向に抜出るのを防止されていることにより、一体ものとして容易に取扱うことが可能となり、円錐ころ軸受を用いていた場合と同様にして複列玉軸受用組品を外輪部材に組付けることが可能となる。
【００１２】
また本発明の複列玉軸受用組品は、前記内輪部材に、前記大径保持器に保持された大径軌道側の玉が前記大径内輪軌道面から軸方向に抜出るのを防止するための、前記大径内輪軌道面よりも大径の抜止め部が、前記大径内輪軌道面と小径内輪軌道面との間の連続面に形成されている。
【００１３】
この構成によれば、大径保持器に玉を組付けた状態で玉を内輪部材の大径内輪軌道面に嵌合させることで、玉が径方向外側および軸方向に抜出るのを防止された状態となるので、これらの玉を特別な手段を用いて保持させることなく、小径保持器に玉を組付けた状態の組品における玉を、手順よく内輪軌道面の小径内輪軌道面に嵌合させ、組付けることができる。
【００１４】
さらに、前記複列玉軸受用組品は、前記大径内輪軌道面と小径内輪軌道面との間の連続面に、前記大径保持器に玉を保持した状態で前記内輪部材に軸方向から組込む際に、前記玉を案内するための斜面が形成されている。
【００１５】
この構成によれば、大径保持器に保持した玉は、斜面に案内されることで大径内輪軌道面に向けて円滑に案内されて、これに嵌合させることができる。
【００１６】
なお、複列玉軸受に対する荷重の働き方に応じては、複列玉軸受用組品における両列の玉が、外輪部材の大径外輪軌道面、小径外輪軌道面にそれぞれ嵌合した状態で前記両列の玉における接触角を同一に設定するばかりでなく、それぞれの接触角を異なった角度に設定するのが望ましい。
また、本発明に係る複列玉軸受用組品を用いる装置の組立方法は、前記大径保持器および前記小径保持器のそれぞれについて各保持器のポケットに内径側から玉を無理嵌めして得られた大径側組品および小径側組品を、それぞれ、前記内輪部材の大径内輪軌道面、小径内輪軌道面に嵌合するように組み付け、その後、この組み付けたものを、前記外輪部材の大径外輪軌道面に大径側組品が嵌合し、小径外輪軌道面に小径側組品が嵌合するように、小径側から組み込む。
【００１７】
【発明の実施の形態】
以下、本発明の実施形態を、図面に基づいて説明する。図は、本発明の実施形態における複列転がり軸受用組品を、車両に付設されるディファレンシャル装置のピニオン軸支持用軸受に適用させている。
【００１８】
図１の全体断面図に示すように、ディファレンシャル装置１は、ディファレンシャルケース２を有している。このディファレンシャルケース２は、フロントケース３とリヤケース４とからなり、両ケース３，４は、ボルト・ナット２ａにより一体に取付けられている。
【００１９】
ディファレンシャルケース２は、左右の車輪を差動連動する差動変速機構５、および軸方向一方側（以下単に一側という）にピニオンギヤ６を有するピニオン軸（ドライブピニオン）７を内装している。ピニオンギヤ６は、差動変速機構５のリングギヤ８に噛合されている。ピニオン軸７の軸部９は、軸方向他方側（以下単に他側という）ほど一側に比べて小径となるよう外周面が段状に形成されている。
【００２０】
ピニオン軸７の軸部９は、その一側を、複列玉軸受１０を介してディファレンシャルケース２に軸心回りに回転自在に支持されている。ピニオン軸７の軸部９はその他側を、複列玉軸受２５を介してディファレンシャルケース２に軸心回りに回転自在に支持されている。
【００２１】
前記フロントケース３の内方に、軸受装着用の環状壁２７，２８が形成され、前記複列玉軸受１０の外輪部材１１および複列玉軸受２５の外輪部材１２が、それぞれ環状壁２７，２８の内周面に嵌着されている。
【００２２】
両複列玉軸受１０，２５は、ピニオン軸７の軸方向において対称の構成であり、複列玉軸受２５の径は、複列玉軸受１０の径に比べて、ピニオン軸７の小径部分に嵌合する分だけ小径となっている。
【００２３】
すなわち複列玉軸受２５は、内輪部材１４、外輪部材１２、ピッチ円直径の異なる２列の玉２６，２９およびその保持器４４，４５を有している。また内輪部材１４は、ピニオン軸７の軸方向途中に嵌合している。
【００２４】
前述のように、両複列玉軸受１０，２５は軸方向において対称形状で径が異なるだけであるため、以下に一側の複列玉軸受１０について、その詳細な構成を代用して説明する。
【００２５】
複列玉軸受１０は、単一の外輪部材１１と、図２に示す複列転がり軸受用組品としての内輪側組品２１とから構成される。図３に示すように、外輪部材１１は、その内周面が段状に形成されている。すなわち、外輪部材１１の内周面には、一側の大径外輪軌道面１１ａと、この大径外輪軌道面１１ａに他側に離隔した部位に形成された小径外輪軌道面１１ｂと、両軌道面１１ａ，１１ｂの間に形成された外輪環状面１１ｃとを有し、この外輪環状面１１ｃの途中には、他側に向けて拡径する傾斜段付面１１ｄが形成されている。さらに、外輪部材１１の内周面一側には、他側に向けて拡径する傾斜案内面１１ｅが形成されている。
【００２６】
図２に示すように、内輪側組品２１は、外輪部材１１の径方向内方に配置される単一の内輪部材１３と、外輪部材１１と内輪部材１３との間に介装されて、ピッチ円直径Ｄ１，Ｄ２がそれぞれ異なる一方列の玉群１５および他方列の玉群１６と、これら玉群１５，１６を構成する玉１７，１８を、円周方向等配位置にそれぞれ保持する大径保持器１９および小径保持器２０とを有する。
【００２７】
同図に示すように、内輪部材１３は、その外周面が段状に形成されている。すなわち、内輪部材１３の外周面に、一側の大径内輪軌道面１７ａと、この大径内輪軌道面１７ａに対して他側に離隔して形成された小径内輪軌道面１８ａと、大径内輪軌道面１７ａと小径内輪軌道面１８ａとの間に形成された内輪環状面とが形成されている。
【００２８】
この内輪環状面は、大径内輪軌道面１７ａ側に形成されて軸方向に沿うとともに、軸方向に所定の長さＬを有する保持部として筒状面部１３ａと、この筒状面部１３ａと小径内輪軌道面１８ａとを連続する傾斜案内面部１３ｂとを有する。筒状面部１３ａの径は、大径内輪軌道面１７ａの底の径よりもわずかに大きく形成されている。
【００２９】
内輪部材１３の軸方向両側に形成された肩部２２，２３のうち、他側の肩部２３の径は、小径内輪軌道面１８ａの底の径よりもわずかに大径に形成されている。両肩部２２，２３は、角Ｒとなる面取りが施されている。なお、大径軌道側の玉１７の径と小径軌道側の玉１８の径とは実質的に同一である。
【００３０】
さらに、図４の断面図に示すように、本発明の実施形態における複列玉軸受１０では、一方列の玉群１５における玉１７と、他方列の玉群１６における玉１８を、上記組品２１を外輪部材１１に対して組付けた際、荷重の働きに応じて接触角θ１，θ２を必要な角度だけ異ならせるよう構成されている。
【００３１】
このように、外輪部材１１が大径外輪軌道面１１ａと小径内輪軌道面１１ｂとを有し、内輪部材１３が大径内輪軌道面１７ａと小径内輪軌道面１８ａとを有し、一方列の玉群１５および他方列の玉群１６におけるピッチ円直径Ｄ１，Ｄ２が異なる構成の複列玉軸受１０は、タンデム型の転がり軸受と称される。
【００３２】
ここで、図５乃至図１０に基づいて、複列玉軸受１０における大径保持器１９および小径保持器２０の構成を説明する。大径保持器１９と小径保持器２０とは、径が異なり、小径保持器２０のポケット８６が大径保持器１９のポケット８９の数よりも少ないだけであるので、ここでは、大径保持器１９の構成の説明をもって、小径保持器２０の構成の説明も代用することとする。
【００３３】
大径保持器１９には、図５および図６の斜視図に示すように、環体の円周数ヶ所に玉１７を装着するための複数個のポケット８６が形成されている。これらポケット８６は、荷重作用線Ｘ（図４参照）に沿う方向に環体を貫通するように形成されている。
【００３４】
そして図７に示すように、各ポケット８６のピッチ円径（ポケット８６どうしの中心を結ぶ円の直径）を軸方向に延長して得られる仮想円筒面Ｙよりも外径側に形成された大輪部８７と、仮想円筒面Ｙよりも内径側に形成された小輪部８８と、図８に示すように、大輪部８７と小輪部８８との円周数ヶ所を連接する複数の架橋部（柱）８９とから形成されている。
【００３５】
ポケット８６は、大輪部８７と周方向で隣合う２つの架橋部８９で形成される略半円状の第１凹部９０と、小輪部８８と周方向で隣合う各２つの架橋部８９で作られる略半円状の第２凹部９１とを組み合わせて構成される。
【００３６】
周方向で隣合う各２つの架橋部８９，８９において、第１凹部９０の内面および第２凹部９１の内面は、玉１７の曲率と同一の曲率に設定された球状の凹面に形成されている。
【００３７】
架橋部８９の外周面において、軸方向に沿う平面８９ａと斜面８９ｂとは軸方向中央で連続して形成されており、その接合部８９ｃを、大輪部８７と小輪部８８とを直線で結ぶ仮想円錐面Ｚ１よりも外径側に配置させている。
【００３８】
架橋部８９の内周面において、軸方向に沿う平面８９ｄと斜面８９ｅとが軸方向中央で連続して形成されており、その接合部８９ｆを、大輪部８７と小輪部８８とを直線で結ぶ仮想円錐面Ｚ２よりも内径側に配置させている。
【００３９】
図９および図１０に示すように、第１凹部９０の外径側の開口縁Ｃ１，Ｃ２の間隔Ｗ３、および第２凹部９１の内径側の開口縁Ｄ１，Ｄ２の間隔Ｗ４は、玉１７の直径よりも小さく設定されるとともに、Ｗ４＞Ｗ３に設定されている。
【００４０】
以上のような構成により、大径保持器１９では、開口縁Ｃ１，Ｃ２、開口縁Ｄ１，Ｄ２が抜止め部として働き、ポケット８６内から玉１７が内径側および外径側に抜出ない構成になっている。なお、ポケット８６に対する玉１７の組込みは、ポケット８６の内径側から無理嵌めすることにより行うよう。
【００４１】
図７に示すように、ポケット８６の中心と玉１７の中心とを一致させた状態において、第１凹部９０の外径縁と玉１７との間のラジアル隙間Δ３は、第２凹部９１の内径縁と玉１７との間のラジアル隙間Δ４とほぼ同じ量になっている。以上が大径保持器１９と小径保持器２０の構成である。
【００４２】
前記複列玉軸受１０の前記内輪側組品２１における内輪部材１３は、ピニオン軸７の軸部９の一側端部に外嵌挿通されている。複列玉軸受１０の内輪部材１３における一側端面は、ピニオンギヤ６の他側端面に軸方向で当接している。複列玉軸受１０の内輪部材１３と、複列玉軸受２５の内輪部材１４の対向する端面間でピニオン軸７の軸部９の途中位置に、塑性スペーサ３３が介装されている。
【００４３】
フロントケース３の外壁と一側の環状壁２７間に、オイル循環路３０が形成されており、このオイル循環路３０のオイル入口３１は、オイル循環路３０のリングギヤ８側に開口され、オイル循環路３０のオイル出口３２は、環状壁２７，２８間に開口されている。
【００４４】
さらにディファレンシャル装置１は、コンパニオンフランジ３４を有し、このコンパニオンフランジ３４は、胴部３５とこの胴部３５に一体的に形成されるフランジ部３６とを有する。胴部３５は、ピニオン軸７の軸部９の他側、すなわち不図示のドライブシャフト側に外嵌するものである。
【００４５】
胴部３５の一側端面と複列玉軸受２５の内輪部材１４端面との間に、遮蔽板３７が介装されている。胴部３５の外周面とフロントケース３の他側開口内周面との間に、オイルシール３８が配置されている。オイルシール３８を覆うためのシール保護カップ３９が、フロントケース３の他側開口部に取付けられている。軸部９の他側外端部にねじ部４０が形成され、このねじ部４０は、フランジ部３６の中心凹部４１に突出している。ねじ部４０に、ナット４２が螺着されている。
【００４６】
ねじ部４０にナット４２を螺着することで、複列玉軸受１０の内輪部材１３および複列玉軸受２５の内輪部材１４がピニオンギヤ６の端面とコンパニオンフランジ３４の端面とで軸方向に挟み込まれ、遮蔽板３７および塑性スペーサ３３を介して、複列玉軸受１０および複列玉軸受２５に所定の予圧が付与されている。
【００４７】
上記構成のディファレンシャル装置１では、ディファレンシャルケース２内には、潤滑用のオイル４３が運転停止状態において所定のレベルにて貯留されている。オイル４３は、運転時にリングギヤ８の回転に伴って跳ね上げられ、フロントケース３内のオイル循環路３０を通って複列玉軸受１０および複列玉軸受２５に供給されるように導かれ、複列玉軸受１０および複列玉軸受２５を潤滑するよう、ディファレンシャルケース２内を循環する。
【００４８】
次に、上記構成のディファレンシャル装置１の組立方法を説明する。まず、複列玉軸受１０における内輪側組品２１の組立て順序を説明する。
【００４９】
一方列の玉群１５を構成する玉１７を、大径保持器１９のポケット８６に、その内径側から無理嵌めして、大径側組品Ｓ１とする。また他方列の玉群１６を構成する玉１８を、小径保持器２０のポケット８６に、その内径側から無理嵌めして、小径側組品Ｓ２とする。このように各玉１７，１８をそれぞれ大径保持器１９、小径保持器２０に装着した大径側組品Ｓ１、小径側組品Ｓ２では、保持器１９，２０の構成により何れの玉１７，１８も各保持器１９，２０から、外径側および内径側に抜出るのを防止された状態にある。
【００５０】
大径側組品Ｓ１において、大径保持器１９に保持された状態で各玉１７の内方側外周面を連ねた仮想円の径は、前記内輪環状面（筒状面部１３ａ）の径よりもわずかに小さい。さらに小径側組品Ｓ２において、小径保持器２０に保持された状態で各玉１８の内方側外周面を連ねた仮想円の径は、他側の肩部２３の径よりもわずかに小さい。
【００５１】
このような大径側組品Ｓ１および小径側組品Ｓ２における玉１７および玉１８を、それぞれ大径内輪軌道面１７ａ、小径内輪軌道面１８ａに嵌合するように、大径側組品Ｓ１および小径側組品Ｓ２を内輪部材１３に組込んで内輪側組品２１とする。
【００５２】
大径側組品Ｓ１および小径側組品Ｓ２を内輪部材１３に組込む際、大径側組品Ｓ１における玉１７は、内輪部材１３の外周面のうち傾斜案内面部１３ｂに案内された後、筒状面部１３ａを通過して、大径内輪軌道面１７ａに嵌合する。このようにすると、大径内輪軌道面１７ａの軌道径よりも筒状面部１３ａの径の方がわずかに大きいので、大径側組品Ｓ１は、内輪部材１３からその他側へ抜出る（離脱する）のが防止された状態となる。勿論、肩部２２によって大径側組品Ｓ１は、一側へ抜出るのも防止された状態となっている。加えて、各玉１７は、大径保持器１９の構成により外径側に抜出るのを防止された状態にある。従って、この時点で内輪部材１３と大径側組品Ｓ１との組品となる。
【００５３】
上記のようにして、大径側組品Ｓ１を内輪部材１３に組付けた後、今度は小径側組品Ｓ２を内輪部材１３に他側から組付ける。このとき、内輪部材１３における他側の肩部２３の径は、小径内輪軌道面１８ａの底の径よりもわずかに大径に形成されており、この肩部２３は、角Ｒとなる面取りが施されているため、小径側組品Ｓ２における玉１８は、面取り部によって円滑に案内され、無理嵌めによって肩部２３を乗越えた後、小径内輪軌道面１８ａに嵌合する。このようにすると、小径内輪軌道面１８ａの底の径よりも肩部２３の径の方がわずかに大きいので、小径側組品Ｓ２が内輪部材１３から他側へ抜出るのが防止された状態となる。加えて、各玉１８は、小径保持器２０の構成により、外径側に抜出るのを防止された状態にある。
【００５４】
このようにして内輪側組品２１の組立てを終了する。よって、この内輪側組品２１では、内輪部材１３と大径側組品Ｓ１および小径側組品Ｓ２が一体になった構成となり、取扱いが極めて便利となる。以上のことは、複列玉軸受２５における大径側組品、小径側組品および内輪部材１４からなる内輪側組品（図示せず）においても同様の作用効果となる。
【００５５】
一方で、フロントケース３とリヤケース４とを未だ分離させた状態で、複列玉軸受１０における外輪部材１１を、フロントケース３に組込む。このとき、外輪部材１１を、フロントケース３の一側開口から環状壁２７に形成されている段部に当たる軸心方向所定位置まで圧入するようにする。また、複列玉軸受２５の外輪部材１２を、フロントケース３の他側開口から、環状壁２８に形成されている段部に当たる軸心方向所定位置まで圧入する。
【００５６】
これとは別に、複列玉軸受１０側の内輪側組品２１を、ピニオン軸７の軸部９に組付けておく。すなわち内輪側組品２１の内輪部材１３を、ピニオン軸７の軸部９に挿通させ、内輪側組品２１をピニオン軸７の軸部９のピニオンギヤ６側に位置させておく。
【００５７】
上記のようにして内輪側組品２１を取付けたピニオン軸７を、その小径側から、またフロントケース３の一側開口から、内輪側組品２１における他方列の玉１８が外輪部材１１の小径外輪軌道面１１ｂに嵌合するよう、かつ内輪側組品２１における一方列の玉１７が外輪部材１１の大径外輪軌道面１１ａに嵌合するよう組込む。
【００５８】
このとき、内輪側組品２１の玉１８は、外輪環状面１１ｃの途中に形成された案内斜面１１ｄに案内され、玉１７は傾斜案内面１１ｅに案内されて、それぞれ円滑に大径外輪軌道面１１ｂ、小径外輪軌道面１１ａに嵌合する。
【００５９】
次に、塑性スペーサ３３を、フロントケース３の他側開口からピニオン軸７の軸部９に外嵌挿入する。続いて、複列玉軸受２５における内輪側組品を、フロントケース３の他側開口からピニオン軸７の軸部９に装着する。この場合、前記組品の内輪部材１４をピニオン軸７の軸部９に挿入して、玉２６，２９を外輪部材１２の外輪軌道面に嵌めるようにする。この場合の作用効果は、複列玉軸受１０における内輪側組品２１を外輪部材１１に組込む場合と同様である。
【００６０】
その後、遮蔽板３７をフロントケース３の他側開口からピニオン軸７の軸部９に挿通し、オイルシール３８を装着し、シール保護カップ３９をフロントケース３の他側開口部に取付け、シール保護カップ３９にコンパニオンフランジ３４の胴部３５を挿通してその端面を遮蔽板３７に当接させる。続いて、軸部９のねじ部４０にナット４２を螺着し、塑性スペーサ３３をアキシャル方向に押圧することで、複列玉軸受１０および複列玉軸受２５に所定の予圧を付与する。
【００６１】
上記のように、ピニオン軸７の軸部９を一側で回転自在に支持するための複列玉軸受１０は、外輪部材１１と内輪側組品２１とからなっている。そしてこの内輪側組品２１は、単一の内輪部材１３と、外輪部材１１と内輪部材１３との間に介装されて、ピッチ円直径Ｄ１，Ｄ２がそれぞれ異なる一方列の玉群１５および他方列の玉群１６と、これら玉群１５，１６を構成する玉１７，１８を、円周方向等配位置にそれぞれ保持する大径保持器１９および小径保持器２０とからなっており、両列の玉１７，１８はそれぞれ大径保持器１９および小径保持器２０によって、外径側に抜出るのを防止された状態で、かつ大径側組品Ｓ１および小径側組品Ｓ２は内輪部材１３から軸方向へ抜出るのを防止された状態で、内輪部材１３に保持されている。
【００６２】
従って、ピニオン軸７の一側に円錐ころ軸受を配置する代わりにタンデム型の複列玉軸受１０を用いる場合でも、円錐ころ軸受を用いた場合に内輪部材と円錐ころと保持器とをひとつの組品として扱うことができるのと同様に、内輪部材１３、一方列の玉群１５、他方列の玉群１６、大径保持器１９および小径保持器２０からなる内輪側組品２１として複列転がり軸受１０の構成部品を扱うことができるようになる。このため、従来の、円錐ころ軸受を用いた場合に比べても、ディファレンシャル装置１の組付け、特に軸受部分での組付けの際の作業性が低下することはない。この点については、ピニオン軸７をその他側で回転自在に支持する複列玉軸受２５についても同様の作用効果を奏し得る。
【００６３】
さらに、本発明の実施形態によれば、大きなスラスト荷重が働くピニオンギヤ６側の転がり軸受として、摩擦抵抗の小さい複列玉軸受１０を用いたことで、従来用いていた円錐ころ軸受に比べて回転トルクが小さくなる。これにより、ディファレンシャル装置１の効率を向上させることができる。しかも、単列の玉軸受でなく、複列玉軸受１０を用いたことにより、単列の玉軸受に比べて負荷容量を大きくすることができ、十分な支持剛性が得られる。
【００６４】
加えて、複列玉軸受１０として、一方列の玉群１５、すなわちピニオンギヤ６側の玉群１５のピッチ円直径Ｄ１を、他方列の玉群１６のピッチ円直径Ｄ２に比べて大きくしたタンデム型の複列玉軸受１０を用いたことにより、より大きなスラスト荷重が働くピニオンギヤ６側の玉群１６における玉１７の数を増加させることができ、大きな負荷に耐え得る。
【００６５】
上記実施形態では、ピニオン軸７を支持する両側の軸受について複列玉軸受１０，２５を用いたがこれに限定されるものではなく、ピニオン軸７の軸部９をその一側で支持する軸受として複列玉軸受１０を用い、他側で支持する軸受として、従来から用いられている単列の円錐ころ軸受としてもよい。
【００６６】
この場合であっても、ディファレンシャル装置１の組付け、特に軸受部分での組付けの際の作業性が低下することはない。
【００６７】
【発明の効果】
以上の説明から明らかな通り、本発明によれば、軸支持用の複列玉軸受を、円錐ころ軸受を用いた場合と同様の取扱いで所定の装置に組付けることができるので、円錐ころ軸受を複列玉軸受に変更したことによる作業性の低下や、組付けの際の煩雑さを防止することができる。
【図面の簡単な説明】
【図１】本発明の実施形態を示すディファレンシャル装置の全体構成を示す断面図である。
【図２】同じく内輪側組品の拡大断面図である。
【図３】同じく内輪側組品を外輪部材に組付ける際の拡大断面図である。
【図４】同じく内輪側組品を外輪部材に組付けた際の拡大断面図である。
【図５】同じく大径保持器の一側からの斜視図である。
【図６】同じく大径保持器の他側からの斜視図である。
【図７】同じく玉を保持した状態の保持器の一部断面図である。
【図８】同じく玉を保持した状態の保持器の一部側面図である。
【図９】同じく保持器の外径側からの平面図である。
【図１０】同じく保持器の内径側からの平面図である。
【図１１】従来例を示すディファレンシャル装置の全体構成を示す断面図である。
【符号の説明】
１ディファレンシャル装置
３フロントケース
４リヤケース
７ピニオン軸
９軸部
１０複列玉軸受
１１外輪部材
１５一方列の玉群
１６他方列の玉群
１９大径保持器
２０小径保持器
２１内輪側組品
Ｓ１大径側組品
Ｓ２小径側組品[0001]
BACKGROUND OF THE INVENTION
  The present invention is an assembly that constitutes a double-row ball bearing used in, for example, a differential device mounted on a vehicle.And assembly method of apparatus using double row ball bearing assemblyAbout.
[0002]
[Prior art]
A conventional differential device includes one in which both sides (a head side and a tail side) of a pinion shaft are rotatably supported by a tapered roller bearing (for example, see Patent Document 1).
[0003]
The configuration of the conventional differential device 60 will be described below with reference to FIG. FIG. 11 shows a cross-sectional structure of the differential device. The differential device 60 has a pinion shaft (drive pinion) 63 in the differential case 61. The pinion shaft 63 is supported by a pair of single-row tapered roller bearings 65 and 66 spaced apart in the axial direction so as to be rotatable around the axial center. A companion flange 64 connected to a propeller shaft (not shown) is provided at the end of the pinion shaft 63.
[0004]
  When assembling such a differential device 60, it is performed as follows.
(1)The outer ring members 69 and 70 of the tapered roller bearings 65 and 66 on both sides are press-fitted into the annular walls 67 and 68 formed in the differential case 61.
(2)The inner ring member 71 in the assembly of the inner ring member 71 of the tapered roller bearing 65 and the roller 73 is press-fitted into the pinion gear 62 side of the pinion shaft 63.
(3)The pinion shaft 63 is inserted from one side of the differential case 61, and the assembled roller 73 is fitted on the raceway surface of the outer ring member 69 of the tapered roller bearing 65 on one side.
(4)The inner ring member 72 is attached to the pinion shaft 63 so that the roller 74 in the assembly of the other side inner ring members 72 and 74 is fitted to the outer ring member 70 of the other side tapered roller bearing 66 and the outer ring raceway surface of the outer ring member 70. Press fit.
(5)A nut 75 is screwed onto the outer end portion of the pinion shaft 63, and a predetermined preload is applied to the rollers 73 and 74 of the tapered roller bearings 65 and 66 on both sides between the pinion gear 62 and the companion flange 64.
[0005]
In the differential device 60, the bearings that rotatably support the pinion shaft 63 are tapered roller bearings 65 and 66. In particular, a large frictional resistance acts on the tapered roller bearing 65 on the pinion gear 62 side having a large thrust load. For this reason, there exists a subject that rotational torque becomes large and the efficiency of the differential apparatus 60 falls. Therefore, it is conceivable to use a tandem double row ball bearing (for example, a double row angular ball bearing) instead of the tapered roller bearing 65 as the bearing on the pinion gear 62 side.
[0006]
[Patent Document 1]
JP 11-48805 (page 3, Fig. 1)
[0007]
[Problems to be solved by the invention]
  By the way, for example, even when the one side (pinion gear 62 side) tapered roller bearing 65 is used in place of the double row ball bearing, the differential device 60 is formed by the same process as in the assembly using the tapered roller bearing 65. As above, to be assembled(1)-(5)It is desirable not to change the process described in. For this reason, the assembly which has a some ball | bowl built in an outer ring member is needed.
[0008]
[Means for Solving the Problems]
  The double row ball bearing assembly of the present invention includes a large diameter inner ring raceway surface, an inner ring member including a small diameter inner ring raceway surface formed at a position axially separated from the large diameter inner ring raceway surface, and a large diameter The retainer and the large-diameter retainer are held at circumferentially equidistant positions, and the large-diameter retainer is prevented from being pulled out radially outward by a retaining portion formed in the large-diameter retainer. A ball on the large-diameter track that is fitted to the inner ring raceway surface, a small-diameter retainer, and a retaining portion formed in the small-diameter retainer while being held in the circumferentially equidistant position by the small-diameter retainer. The ball on the small-diameter track side that is fitted to the small-diameter inner ring raceway surface after fitting the large-diameter side ball to the large-diameter inner ring raceway surface in a state that is prevented from being pulled out radially outward by A ball held by the small-diameter retainer is pulled out from the small-diameter inner ring raceway surface in the axial direction. A shoulder having a diameter larger than that of the small-diameter inner ring raceway surface is formed, and the large-diameter retainer and the small-diameter retainer each have a plurality of pockets for mounting and holding each ball. A large ring formed on the outer diameter side of the virtual cylindrical surface obtained by extending the pitch circle diameter of each pocket in the axial direction, and an inner diameter larger than the virtual cylindrical surface. A small ring portion formed on the side, and a plurality of bridging portions connecting several circumferential points of the large ring portion and the small ring portion, and the pocket is adjacent to the large ring portion in the circumferential direction 2 A combination of a substantially semicircular first recess formed by the two bridging portions and a substantially semicircular second recess formed by the two bridging portions adjacent to the small ring portion in the circumferential direction. The interval W3 of the opening edge on the outer diameter side of the first recess is equal to the interval W4 of the opening edge on the inner diameter side of the second recess. It is set in a smallIn addition, the outer peripheral surface of each bridging portion is connected to the large ring portion and is a plane along the axial direction, and a slope that is connected to the small ring portion and is reduced in diameter toward the small ring portion. Is formed continuously at the center in the axial direction of the bridging portion, and the joint portion is formed between the radially outer end portion of the inner surface of the first recess in the large ring portion and the inner surface of the second recess in the small ring portion. It is arranged on the outer diameter side of the virtual conical surface connecting the radially outer end portion with a straight line, and the inner peripheral surface of each bridging portion is connected to the small ring portion and a plane along the axial direction, and the large ring portion It is connected to the large ring portion and has a slope that is enlarged in diameter, and the flat surface and the slope are formed continuously at the center in the axial direction of the bridging portion. The radially inner end portion of the inner surface and the first in the small ring portion And is disposed on the inner diameter side than the virtual conical surface connecting the points radially inner end of the inner surface of the recess in a straight line.
[0009]
In the above configuration, the ball is fitted to the large-diameter inner ring raceway surface of the inner ring member with the ball assembled to the large-diameter cage, and the ball is assembled to the small-diameter inner ring of the inner ring raceway surface with the ball assembled to the small-diameter cage. By fitting to the raceway surface, a double row ball bearing assembly is obtained.
[0010]
When assembling a double row ball bearing using such a double row ball bearing assembly, for example, an outer ring member is assembled in advance on the inner surface of the housing, and the shaft is inserted into the inner ring member of the double row ball bearing assembly. In addition, the double-row ball bearing is adapted so that the ball held in the small-diameter retainer in the double-row ball bearing assembly is fitted to the small-diameter outer ring raceway surface of the outer ring member so that the shaft is inserted into the housing. The ball held by the large-diameter cage is assembled so as to fit the large-diameter outer ring raceway surface of the outer ring member.
[0011]
At this time, the balls in both rows in the double row ball bearing assembly are prevented from being pulled out in the radially outward direction and the axial direction, so that they can be easily handled as a single unit. It becomes possible to assemble the double row ball bearing assembly to the outer ring member in the same manner as in the case of using it.
[0012]
Further, the double row ball bearing assembly of the present invention prevents the ball on the large diameter raceway side held by the large diameter cage from being pulled out from the large diameter inner ring raceway surface in the inner ring member in the axial direction. Therefore, a retaining portion having a larger diameter than the large-diameter inner ring raceway surface is formed on a continuous surface between the large-diameter inner ring raceway surface and the small-diameter inner ring raceway surface.
[0013]
According to this configuration, the ball is prevented from being pulled out radially outward and axially by fitting the ball to the large diameter inner ring raceway surface of the inner ring member in a state where the ball is assembled to the large diameter cage. Therefore, without holding these balls using special means, fit the balls in the assembled state with the small-diameter cage into the small-diameter inner ring raceway surface of the inner ring raceway. Can be combined and assembled.
[0014]
Furthermore, the assembly for the double row ball bearing is axially connected to the inner ring member in a state where balls are held by the large diameter cage on a continuous surface between the large diameter inner ring raceway surface and the small diameter inner ring raceway surface. A slope for guiding the balls when assembled is formed.
[0015]
According to this configuration, the ball held by the large-diameter cage is smoothly guided toward the large-diameter inner ring raceway surface by being guided by the inclined surface, and can be fitted thereto.
[0016]
  Depending on how the load is applied to the double-row ball bearing, both rows in the double-row ball bearing assembly are fitted to the large-diameter outer ring raceway surface and the small-diameter outer ring raceway surface of the outer ring member, respectively. In addition to setting the contact angles of the balls in both rows to be the same, it is desirable to set the contact angles to different angles.
  Further, the method of assembling the apparatus using the double row ball bearing assembly according to the present invention is obtained by forcibly fitting a ball from the inner diameter side into the pocket of each cage for each of the large diameter cage and the small diameter cage. The large-diameter side assembly and the small-diameter side assembly are assembled so as to be fitted to the large-diameter inner ring raceway surface and the small-diameter inner ring raceway surface of the inner ring member, respectively. The small diameter side assembly is assembled from the small diameter side so that the large diameter side assembly is fitted to the large diameter outer ring raceway surface and the small diameter side assembly is fitted to the small diameter outer ring raceway surface.
[0017]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the figure, the double row rolling bearing assembly according to the embodiment of the present invention is applied to a pinion shaft support bearing of a differential device attached to a vehicle.
[0018]
As shown in the overall sectional view of FIG. 1, the differential device 1 has a differential case 2. The differential case 2 includes a front case 3 and a rear case 4, and the cases 3 and 4 are integrally attached by bolts and nuts 2a.
[0019]
The differential case 2 includes a differential transmission mechanism 5 that differentially interlocks the left and right wheels, and a pinion shaft (drive pinion) 7 having a pinion gear 6 on one side in the axial direction (hereinafter simply referred to as one side). The pinion gear 6 is meshed with the ring gear 8 of the differential transmission mechanism 5. The shaft portion 9 of the pinion shaft 7 has a stepped outer peripheral surface so that the other side in the axial direction (hereinafter simply referred to as the other side) has a smaller diameter than the one side.
[0020]
One side of the shaft portion 9 of the pinion shaft 7 is supported by the differential case 2 via a double row ball bearing 10 so as to be rotatable about the axis. The other end of the shaft portion 9 of the pinion shaft 7 is supported by the differential case 2 via a double row ball bearing 25 so as to be rotatable about the axis.
[0021]
Inner walls 27 and 28 for mounting bearings are formed on the inner side of the front case 3, and the outer ring member 11 of the double row ball bearing 10 and the outer ring member 12 of the double row ball bearing 25 are respectively annular walls 27 and 28. It is fitted on the inner peripheral surface of.
[0022]
The double-row ball bearings 10 and 25 are symmetrical in the axial direction of the pinion shaft 7, and the diameter of the double-row ball bearing 25 is smaller than the diameter of the double-row ball bearing 10. The diameter is reduced by the amount of fitting.
[0023]
That is, the double-row ball bearing 25 includes the inner ring member 14, the outer ring member 12, two rows of balls 26 and 29 having different pitch circle diameters, and cages 44 and 45 thereof. The inner ring member 14 is fitted in the middle of the pinion shaft 7 in the axial direction.
[0024]
As described above, the double-row ball bearings 10 and 25 are symmetrical in the axial direction and only have different diameters. Therefore, the detailed configuration of the double-row ball bearing 10 on one side will be described below. .
[0025]
The double row ball bearing 10 is composed of a single outer ring member 11 and an inner ring side assembly 21 as a double row rolling bearing assembly shown in FIG. As shown in FIG. 3, the outer ring member 11 has an inner peripheral surface formed in a step shape. That is, on the inner peripheral surface of the outer ring member 11, a large-diameter outer ring raceway surface 11a on one side, a small-diameter outer ring raceway surface 11b formed on a portion separated from the large-diameter outer ring raceway surface 11a on the other side, The outer ring annular surface 11c is formed between the surfaces 11a and 11b, and an inclined stepped surface 11d whose diameter increases toward the other side is formed in the middle of the outer ring annular surface 11c. Furthermore, an inclined guide surface 11e that is enlarged in diameter toward the other side is formed on one side of the inner peripheral surface of the outer ring member 11.
[0026]
As shown in FIG. 2, the inner ring side assembly 21 is interposed between a single inner ring member 13 disposed radially inward of the outer ring member 11, and the outer ring member 11 and the inner ring member 13. A large group for holding the ball group 15 in one row and the ball group 16 in the other row with different pitch circle diameters D1 and D2 and the balls 17 and 18 constituting these ball groups 15 and 16 at equal circumferential positions, respectively. A diameter holder 19 and a small diameter holder 20 are provided.
[0027]
As shown in the figure, the inner ring member 13 has a stepped outer peripheral surface. That is, on the outer peripheral surface of the inner ring member 13, a large-diameter inner ring raceway surface 17a on one side, a small-diameter inner ring raceway surface 18a formed on the other side away from the large-diameter inner ring raceway surface 17a, and a large-diameter inner ring An inner ring annular surface formed between the raceway surface 17a and the small-diameter inner ring raceway surface 18a is formed.
[0028]
The inner ring annular surface is formed on the large-diameter inner ring raceway surface 17a side, extends along the axial direction, and has a cylindrical surface portion 13a as a holding portion having a predetermined length L in the axial direction, and the cylindrical surface portion 13a and the small-diameter inner ring. And an inclined guide surface portion 13b continuous with the raceway surface 18a. The diameter of the cylindrical surface portion 13a is slightly larger than the diameter of the bottom of the large-diameter inner ring raceway surface 17a.
[0029]
Of the shoulder portions 22 and 23 formed on both sides in the axial direction of the inner ring member 13, the diameter of the shoulder portion 23 on the other side is slightly larger than the diameter of the bottom of the small-diameter inner ring raceway surface 18a. Both shoulder portions 22 and 23 are chamfered to form a corner R. The diameter of the ball 17 on the large-diameter track side and the diameter of the ball 18 on the small-diameter track side are substantially the same.
[0030]
Furthermore, as shown in the cross-sectional view of FIG. 4, in the double row ball bearing 10 according to the embodiment of the present invention, the ball 17 in the ball group 15 in one row and the ball 18 in the ball group 16 in the other row are combined. When 21 is assembled to the outer ring member 11, the contact angles θ 1 and θ 2 are configured to differ by a necessary angle according to the function of the load.
[0031]
Thus, the outer ring member 11 has the large-diameter outer ring raceway surface 11a and the small-diameter inner ring raceway surface 11b, and the inner ring member 13 has the large-diameter inner ring raceway surface 17a and the small-diameter inner ring raceway surface 18a. The double row ball bearing 10 having a configuration in which the pitch circle diameters D1 and D2 in the group 15 and the ball group 16 in the other row are different is referred to as a tandem type rolling bearing.
[0032]
Here, based on FIG. 5 thru | or FIG. 10, the structure of the large diameter holder 19 and the small diameter holder 20 in the double row ball bearing 10 is demonstrated. The large-diameter retainer 19 and the small-diameter retainer 20 have different diameters, and the number of pockets 86 of the small-diameter retainer 20 is only smaller than the number of pockets 89 of the large-diameter retainer 19. With the description of the configuration of 19, the description of the configuration of the small diameter holder 20 is also substituted.
[0033]
As shown in the perspective views of FIGS. 5 and 6, the large-diameter retainer 19 is formed with a plurality of pockets 86 for mounting the balls 17 at several places around the circumference of the ring. These pockets 86 are formed so as to penetrate the ring body in the direction along the load action line X (see FIG. 4).
[0034]
Then, as shown in FIG. 7, a large ring formed on the outer diameter side of the virtual cylindrical surface Y obtained by extending the pitch circle diameter of each pocket 86 (diameter of the circle connecting the centers of the pockets 86) in the axial direction. Part 87, small ring part 88 formed on the inner diameter side of virtual cylindrical surface Y, and a plurality of bridging parts connecting several circumferential points of large ring part 87 and small ring part 88 as shown in FIG. (Pillar) 89 and the like.
[0035]
The pocket 86 includes a substantially semicircular first recess 90 formed by two bridging portions 89 adjacent to the large ring portion 87 in the circumferential direction, and two bridging portions 89 adjacent to the small ring portion 88 in the circumferential direction. A substantially semicircular second recess 91 is formed in combination.
[0036]
In each of the two bridging portions 89 and 89 adjacent in the circumferential direction, the inner surface of the first recess 90 and the inner surface of the second recess 91 are formed as spherical concave surfaces set to the same curvature as the curvature of the ball 17. .
[0037]
On the outer peripheral surface of the bridging portion 89, the plane 89a and the slope 89b along the axial direction are continuously formed at the center in the axial direction, and the joint portion 89c is connected to the large ring portion 87 and the small ring portion 88 by a straight line. It arrange | positions on the outer diameter side rather than the virtual conical surface Z1.
[0038]
On the inner peripheral surface of the bridging portion 89, a plane 89d and an inclined surface 89e along the axial direction are continuously formed at the center in the axial direction, and the joint portion 89f is a straight line between the large ring portion 87 and the small ring portion 88. It arrange | positions rather than the virtual conical surface Z2 to connect to the inner diameter side.
[0039]
As shown in FIGS. 9 and 10, the distance W3 between the opening edges C1 and C2 on the outer diameter side of the first recess 90 and the distance W4 between the opening edges D1 and D2 on the inner diameter side of the second recess 91 are It is set smaller than the diameter and W4> W3.
[0040]
With the configuration as described above, in the large-diameter retainer 19, the opening edges C1 and C2 and the opening edges D1 and D2 function as a retaining portion, and the ball 17 is not pulled out from the pocket 86 to the inner diameter side and the outer diameter side. It has become. The ball 17 is assembled into the pocket 86 by forcibly fitting it from the inner diameter side of the pocket 86.
[0041]
As shown in FIG. 7, in the state where the center of the pocket 86 and the center of the ball 17 are aligned, the radial gap Δ3 between the outer diameter edge of the first recess 90 and the ball 17 is the inner diameter of the second recess 91. The amount is almost the same as the radial gap Δ4 between the edge and the ball 17. The above is the configuration of the large-diameter cage 19 and the small-diameter cage 20.
[0042]
The inner ring member 13 in the inner ring side assembly 21 of the double row ball bearing 10 is externally inserted into one end of the shaft part 9 of the pinion shaft 7. One end face of the inner ring member 13 of the double row ball bearing 10 is in contact with the other end face of the pinion gear 6 in the axial direction. A plastic spacer 33 is interposed in the middle of the shaft portion 9 of the pinion shaft 7 between the opposing end surfaces of the inner ring member 13 of the double row ball bearing 10 and the inner ring member 14 of the double row ball bearing 25.
[0043]
An oil circulation path 30 is formed between the outer wall of the front case 3 and the annular wall 27 on one side, and an oil inlet 31 of the oil circulation path 30 is opened to the ring gear 8 side of the oil circulation path 30 so as to circulate the oil. An oil outlet 32 of the passage 30 is opened between the annular walls 27 and 28.
[0044]
Further, the differential device 1 has a companion flange 34, and the companion flange 34 has a body portion 35 and a flange portion 36 formed integrally with the body portion 35. The body portion 35 is externally fitted to the other side of the shaft portion 9 of the pinion shaft 7, that is, the drive shaft side (not shown).
[0045]
A shielding plate 37 is interposed between one end face of the body portion 35 and the end face of the inner ring member 14 of the double row ball bearing 25. An oil seal 38 is disposed between the outer peripheral surface of the trunk portion 35 and the inner peripheral surface of the other opening of the front case 3. A seal protection cup 39 for covering the oil seal 38 is attached to the other side opening of the front case 3. A threaded portion 40 is formed at the other outer end portion of the shaft portion 9, and the threaded portion 40 projects into the central recess 41 of the flange portion 36. A nut 42 is screwed onto the screw portion 40.
[0046]
By screwing the nut 42 onto the screw portion 40, the inner ring member 13 of the double row ball bearing 10 and the inner ring member 14 of the double row ball bearing 25 are sandwiched between the end face of the pinion gear 6 and the end face of the companion flange 34 in the axial direction. A predetermined preload is applied to the double row ball bearing 10 and the double row ball bearing 25 through the shielding plate 37 and the plastic spacer 33.
[0047]
In the differential device 1 having the above-described configuration, the lubricating oil 43 is stored in the differential case 2 at a predetermined level when the operation is stopped. The oil 43 is spun up along with the rotation of the ring gear 8 during operation, and is guided to be supplied to the double row ball bearing 10 and the double row ball bearing 25 through the oil circulation path 30 in the front case 3. It circulates in the differential case 2 so as to lubricate the row ball bearing 10 and the double row ball bearing 25.
[0048]
Next, a method for assembling the differential device 1 having the above-described configuration will be described. First, the assembly sequence of the inner ring side assembly 21 in the double row ball bearing 10 will be described.
[0049]
The balls 17 constituting the ball group 15 on one row are forcibly fitted into the pockets 86 of the large-diameter retainer 19 from the inner diameter side to obtain a large-diameter side assembly S1. Further, the balls 18 constituting the ball group 16 in the other row are forcibly fitted into the pocket 86 of the small-diameter retainer 20 from the inner diameter side to obtain a small-diameter assembly S2. Thus, in the large-diameter side assembly S1 and the small-diameter side assembly S2 in which the balls 17 and 18 are mounted on the large-diameter retainer 19 and the small-diameter retainer 20, respectively, depending on the configuration of the retainers 19 and 20, 18 is also in a state in which it is prevented from being pulled out from the cages 19 and 20 to the outer diameter side and the inner diameter side.
[0050]
In the large-diameter side assembly S1, the diameter of the virtual circle connecting the inner peripheral surfaces of the balls 17 while being held by the large-diameter retainer 19 is larger than the diameter of the inner ring annular surface (cylindrical surface portion 13a). Is also slightly smaller. Further, in the small-diameter side assembly S2, the diameter of the imaginary circle connecting the inner peripheral surfaces of the balls 18 while being held by the small-diameter retainer 20 is slightly smaller than the diameter of the shoulder 23 on the other side.
[0051]
The large-diameter side assembly S1 and the ball 18 in the large-diameter side assembly S1 and the small-diameter side assembly S2 are fitted to the large-diameter inner ring raceway surface 17a and the small-diameter inner ring raceway surface 18a, respectively. The small-diameter side assembly S2 is assembled into the inner ring member 13 to form an inner ring-side assembly 21.
[0052]
When the large-diameter side assembly S1 and the small-diameter side assembly S2 are assembled into the inner ring member 13, the balls 17 in the large-diameter side assembly S1 are guided to the inclined guide surface portion 13b on the outer peripheral surface of the inner ring member 13, and then the cylinder It passes through the shaped surface portion 13a and is fitted to the large-diameter inner ring raceway surface 17a. In this case, since the diameter of the cylindrical surface portion 13a is slightly larger than the track diameter of the large-diameter inner ring raceway surface 17a, the large-diameter side assembly S1 is pulled out (detached) from the inner ring member 13 to the other side. ) Is prevented. Of course, the shoulder portion 22 prevents the large-diameter assembly S1 from being pulled out to one side. In addition, each ball 17 is in a state of being prevented from being pulled out to the outer diameter side by the configuration of the large-diameter retainer 19. Therefore, at this time, the inner ring member 13 and the large-diameter side assembly S1 are assembled.
[0053]
After the large-diameter side assembly S1 is assembled to the inner ring member 13 as described above, the small-diameter side assembly S2 is then assembled to the inner ring member 13 from the other side. At this time, the diameter of the shoulder 23 on the other side of the inner ring member 13 is formed to be slightly larger than the diameter of the bottom of the small-diameter inner ring raceway surface 18a, and the shoulder 23 is chamfered at an angle R. Therefore, the ball 18 in the small-diameter side assembly S2 is smoothly guided by the chamfered portion, and after getting over the shoulder portion 23 by forcible fitting, the ball 18 is fitted to the small-diameter inner ring raceway surface 18a. In this case, since the diameter of the shoulder 23 is slightly larger than the diameter of the bottom of the small-diameter inner ring raceway surface 18a, the small-diameter side assembly S2 is prevented from being pulled out from the inner ring member 13 to the other side. It becomes. In addition, each ball 18 is in a state of being prevented from being pulled out to the outer diameter side by the configuration of the small-diameter retainer 20.
[0054]
In this way, the assembly of the inner ring side assembly 21 is completed. Therefore, in this inner ring side assembly 21, the inner ring member 13, the large diameter side assembly S1 and the small diameter side assembly S2 are integrated, and handling becomes extremely convenient. The above is the same effect in the inner ring side assembly (not shown) including the large diameter side assembly, the small diameter side assembly, and the inner ring member 14 in the double row ball bearing 25.
[0055]
On the other hand, the outer ring member 11 in the double row ball bearing 10 is assembled in the front case 3 in a state where the front case 3 and the rear case 4 are still separated. At this time, the outer ring member 11 is press-fitted from the opening on one side of the front case 3 to a predetermined position in the axial direction corresponding to the step formed on the annular wall 27. Further, the outer ring member 12 of the double row ball bearing 25 is press-fitted from the other side opening of the front case 3 to a predetermined position in the axial direction corresponding to the step formed in the annular wall 28.
[0056]
Separately, the inner ring side assembly 21 on the double row ball bearing 10 side is assembled to the shaft portion 9 of the pinion shaft 7. That is, the inner ring member 13 of the inner ring side assembly 21 is inserted into the shaft portion 9 of the pinion shaft 7, and the inner ring side assembly 21 is positioned on the pinion gear 6 side of the shaft portion 9 of the pinion shaft 7.
[0057]
The pinion shaft 7 to which the inner ring side assembly 21 is mounted as described above is arranged so that the ball 18 in the other row of the inner ring side assembly 21 has a small diameter of the outer ring member 11 from the small diameter side and from one side opening of the front case 3. The balls 17 in one row of the inner ring side assembly 21 are assembled so as to be fitted to the outer ring raceway surface 11 b and the large diameter outer ring raceway surface 11 a of the outer ring member 11.
[0058]
At this time, the ball 18 of the inner ring side assembly 21 is guided by a guide slope 11d formed in the middle of the outer ring annular surface 11c, and the ball 17 is guided by the inclined guide surface 11e, and each smoothly and smoothly has a large-diameter outer ring raceway surface. 11b, which is fitted to the small-diameter outer ring raceway surface 11a.
[0059]
Next, the plastic spacer 33 is externally inserted into the shaft portion 9 of the pinion shaft 7 from the other side opening of the front case 3. Subsequently, the inner ring side assembly in the double row ball bearing 25 is mounted on the shaft portion 9 of the pinion shaft 7 from the other side opening of the front case 3. In this case, the inner ring member 14 of the assembly is inserted into the shaft portion 9 of the pinion shaft 7 so that the balls 26 and 29 are fitted on the outer ring raceway surface of the outer ring member 12. The effect in this case is the same as the case where the inner ring side assembly 21 in the double row ball bearing 10 is assembled into the outer ring member 11.
[0060]
Thereafter, the shielding plate 37 is inserted from the other side opening of the front case 3 into the shaft portion 9 of the pinion shaft 7, the oil seal 38 is attached, and the seal protection cup 39 is attached to the other side opening of the front case 3 to protect the seal. The body portion 35 of the companion flange 34 is inserted into the cup 39 and the end surface thereof is brought into contact with the shielding plate 37. Subsequently, a nut 42 is screwed onto the screw portion 40 of the shaft portion 9 and the plastic spacer 33 is pressed in the axial direction, whereby a predetermined preload is applied to the double row ball bearing 10 and the double row ball bearing 25.
[0061]
As described above, the double-row ball bearing 10 for rotatably supporting the shaft portion 9 of the pinion shaft 7 on one side includes the outer ring member 11 and the inner ring side assembly 21. The inner ring side assembly 21 is interposed between a single inner ring member 13, the outer ring member 11 and the inner ring member 13, and one group of balls 15 and the other having different pitch circle diameters D 1 and D 2. The ball group 16 of the row | line | column and the large diameter holder | retainer 19 and the small diameter holder | retainer 20 which hold | maintain the balls 17 and 18 which comprise these ball groups 15 and 16 in the circumferential direction equidistant position respectively, The balls 17 and 18 are prevented from being pulled out to the outer diameter side by the large-diameter retainer 19 and the small-diameter retainer 20, and the large-diameter side assembly S1 and the small-diameter side assembly S2 are the inner ring member 13. It is held by the inner ring member 13 in a state where it is prevented from being pulled out in the axial direction.
[0062]
Therefore, even when the tandem double-row ball bearing 10 is used instead of the tapered roller bearing disposed on one side of the pinion shaft 7, when the tapered roller bearing is used, the inner ring member, the tapered roller and the cage are combined into one. In the same way that it can be handled as an assembly, the inner ring member 13, one row of ball group 15, the other row of ball group 16, a large diameter cage 19 and a small diameter cage 20, double row as an inner ring side assembly 21. The components of the rolling bearing 10 can be handled. For this reason, even if it compares with the case where the conventional tapered roller bearing is used, the workability | operativity at the time of the assembly | attachment of the differential apparatus 1, especially the assembly in a bearing part does not fall. About this point, the same effect can be show | played also about the double row ball bearing 25 which supports the pinion shaft 7 rotatably on the other side.
[0063]
Furthermore, according to the embodiment of the present invention, the double row ball bearing 10 having a low frictional resistance is used as the rolling bearing on the pinion gear 6 side where a large thrust load is applied, so that it can be rotated as compared with a conventionally used tapered roller bearing. Torque is reduced. Thereby, the efficiency of the differential apparatus 1 can be improved. Moreover, by using the double row ball bearing 10 instead of the single row ball bearing, the load capacity can be increased as compared with the single row ball bearing, and sufficient support rigidity can be obtained.
[0064]
In addition, as the double row ball bearing 10, the tandem type in which the pitch circle diameter D1 of the ball group 15 in one row, that is, the ball group 15 on the pinion gear 6 side, is larger than the pitch circle diameter D2 of the ball group 16 in the other row. By using this double-row ball bearing 10, the number of balls 17 in the ball group 16 on the pinion gear 6 side on which a larger thrust load acts can be increased, and a large load can be endured.
[0065]
In the above embodiment, the double-row ball bearings 10 and 25 are used as the bearings on both sides that support the pinion shaft 7, but the present invention is not limited to this, and the bearing that supports the shaft portion 9 of the pinion shaft 7 on one side thereof. The double row ball bearing 10 may be used as a bearing supported on the other side as a single row tapered roller bearing conventionally used.
[0066]
Even in this case, workability at the time of assembling the differential device 1, particularly at the bearing portion, does not deteriorate.
[0067]
【The invention's effect】
As apparent from the above description, according to the present invention, the double-row ball bearing for shaft support can be assembled to a predetermined device in the same manner as when a tapered roller bearing is used. Therefore, it is possible to prevent deterioration in workability due to the change to the double-row ball bearing and the complexity during assembly.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing an overall configuration of a differential apparatus showing an embodiment of the present invention.
FIG. 2 is an enlarged sectional view of the inner ring side assembly.
FIG. 3 is an enlarged cross-sectional view when the inner ring side assembly is similarly assembled to the outer ring member.
FIG. 4 is an enlarged cross-sectional view when the inner ring side assembly is similarly assembled to the outer ring member.
FIG. 5 is a perspective view from one side of the large-diameter retainer.
FIG. 6 is a perspective view of the large diameter cage from the other side.
FIG. 7 is a partial cross-sectional view of the cage in a state where the ball is similarly held.
FIG. 8 is a partial side view of the cage in a state where the ball is similarly held.
FIG. 9 is a plan view similarly from the outer diameter side of the cage.
FIG. 10 is a plan view similarly from the inner diameter side of the cage.
FIG. 11 is a cross-sectional view showing an overall configuration of a differential apparatus showing a conventional example.
[Explanation of symbols]
1 Differential equipment
3 Front case
4 Rear case
7 Pinion shaft
9 Shaft
10 Double row ball bearing
11 Outer ring member
15 Balls in one row
16 Balls in the other row
19 Large diameter cage
20 Small diameter cage
21 Inner ring side assembly
S1 Large diameter side assembly
S2 Small diameter side assembly

Claims

A double row ball bearing assembly assembled from an axial direction with respect to an outer ring member having a large diameter outer ring raceway surface and a small diameter outer ring raceway surface,
An inner ring member including a large-diameter inner ring raceway surface and a small-diameter inner ring raceway surface formed in a position axially separated from the large-diameter inner ring raceway surface;
A large-diameter retainer and a state where the large-diameter retainer is held at a circumferentially equidistant position and prevented from being pulled out radially outward by a retaining portion formed in the large-diameter retainer. A ball on the large-diameter track side that is fitted to the raceway surface of the large-diameter inner ring, a small-diameter retainer, and the small-diameter retainer are held in a circumferentially equidistant position, and are formed in the small-diameter retainer A ball on the small-diameter track side that is fitted to the small-diameter inner ring raceway surface after the large-diameter side ball is fitted to the large-diameter inner ring raceway surface in a state that is prevented from being pulled out radially outward by a stopper. Including
A shoulder having a diameter larger than that of the small-diameter inner ring raceway surface is formed on the inner ring member to prevent the balls held in the small-diameter retainer from being pulled out from the small-diameter inner ring raceway surface in an axial direction.
The large-diameter cage and the small-diameter cage are formed with a plurality of pockets for mounting and holding each ball at several places around the circumference of the ring, and the pitch circle diameter of each pocket is determined in the axial direction. A large ring portion formed on the outer diameter side of the virtual cylindrical surface obtained by extending to the inner ring, a small ring portion formed on the inner diameter side of the virtual cylindrical surface, and a circle of the large ring portion and the small ring portion It is formed from a plurality of bridging sections that connect several places,
The pocket is formed of a substantially semicircular first recess formed by the two bridging portions adjacent to the large ring portion in the circumferential direction, and two bridging portions adjacent to the small ring portion in the circumferential direction. And a substantially semicircular second recess,
The interval W3 of the opening edge on the outer diameter side of the first recess is set smaller than the interval W4 of the opening edge on the inner diameter side of the second recess ,
The outer peripheral surface of each bridging portion is composed of a plane that is connected to the large ring portion and extends in the axial direction, and a slope that is connected to the small ring portion and is reduced in diameter toward the small ring portion. Are formed continuously at the center in the axial direction of the portion, and the joint portion is radially outer end of the inner surface of the first recess in the large ring portion and the radial direction of the inner surface of the second recess in the small ring portion. Arranged on the outer diameter side of the virtual conical surface connecting the outer end portion with a straight line,
The inner peripheral surface of each bridging portion is a plane that is connected to the small ring portion and extends along the axial direction, and a slope that is connected to the large ring portion and has a diameter that increases toward the large ring portion. Are formed continuously at the center in the axial direction of the portion, and the joint portion is radially inward of the inner surface of the first recess in the large ring portion and the radial direction of the inner surface of the second recess in the small ring portion. An assembly for a double row ball bearing, wherein the assembly is arranged on the inner diameter side of a virtual conical surface connecting the inner end portion with a straight line .

A double-row ball bearing assembly according to claim 1,
The inner ring member has a larger diameter than the large-diameter inner ring raceway surface for preventing the ball on the large-diameter raceway side held by the large-diameter cage from being pulled out from the large-diameter inner ring raceway surface in the axial direction. The double row ball bearing assembly is characterized in that a retaining portion is formed on a continuous surface between the large-diameter inner ring raceway surface and the small-diameter inner ring raceway surface.

A double-row ball bearing assembly according to claim 1 or 2,
A slope for guiding the ball when it is assembled in the inner ring member from the axial direction in a state where the ball is held in the large-diameter retainer on a continuous surface between the large-diameter inner ring raceway surface and the small-diameter inner ring raceway surface. An assembly for a double row ball bearing, characterized in that is formed.

A method for assembling an apparatus using the double-row ball bearing assembly according to any one of claims 1 to 3,
For each of the large-diameter cage and the small-diameter cage, a large-diameter side assembly and a small-diameter side assembly obtained by forcibly fitting balls from the inner diameter side into pockets of the respective cages, respectively, Assemble the inner ring raceway surface and the small inner ring raceway surface,
After that, this assembly is assembled from the small diameter side so that the large diameter side assembly is fitted to the large diameter outer ring raceway surface of the outer ring member and the small diameter side assembly is fitted to the small diameter outer ring raceway surface. A method of assembling an apparatus using a double row ball bearing assembly characterized by the above.