JP2010091054A - Conical roller bearing device - Google Patents

Conical roller bearing device Download PDF

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Publication number
JP2010091054A
JP2010091054A JP2008262967A JP2008262967A JP2010091054A JP 2010091054 A JP2010091054 A JP 2010091054A JP 2008262967 A JP2008262967 A JP 2008262967A JP 2008262967 A JP2008262967 A JP 2008262967A JP 2010091054 A JP2010091054 A JP 2010091054A
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Prior art keywords
lubricating oil
inner ring
ring member
tapered roller
bearing
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JP2008262967A
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Japanese (ja)
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Ryosuke Nakado
了介 中堂
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JTEKT Corp
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JTEKT Corp
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Priority to JP2008262967A priority Critical patent/JP2010091054A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

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  • Rolling Contact Bearings (AREA)
  • General Details Of Gearings (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To release heat from a major collar part that is the major diameter end side of an inner ring member where the temperature tends to rise in a conical roller bearing. <P>SOLUTION: In a rear bearing 28 as the conical roller bearing including an inner ring member 28a, an outer ring member 28c, and a conical roller 28b, in which lubricating oil L for smoothing rolling of the conical roller 28b flows from a minor collar part 28a-1 side that is the minor diameter end side of the inner ring member 28a and discharges to a major collar part 28a-2 side that is the major diameter end side, a lubricating oil storage part 36 capable of storing the lubricating oil L is formed on the major collar part side 28a-2 to which the lubricating oil L is discharged, and a cooling member 29 formed in an annular shape is arranged on the major collar part 28a-2 that is the major diameter end side of the inner ring member 28a in a manner such that it can contact therewith. The arrangement position of the outer shape of the cooling member 29 is set to a position where at least its outer circumferential end portion can contact the lubricating oil L stored in the storage part 36. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、円すいころ軸受装置に関する。詳細には、円すいころの転動を円滑にする潤滑油が、内輪部材の小径端部側から流入し、大鍔部側に排出される円すいころ軸受装置に関する。   The present invention relates to a tapered roller bearing device. More specifically, the present invention relates to a tapered roller bearing device in which lubricating oil that smoothly rolls a tapered roller flows from the small diameter end portion side of the inner ring member and is discharged to the large collar portion side.

図５に図示されるように、従来、例えば、自動車等車両の駆動経路に設置される汎用のデファレンシャル装置は、デファレンシャルキャリア１１２内にデファレンシャルリングギヤ１１４とドライブピニオン１１６が噛合して配置されて構成されている。例えば、四輪駆動車両のフロントデファレンシャル装置１１０において、ドライブピニオン１１６を端部に一体形成したドライブピニオンシャフト１１８は該シャフトに軸方向に間隔を置いて嵌合配置されたフロント軸受１２６及びリヤ軸受１２８によりデファレンシャルキャリア１１２に支持されており、両軸受間には両軸受を潤滑する潤滑油Ｌのオイル溜り１３０が形成されている。この両軸受間に形成されたオイル溜り１３０と、デファレンシャルリングギヤ１１４が配置された潤滑油室１３２との間には潤滑油Ｌを導入するための導入流路１３４が形成されており、デファレンシャルリングギヤ１１４により掻き揚げられた潤滑油Ｌをオイル溜り１３０に導入するようになっている。この導入流路１３４は通常、デファレンシャルキャリア１１２の上方位置に潤滑油Ｌが流下する構造として形成されている。   As shown in FIG. 5, for example, a general-purpose differential device that is conventionally installed in a drive path of a vehicle such as an automobile is configured such that a differential ring gear 114 and a drive pinion 116 are engaged with each other in a differential carrier 112. ing. For example, in a front differential device 110 of a four-wheel drive vehicle, a drive pinion shaft 118 having a drive pinion 116 integrally formed at an end thereof is fitted with a front bearing 126 and a rear bearing 128 that are fitted and arranged on the shaft at an interval in the axial direction. Is supported by the differential carrier 112, and an oil reservoir 130 of a lubricating oil L for lubricating both bearings is formed between the both bearings. Between the oil reservoir 130 formed between the two bearings and the lubricating oil chamber 132 in which the differential ring gear 114 is disposed, an introduction flow path 134 for introducing the lubricating oil L is formed, and the differential ring gear 114. Thus, the lubricating oil L lifted up by the above is introduced into the oil reservoir 130. The introduction flow path 134 is usually formed as a structure in which the lubricating oil L flows down above the differential carrier 112.

このフロント軸受１２６及びリヤ軸受１２８は、円すいころ軸受が使用されることがある。
この円すいころ軸受は、フロント軸受１２６を例にして説明すると、内輪部材１２６ａが、外周面が円すい面状に形成され、この外周面における小径端部側には鍔状の小鍔部１２６ａ−１が、大径端部側には鍔状の大鍔部１２６ａ−２が形成されている。そして、外輪部材１２６ｃが、この内輪部材１２６ａの外周面の円すい面状に対向して、内周面が円すい面状に形成されている。そして、円すいころ１２６ｂが、内輪部材１２６ａと外輪部材１２６ｃの間に挟み込まれた状態で配設可能に円すい状に形成されて複数配列されている。そして、フロント軸受１２６およびリヤ軸受１２８の両軸受共、内輪部材１２６ａ、１２８ａの小径端部側である小鍔部１２６ａ−１、１２８ａ−１側（換言すれば、円すいころ１２６ｂ、１２８ｂの小径部１２６ｂ−１、１２８ｂ−１側）がオイル溜り１３０側となるように配置されている。なお、リヤ軸受１２８もフロント軸受１２６の同じ構成部位には、符号１２８の後にａ、ｂ、ｃの符号を付して示した。
そして、この小鍔部１２６ａ−１、１２８ａ−１側から供給される潤滑油Ｌは、この円すいころ軸受のポンプ作用と呼ばれる油の引き込み現象によって、フロント軸受１２６およびリヤ軸受１２８内に流入し、円すいころ１２６ｂ、１２８ｂの自転及び公転の回転に伴う遠心力で軸受内を流通して内輪部材１２６ａ、１２８ａの大鍔部１２６ａ−２、１２８ａ−２側（換言すれば、円すいころの大径部１２６ｂ−２、１２８ｂ−２側）に排出される。こうして、オイル溜り１３０の潤滑油Ｌは両軸受ともその小鍔部１２６ａ−１、１２８ａ−１側から大鍔部１２６ａ−２、１２８ａ−２側に流通して潤滑が行われる。
通常、四輪駆動の自動車の場合において、このドライブピニオンシャフト１１８に嵌合配置されるフロント軸受１２６及びリヤ軸受１２８の配置関係は、車両進行方向前方位置にデファレンシャルリングギヤ１１４が配設されている。そして、駆動源からの駆動経路の下流側に配置されるのがフロント軸受１２６であり、上流側に配置されるのがリヤ軸受１２８である。すなわち、車両進行方向前方位置に配設されるのがフロント軸受１２６となり、後方位置に配設されるのがリヤ軸受１２８となる。
このような配置関係により、フロント軸受１２６のオイル溜り１３０側と反対側はデファレンシャルリングギヤ１１４が配置される潤滑油室１３２となっている。このためオイル溜り１３０からフロント軸受１２６を潤滑した潤滑油Ｌは潤滑油室１３２に戻る。
また、リヤ軸受１２８のオイル溜り１３０側とは反対側にはオイル戻し溜り１３６が形成されており、オイル溜り１３０からリヤ軸受１２８を潤滑した潤滑油Ｌが貯留されるようになっている。このオイル戻し溜り１３６に貯留された潤滑油Ｌは、ドライブピニオンシャフト１１８の他端に駆動連結状態として取付けられるコンパニオンフランジ１２０のスリーブ１２２に嵌合配設されるオイルシール１３８を潤滑するようになっている。
なお、リヤ軸受１２８のオイル溜り１３０側とは反対側に形成されたオイル戻し溜り１３６と、デファレンシャルリングギヤ１１４が配置された潤滑油室１３２との間には、図示を省略するリターン流路が形成されている。このリターン流路は、リヤ軸受１２８及びオイルシール１３８を潤滑した潤滑油Ｌをオイル戻し溜り１３６から潤滑油室１３２に戻す。 As the front bearing 126 and the rear bearing 128, tapered roller bearings may be used.
In this tapered roller bearing, the front bearing 126 will be described as an example. The inner ring member 126a is formed with a tapered outer peripheral surface, and a flange-shaped small flange portion 126a-1 is formed on the outer diameter side of the outer peripheral surface. However, a bowl-shaped large collar portion 126a-2 is formed on the large-diameter end portion side. The outer ring member 126c is opposed to the conical surface of the outer peripheral surface of the inner ring member 126a, and the inner peripheral surface is formed into a conical surface. A plurality of tapered rollers 126b are formed in a tapered shape so as to be disposed in a state of being sandwiched between the inner ring member 126a and the outer ring member 126c. In addition, both the front bearing 126 and the rear bearing 128 have the small flange portions 126a-1 and 128a-1 side (in other words, the small diameter portions of the tapered rollers 126b and 128b) which are the small diameter end portions of the inner ring members 126a and 128a. 126b-1 and 128b-1 side) are disposed on the oil reservoir 130 side. In the rear bearing 128, the same components of the front bearing 126 are indicated by reference numerals 128, a, b, and c.
Then, the lubricating oil L supplied from the side of the small flange portions 126a-1 and 128a-1 flows into the front bearing 126 and the rear bearing 128 by an oil drawing phenomenon called a pump action of the tapered roller bearing, Circumferential force associated with the rotation of the tapered rollers 126b and 128b and the rotation of the tapered rollers 126b and 128b, and the inner ring members 126a and 128a on the large flange portions 126a-2 and 128a-2 side (in other words, the large diameter portion of the tapered rollers). 126b-2, 128b-2 side). Thus, the lubricating oil L in the oil reservoir 130 is circulated from both the small flange portions 126a-1 and 128a-1 to the large flange portions 126a-2 and 128a-2 and lubricated.
Normally, in the case of a four-wheel drive vehicle, the differential relationship between the front bearing 126 and the rear bearing 128 that are fitted and disposed on the drive pinion shaft 118 is such that a differential ring gear 114 is disposed at a front position in the vehicle traveling direction. The front bearing 126 is disposed on the downstream side of the drive path from the drive source, and the rear bearing 128 is disposed on the upstream side. That is, the front bearing 126 is disposed at the front position in the vehicle traveling direction, and the rear bearing 128 is disposed at the rear position.
Due to such an arrangement relationship, a side of the front bearing 126 opposite to the oil reservoir 130 is a lubricating oil chamber 132 in which the differential ring gear 114 is arranged. Therefore, the lubricating oil L that has lubricated the front bearing 126 from the oil reservoir 130 returns to the lubricating oil chamber 132.
An oil return reservoir 136 is formed on the opposite side of the rear bearing 128 to the oil reservoir 130 side, and the lubricating oil L that lubricates the rear bearing 128 is stored from the oil reservoir 130. The lubricating oil L stored in the oil return reservoir 136 lubricates the oil seal 138 that is fitted and disposed in the sleeve 122 of the companion flange 120 that is attached to the other end of the drive pinion shaft 118 as a drive connection state. ing.
A return flow path (not shown) is formed between the oil return reservoir 136 formed on the opposite side of the oil reservoir 130 of the rear bearing 128 and the lubricating oil chamber 132 in which the differential ring gear 114 is disposed. Has been. The return flow path returns the lubricating oil L that has lubricated the rear bearing 128 and the oil seal 138 from the oil return reservoir 136 to the lubricating oil chamber 132.

上記のように構成されたデファレンシャル装置１１０の潤滑構造によれば、ドライブピニオンシャフト１１８に関係して配設されたフロント軸受１２６、リヤ軸受１２８、及びオイルシール１３８の潤滑は、導入流路１３４を通じて導入される潤滑油Ｌによって行われる。導入流路１３４にはデファレンシャルリングギヤ１１４が配置された潤滑油室１３２の潤滑油Ｌがデファレンシャルリングギヤ１１４の駆動回転により掻き揚げられて、その飛散状態の潤滑油Ｌが導入される。導入流路１３４に導かれた潤滑油Ｌは流下してオイル溜り１３０に導入される。オイル溜り１３０に導入された潤滑油Ｌにより上述した様にフロント軸受１２６、リヤ軸受１２８、及びオイルシール１３８の潤滑を行う。   According to the lubrication structure of the differential device 110 configured as described above, the lubrication of the front bearing 126, the rear bearing 128, and the oil seal 138 disposed in relation to the drive pinion shaft 118 is performed through the introduction flow path 134. This is done with the lubricating oil L introduced. Lubricating oil L in the lubricating oil chamber 132 in which the differential ring gear 114 is arranged is lifted up by the driving rotation of the differential ring gear 114 and the scattered lubricating oil L is introduced into the introduction flow path 134. The lubricating oil L guided to the introduction flow path 134 flows down and is introduced into the oil reservoir 130. As described above, the front bearing 126, the rear bearing 128, and the oil seal 138 are lubricated by the lubricating oil L introduced into the oil reservoir 130.

このフロント軸受１２６及びリヤ軸受１２８を流通する潤滑油Ｌの潤滑状態を良好にするために様々な技術が開示されている。例えば、特許文献１のように、この円すいころ軸受のポンプ作用を利用して、内輪部材の小径端部側である小鍔部側から流入して大径端部側である大鍔部側に排出される潤滑油Ｌを循環させて、再度小鍔部側に送油することによって潤滑油Ｌの潤滑状態を良好にする技術が知られている。また特許文献２のように、円すいころの小径部側の外輪部材の端部に外輪の開口円直径と略等しい内径で軸方向に延びるオイル整流部材を設けたものが知られている。また、特許文献３のように、内輪部材の小径端部側である小鍔部側（円すいころの小径部側）の潤滑油流入口に可撓性のメッシュ部材を配設し、流入する潤滑油Ｌの量を調節するものが知られている。
特開２００３−２０６９３８号公報 特開２００６−２２６３０９号公報 特開２００５−２７３７１６号公報 Various techniques are disclosed in order to improve the lubrication state of the lubricating oil L flowing through the front bearing 126 and the rear bearing 128. For example, as in Patent Document 1, the pump action of this tapered roller bearing is used to flow from the small flange side, which is the small diameter end side of the inner ring member, into the large collar portion side, which is the large diameter end side. A technique for improving the lubrication state of the lubricating oil L by circulating the discharged lubricating oil L and feeding it again to the small collar portion side is known. Further, as disclosed in Patent Document 2, an oil rectifying member that extends in the axial direction with an inner diameter substantially equal to the opening circle diameter of the outer ring is known at the end of the outer ring member on the small diameter side of the tapered roller. Further, as in Patent Document 3, a flexible mesh member is disposed at the lubricating oil inlet of the small flange portion side (small diameter portion side of the tapered roller), which is the small diameter end portion side of the inner ring member. What adjusts the quantity of the oil L is known.
JP 2003-206938 A JP 2006-226309 A JP 2005-273716 A

しかしながら、上気した特許文献１から３に開示された潤滑状態を良好にする技術では、円すいころ軸受内の温度上昇による潤滑油Ｌの潤滑効率の低下を解消することができないという問題がある。この問題について以下に説明する。なお、フロント軸受１２６及びリヤ軸受１２８は同様の構成であるため、フロント軸受１２６を例にして説明する。
すなわち、このフロント軸受１２６の円すいころ１２６ｂがドライブピニオンシャフト１１８の外周面上を転動する際に、円すいころ１２６ｂの外周面と内輪部材１２６ａ及び外輪部材１２６ｃの円すい面が摺動するため摺動摩擦熱が発生するという問題がある。特に、円すいころ１２６ｂの大径部１２６ｂ−２の端面と内輪部材１２６ａの大径端部側である大鍔部１２６ａ−２の接触面において温度が上昇しやすい。
一般的に、潤滑油は、使用温度が高い状態では粘度は低く、使用温度が低い状態では粘度が高いことが知られている。フロント軸受１２６内が高温状態で潤滑油Ｌが流入すると、潤滑油Ｌの粘度が低下する。この潤滑油Ｌの粘度が低い状態では、円すいころ軸受に構成される円すいころ１２６ｂと、内輪部材１２６ａ及び外輪部材１２６ｃの間において潤滑油Ｌの流通が不十分な状態となって金属接触を起こす転動状態となるおそれがあり、異常磨耗や焼きつきが発生しやすくなる。 However, the above-described technology for improving the lubrication state disclosed in Patent Documents 1 to 3 has a problem that the reduction in the lubrication efficiency of the lubricating oil L due to the temperature rise in the tapered roller bearing cannot be solved. This problem will be described below. Since the front bearing 126 and the rear bearing 128 have the same configuration, the front bearing 126 will be described as an example.
That is, when the tapered roller 126b of the front bearing 126 rolls on the outer peripheral surface of the drive pinion shaft 118, the outer peripheral surface of the tapered roller 126b slides on the tapered surfaces of the inner ring member 126a and the outer ring member 126c. There is a problem that heat is generated. In particular, the temperature tends to rise at the contact surface between the end surface of the large diameter portion 126b-2 of the tapered roller 126b and the large collar portion 126a-2 on the large diameter end portion side of the inner ring member 126a.
Generally, it is known that a lubricating oil has a low viscosity at a high use temperature and a high viscosity at a low use temperature. When the lubricating oil L flows in the front bearing 126 at a high temperature, the viscosity of the lubricating oil L decreases. In a state where the viscosity of the lubricating oil L is low, the flow of the lubricating oil L becomes insufficient between the tapered roller 126b configured in the tapered roller bearing and the inner ring member 126a and the outer ring member 126c, thereby causing metal contact. There is a risk of rolling, and abnormal wear and seizure are likely to occur.

ところで、デファレンシャル装置１１０に用いられる潤滑油Ｌの粘度は使用温度によって変化する。例えば、長時間連続運転に伴いデファレンシャル装置１１０内は高温状態となる。このとき、潤滑油Ｌの潤滑効率の低下を抑制するためにブリーザ装置によってデファレンシャル装置内の内圧を抑制したり、オイルクーラーによって潤滑油Ｌを冷却して、デファレンシャルリングギヤ１１４により掻き揚げられて潤滑油オイル溜り１３０に導入される潤滑油Ｌの使用温度状態を適温にすることが図られている。
しかし、潤滑油オイル溜り１３０に導入される潤滑油Ｌの使用温度状態が適温であっても、上記フロント軸受１２６内が摺動摩擦熱に伴って高温状態であると、この軸受内に流入した潤滑油Ｌが高温となり潤滑油Ｌの粘度が低下する。そのため良好な潤滑ができない状態となり、更には、この高温状態の潤滑油Ｌがデファレンシャル装置内を循環して再びフロント軸受１２６内に流入されると、より一層良好な潤滑ができない状態となる。 By the way, the viscosity of the lubricating oil L used in the differential device 110 varies depending on the operating temperature. For example, the inside of the differential device 110 becomes a high temperature state with continuous operation for a long time. At this time, in order to suppress a decrease in the lubrication efficiency of the lubricating oil L, the internal pressure in the differential device is suppressed by the breather device, or the lubricating oil L is cooled by the oil cooler and is swept up by the differential ring gear 114 to be lubricated. The use temperature state of the lubricating oil L introduced into the oil reservoir 130 is set to an appropriate temperature.
However, even if the operating temperature state of the lubricating oil L introduced into the lubricating oil reservoir 130 is an appropriate temperature, if the inside of the front bearing 126 is in a high temperature state due to sliding friction heat, the lubrication that has flowed into the bearing The oil L becomes high temperature and the viscosity of the lubricating oil L decreases. Therefore, it becomes a state where good lubrication cannot be performed, and further, when this high temperature lubricating oil L circulates in the differential device and flows into the front bearing 126 again, even better lubrication cannot be achieved.

更に、四輪駆動車両のフロントデファレンシャル装置１１０においては、デファレンシャルリングギヤ１１４の回転方向は前進時には図５で見て反時計回り方向に回転し、この回転に伴って潤滑油Ｌも反時計回り方向に追従飛散し、導入流路１３４の上方開口から導入されてオイル溜り１３０に流下する構成である。これは、後進時、デファレンシャルリングギヤ１１４の回転方向が時計回り方向に回転する場合の潤滑油Ｌの掻き揚げ量に比べて少ない。そのため、フロント軸受１２６内が摺動摩擦熱に伴って高温状態の場合に、潤滑油Ｌの掻き揚げ量が減少し、フロント軸受１２６への潤滑油Ｌの供給量が不足して潤滑不足となると、軸受内の異常磨耗や焼きつきが、上記問題と相俟ってより発生しやすくなる。そのため、円すいころ軸受において、温度上昇しやすい内輪部材の大径端部側である大鍔部からの放熱性の確保が更に要請されている。
そこで、本発明者は鋭意検討の結果、円すいころ軸受において、温度上昇しやすい内輪部材の大径端部側である大鍔部からの放熱ができれば、円すいころ軸受内に流入した潤滑油の温度上昇を抑制することができ、潤滑性の低下を抑制することができ、異常磨耗、焼きつきの発生を防ぐことができることに着目した。 Further, in the front differential device 110 of a four-wheel drive vehicle, the rotational direction of the differential ring gear 114 rotates counterclockwise as viewed in FIG. 5 when moving forward, and the lubricating oil L also rotates counterclockwise along with this rotation. The structure is such that it follows and scatters, is introduced from the upper opening of the introduction flow path 134 and flows down to the oil reservoir 130. This is less than the amount of the lubricating oil L lifted up when the rotational direction of the differential ring gear 114 rotates clockwise during reverse travel. Therefore, when the inside of the front bearing 126 is in a high temperature state due to sliding frictional heat, the amount of scraping of the lubricating oil L is reduced, and the amount of lubricating oil L supplied to the front bearing 126 is insufficient, resulting in insufficient lubrication. Abnormal wear and seizure in the bearing are more likely to occur in combination with the above problems. For this reason, in the tapered roller bearing, it is further required to ensure heat dissipation from the large collar portion, which is the large diameter end portion side of the inner ring member that is likely to increase in temperature.
Therefore, as a result of intensive studies, the present inventor has determined that the temperature of the lubricating oil flowing into the tapered roller bearing can be reduced if heat can be radiated from the large collar portion on the large diameter end side of the inner ring member that tends to rise in temperature in the tapered roller bearing. The inventors focused on the fact that the increase can be suppressed, the decrease in lubricity can be suppressed, and the occurrence of abnormal wear and seizure can be prevented.

而して、本発明は、このような点に鑑みて創案されたものであり、本発明が解決しようとする課題は、円すいころ軸受において、温度上昇しやすい内輪部材の大径端部側である大鍔部からの放熱を図ることにある。   Thus, the present invention was devised in view of the above points, and the problem to be solved by the present invention is in the tapered roller bearing, on the large-diameter end portion side of the inner ring member that easily rises in temperature. The purpose is to dissipate heat from a certain vase.

上記した課題を達成するために、本発明に係る円すいころ軸受装置は、次の手段をとる。
本発明の第１の発明は、外周面が円すい面状に形成され、該外周面における大径端部側には鍔状の大鍔部が形成された内輪部材と、該内輪部材の外周面の円すい面状に対向して、内周面が円すい面状に形成された外輪部材と、前記内輪部材と前記外輪部材の間に円すいころが複数配列されており、前記円すいころの転動を円滑にする潤滑油が、該内輪部材の小径端部側から流入し、大鍔部側に排出される円すいころ軸受装置であって、前記潤滑油が排出される前記大鍔部側には、該潤滑油を貯留可能な潤滑油貯留部が形成されており、前記内輪部材の大鍔部に、環状に形成された冷却部材が接触可能に配設されており、該冷却部材の外周形状の配設位置は、少なくともその外周端部が前記潤滑油貯留部に貯留した潤滑油に接触可能な位置とされていることを特徴とする。 In order to achieve the above-described problems, the tapered roller bearing device according to the present invention takes the following means.
According to a first aspect of the present invention, there is provided an inner ring member having an outer peripheral surface formed in a conical surface shape, and a flange-shaped large collar portion formed on a large diameter end portion side of the outer peripheral surface, and an outer peripheral surface of the inner ring member A plurality of tapered rollers arranged between the inner ring member and the outer ring member, the rolling of the tapered rollers. In the tapered roller bearing device in which the lubricating oil to be smoothed flows in from the small diameter end side of the inner ring member and is discharged to the large collar part side, on the large collar part side from which the lubricating oil is discharged, A lubricating oil storage portion capable of storing the lubricating oil is formed, and a cooling member formed in an annular shape is disposed on the large collar portion of the inner ring member so as to be in contact with the outer peripheral shape of the cooling member. The disposition position is a position where at least the outer peripheral end can contact the lubricant stored in the lubricant storage section. And wherein the are.

この第１の発明によれば、潤滑油が排出される大鍔部側には、潤滑油を貯留可能な潤滑油貯留部が形成されている。そして、環状に形成された冷却部材が内輪部材の大鍔部に接触可能に配設されている。この冷却部材の外周形状の配設位置は、少なくともその外周端部が潤滑油貯留部に貯留した潤滑油に接触可能な位置とされている。
すなわち、温度上昇しやすい内輪部材の大鍔部の摺動摩擦熱が、冷却部材を介して潤滑油貯留部に貯留した潤滑油に放熱させることができる。そのため、内輪部材の大鍔部の温度上昇が抑制されるため軸受内に流入した潤滑油の温度上昇を抑制することができ、潤滑性の低下を抑制することができる。 According to the first aspect of the present invention, the lubricating oil reservoir that can store the lubricating oil is formed on the large collar portion side from which the lubricating oil is discharged. An annularly formed cooling member is disposed so as to be in contact with the large collar portion of the inner ring member. The arrangement position of the outer peripheral shape of the cooling member is a position where at least the outer peripheral end of the cooling member can contact the lubricant stored in the lubricant storage section.
That is, the sliding frictional heat of the large collar portion of the inner ring member that easily rises in temperature can be radiated to the lubricating oil stored in the lubricating oil storage portion via the cooling member. Therefore, since the temperature rise of the large collar part of the inner ring member is suppressed, the temperature rise of the lubricating oil flowing into the bearing can be suppressed, and the deterioration of lubricity can be suppressed.

本発明の第２の発明は、前記冷却部材の配設位置は、前記内輪部材の大鍔部の端面又は外周面の少なくとも一方に接触可能な位置とされていることを特徴とする。   According to a second aspect of the present invention, the cooling member is disposed at a position where it can contact at least one of an end surface or an outer peripheral surface of the large collar portion of the inner ring member.

この第２の発明によれば、環状に形成された冷却部材は、大鍔部に接触可能に配設される位置として、大鍔部の端面又は外周面の少なくとも一方において接触可能な位置とされている。これにより、冷却部材を環状に形成する際の加工は複雑になることがない。また、冷却部材を配設することに伴い、軸受を支持する支持部材側の加工が必要となる場合でも、この支持部材側の加工が複雑にならない。すなわち、加工の容易性を図りつつ、冷却部材を内輪部材の大鍔部に接触可能に配設することができる。   According to the second aspect of the present invention, the annularly formed cooling member is a position at which at least one of the end surface or the outer peripheral surface of the large collar portion can be contacted as a position at which the cooling member is arranged to be able to contact the large collar portion. ing. Thereby, the process at the time of forming an annular cooling member does not become complicated. In addition, when the cooling member is provided, the processing on the support member side is not complicated even when the processing on the support member side that supports the bearing is required. That is, the cooling member can be disposed so as to be able to contact the large collar portion of the inner ring member while facilitating processing.

本発明の第３の発明は、前記冷却部材は、放熱性の良好な金属で形成されていることを特徴とする。   A third aspect of the present invention is characterized in that the cooling member is formed of a metal having good heat dissipation.

この第３の発明によれば、冷却部材は、放熱性の良好な金属で形成されている。これにより、円すいころ軸受において、温度上昇しやすい内輪部材の大鍔部の放熱をより一層向上させることができる。   According to the third aspect of the invention, the cooling member is made of a metal with good heat dissipation. Thereby, in the tapered roller bearing, it is possible to further improve the heat radiation of the large collar portion of the inner ring member that easily rises in temperature.

本発明の第４の発明は、前記冷却部材の形状は、前記潤滑油貯留部に貯留した潤滑油に接触可能な部位の形状が凹凸形状で形成されていることを特徴とする。   According to a fourth aspect of the present invention, the shape of the cooling member is such that the shape of the portion that can contact the lubricating oil stored in the lubricating oil reservoir is formed in an uneven shape.

この第４の発明によれば、冷却部材の形状は、潤滑油貯留部に貯留した潤滑油に接触可能な部位の形状が凹凸形状で形成されている。これにより、冷却部材は、潤滑油貯留部に貯留した潤滑油と接触する面積が大きい形状で形成されるためより一層効率的に、潤滑油への放熱を行うことができる。   According to the fourth aspect of the present invention, the shape of the cooling member is such that the shape of the portion that can come into contact with the lubricating oil stored in the lubricating oil reservoir is an uneven shape. Thereby, since the cooling member is formed in a shape having a large area in contact with the lubricating oil stored in the lubricating oil storage part, heat can be radiated to the lubricating oil more efficiently.

本発明は上記各発明の手段をとることにより次の効果を得ることができる。
先ず、上記第１の発明の円すいころ軸受装置によれば、温度上昇しやすい内輪部材の大鍔部の摺動摩擦熱が、冷却部材を介して潤滑油貯留部に貯留した潤滑油に放熱させることができる。そのため、内輪部材の大鍔部の温度上昇が抑制されるため軸受内に流入した潤滑油の温度上昇を抑制することができ、潤滑性の低下を抑制することができる。
次に、上記第２の発明の円すいころ軸受装置によれば、冷却部材の加工の容易性を図りつつ、冷却部材を内輪部材の大鍔部に接触可能に配設することができる。
次に、上記第３の発明の円すいころ軸受装置によれば、円すいころ軸受において、温度上昇しやすい内輪部材の大鍔部の放熱をより一層向上させることができる。
次に、上記第４の発明の円すいころ軸受装置によれば、冷却部材は、潤滑油貯留部に貯留した潤滑油と接触する面積が大きい形状で形成されるためより一層効率的に、潤滑油への放熱を行うことができる。 The present invention can obtain the following effects by taking the measures of the above inventions.
First, according to the tapered roller bearing device according to the first aspect of the present invention, the sliding frictional heat of the large collar portion of the inner ring member that easily rises in temperature is dissipated to the lubricating oil stored in the lubricating oil reservoir through the cooling member. Can do. Therefore, since the temperature rise of the large collar part of the inner ring member is suppressed, the temperature rise of the lubricating oil flowing into the bearing can be suppressed, and the deterioration of lubricity can be suppressed.
Next, according to the tapered roller bearing device of the second invention, the cooling member can be disposed so as to be able to contact the large collar portion of the inner ring member while facilitating the processing of the cooling member.
Next, according to the tapered roller bearing device of the third aspect of the present invention, in the tapered roller bearing, it is possible to further improve the heat radiation of the large collar portion of the inner ring member that easily rises in temperature.
Next, according to the tapered roller bearing device of the fourth aspect of the invention, the cooling member is formed in a shape having a large area in contact with the lubricating oil stored in the lubricating oil storage portion, so that the lubricating oil is more efficiently used. Can be dissipated.

以下に、本発明を実施するための最良の形態の一実施例を、図面を用いて説明する。この実施例は、四輪駆動の駆動形態自動車に適用されたデファレンシャル装置のフロントデファレンシャル装置を例にして説明する。図１は、本発明の一実施例として、デファレンシャル装置の全体構成を概略的に示した断面図である。図１において、デファレンシャルリングギヤ１４には差動機構が装備されているが図示を省略している。なお、図１において矢印Ｆ方向は自動車の前進時における進行方向を示している。   Hereinafter, an embodiment of the best mode for carrying out the present invention will be described with reference to the drawings. In this embodiment, a front differential device of a differential device applied to a four-wheel drive type automobile will be described as an example. FIG. 1 is a cross-sectional view schematically showing the overall configuration of a differential apparatus as an embodiment of the present invention. In FIG. 1, the differential ring gear 14 is equipped with a differential mechanism, but the illustration is omitted. In addition, the arrow F direction in FIG. 1 has shown the advancing direction at the time of advance of a motor vehicle.

図１に示すように、本実施例のデファレンシャル装置１０は、デファレンシャルキャリア１２内にデファレンシャルリングギヤ１４とドライブピニオン１６が噛合して配置されて構成されている。ドライブピニオン１６はドライブピニオンシャフト１８の図１で見て左端に一体的に形成されている。ドライブピニオンシャフト１８の図１で見て右端はコンパニオンフランジ２０のスリーブ２２がナット２４により締め付けられて回転連結されている。コンパニオンフランジ２０は不図示の継手やプロペラシャフトを介してフロントエンジンに駆動連結されており、フロントエンジンの駆動力が伝達されてくるようになっている。なお、デファレンシャルリングギヤ１４には不図示の差動機構が装備されており、差動機構から左右の車輪に動力が伝達されるようになっている。   As shown in FIG. 1, the differential apparatus 10 according to the present embodiment is configured by a differential ring gear 14 and a drive pinion 16 being arranged in a differential carrier 12. The drive pinion 16 is formed integrally with the left end of the drive pinion shaft 18 as viewed in FIG. The right end of the drive pinion shaft 18 as viewed in FIG. 1 is rotationally connected to a sleeve 22 of a companion flange 20 that is fastened by a nut 24. The companion flange 20 is drivingly connected to the front engine via a joint and a propeller shaft (not shown) so that the driving force of the front engine is transmitted. The differential ring gear 14 is equipped with a differential mechanism (not shown) so that power is transmitted from the differential mechanism to the left and right wheels.

ドライブピニオンシャフト１８はフロント軸受２６及びリヤ軸受２８によりデファレンシャルキャリア１２に支持されている。このフロント軸受２６及びリヤ軸受２８は共に円すいころ軸受として形成されている。
フロント軸受２６は、概略、内輪部材２６ａ、円すいころ２６ｂ、外輪部材２６ｃ、保持器２６ｄから構成されている。
この内輪部材２６ａは、外周面が円すい面状に形成され、該外周面における小径端部側には鍔状の小鍔部２６ａ−１が、大径端部側には鍔状の大鍔部２６ａ−２が形成されている。外輪部材２６ｃは、内輪部材２６ａの外周面の円すい面状に対向して、内周面が円すい面状に形成されている。円すいころ２６ｂは、内輪部材２６ａと外輪部材２６ｃの間に挟み込まれた状態で配設可能な円すい状に形成されており、小径に形成された小径部２６ｂ−１と大径に形成された大径部２６ｂ−２が形成されている。この円すいころ２６ｂは、保持器２６ｄに保持された状態で内輪部材２６ａと外輪部材２６ｃの間に挟みこまれて複数配列されており、ドライブピニオンシャフト１８の外周面上を自転かつ公転可能とされている。保持器２６ｄは、円すいころ２６ｂが内輪部材２６ａと外輪部材２６ｃの間の円すい面上を自転かつ公転可能な状態で保持するものである。 The drive pinion shaft 18 is supported on the differential carrier 12 by a front bearing 26 and a rear bearing 28. Both the front bearing 26 and the rear bearing 28 are formed as tapered roller bearings.
The front bearing 26 is roughly constituted by an inner ring member 26a, a tapered roller 26b, an outer ring member 26c, and a cage 26d.
The inner ring member 26a has an outer peripheral surface formed in a conical shape, and a flange-shaped small flange portion 26a-1 is formed on the small-diameter end portion side of the outer peripheral surface, and a flange-shaped large flange portion is formed on the large-diameter end portion side. 26a-2 is formed. The outer ring member 26c is opposed to the conical surface of the outer peripheral surface of the inner ring member 26a, and the inner peripheral surface is formed into a conical surface. The tapered roller 26b is formed in a conical shape that can be disposed in a state of being sandwiched between the inner ring member 26a and the outer ring member 26c, and has a small diameter portion 26b-1 formed in a small diameter and a large diameter formed in a large diameter. A diameter portion 26b-2 is formed. A plurality of the tapered rollers 26b are sandwiched between the inner ring member 26a and the outer ring member 26c while being held by the cage 26d, and can rotate and revolve on the outer peripheral surface of the drive pinion shaft 18. ing. The retainer 26d holds the tapered roller 26b on the conical surface between the inner ring member 26a and the outer ring member 26c in a state where it can rotate and revolve.

リヤ軸受２８は、概略、内輪部材２８ａ、円すいころ２８ｂ、外輪部材２８ｃ、保持器２８ｄから構成されている。
この内輪部材２８ａは、外周面が円すい面状に形成され、該外周面における小径端部側には鍔状の小鍔部２８ａ−１が、大径端部側には鍔状の大鍔部２８ａ−２が形成されている。外輪部材２８ｃは、内輪部材２８ａの外周面の円すい面状に対向して、内周面が円すい面状に形成されている。円すいころ２８ｂは、内輪部材２８ａと外輪部材２８ｃの間に挟み込まれた状態で配設可能な円すい状に形成されており、小径に形成された小径部２８ｂ−１と大径に形成された大径部２８ｂ−２が形成されている。この円すいころ２８ｂは、保持器２８ｄに保持された状態で内輪部材２８ａと外輪部材２８ｃの間に挟みこまれて複数配列されており、ドライブピニオンシャフト１８の外周面上を自転かつ公転可能とされている。保持器２８ｄは、円すいころ２８ｂが内輪部材２８ａと外輪部材２８ｃの間の円すい面上を自転かつ公転可能な状態で保持するものである。 The rear bearing 28 is generally composed of an inner ring member 28a, a tapered roller 28b, an outer ring member 28c, and a cage 28d.
The inner ring member 28a has an outer peripheral surface formed in a conical shape, and a flange-shaped small flange portion 28a-1 is formed on the small-diameter end portion side of the outer peripheral surface, and a flange-shaped large flange portion is formed on the large-diameter end portion side. 28a-2 is formed. The outer ring member 28c is opposed to the conical surface of the outer peripheral surface of the inner ring member 28a, and the inner peripheral surface is formed into a conical surface. The tapered roller 28b is formed in a tapered shape that can be disposed in a state of being sandwiched between the inner ring member 28a and the outer ring member 28c, and has a small diameter portion 28b-1 formed in a small diameter and a large diameter formed in a large diameter. A diameter portion 28b-2 is formed. A plurality of the tapered rollers 28b are sandwiched between the inner ring member 28a and the outer ring member 28c while being held by the cage 28d, and can rotate and revolve on the outer peripheral surface of the drive pinion shaft 18. ing. The retainer 28d holds the tapered roller 28b on the conical surface between the inner ring member 28a and the outer ring member 28c in a state where it can rotate and revolve.

上記フロント軸受２６及びリヤ軸受２８は、ドライブピニオンシャフト１８に軸方向に間隔を置いて配置されており、その内輪部材２６ａ、２８ａがドライブピニオンシャフト１８に嵌合した状態で配置されている。フロント軸受２６は図１で見てドライブピニオン１６に隣接して配置されており、リヤ軸受２８は図１で見てコンパニオンフランジ２０のスリーブ２２に隣接して配置されている。すなわち、駆動経路の上流側に配設されるのがリヤ軸受２８であり、下流側に配設されるのがフロント軸受２６となっている。また、内輪部材２６ａの小径端部側である小鍔部２６ａ−１と、内輪部材２８ａの小径端部側である小鍔部２８ａ−１が対向した状態として配置されている。この状態は、換言すれば、円すいころ２６ｂの小径部２６ｂ−１と、円すいころ２８ｂの小径部２８ｂ−１が対向した配置状態である。   The front bearing 26 and the rear bearing 28 are arranged on the drive pinion shaft 18 at an interval in the axial direction, and the inner ring members 26 a and 28 a are arranged in a state of being fitted to the drive pinion shaft 18. The front bearing 26 is disposed adjacent to the drive pinion 16 as viewed in FIG. 1, and the rear bearing 28 is disposed adjacent to the sleeve 22 of the companion flange 20 as viewed in FIG. That is, the rear bearing 28 is disposed on the upstream side of the drive path, and the front bearing 26 is disposed on the downstream side. Moreover, the small collar part 26a-1 which is the small diameter edge part side of the inner ring member 26a and the small collar part 28a-1 which is the small diameter edge part side of the inner ring member 28a are arranged in a state of facing each other. In other words, this state is an arrangement state in which the small diameter portion 26b-1 of the tapered roller 26b and the small diameter portion 28b-1 of the tapered roller 28b face each other.

軸方向に間隔を置いて配置されたフロント軸受２６とリヤ軸受２８との間のデファレンシャルキャリア１２の箇所は、該両軸受２６、２８に潤滑油Ｌを供給するオイル溜り３０として形成されている。デファレンシャル装置１０における潤滑油Ｌの主たるオイル貯留はデファレンシャルリングギヤ１４が配置されている潤滑油室３２で行われる。潤滑油室３２内の潤滑油Ｌは、デファレンシャルリングギヤ１４がドライブシャフト１３を中心に回転することにより攪拌されて、潤滑油室３２内に飛散状態となり、攪拌により上方に掻き揚げられた潤滑油Ｌがデファレンシャルキャリア１２の上方に形成した導入流路３４を通ってオイル溜り３０に導入される。導入流路３４は潤滑油室３２の上方とオイル溜り３０の上方とを連通する状態として形成されており、導入流路３４に導入されてきた潤滑油Ｌが自重で流下可能な形状として形成されている。この実施例の場合は、オイル溜り３０に対して下降傾斜する形状として形成されている。
図１で見て、デファレンシャルリングギヤ１４の回転方向は前進時には図１で見て反時計回り方向に回転しており、その回転に伴って潤滑油Ｌも反時計回り方向に追従飛散し、導入流路３４の上方開口から導入されてオイル溜り３０に流下していくようになっている。 A portion of the differential carrier 12 between the front bearing 26 and the rear bearing 28 that are spaced apart in the axial direction is formed as an oil reservoir 30 that supplies the lubricating oil L to the bearings 26 and 28. The main oil storage of the lubricating oil L in the differential device 10 is performed in the lubricating oil chamber 32 in which the differential ring gear 14 is disposed. The lubricating oil L in the lubricating oil chamber 32 is agitated by the differential ring gear 14 rotating around the drive shaft 13, is scattered in the lubricating oil chamber 32, and is swept upward by the agitation. Is introduced into the oil reservoir 30 through the introduction flow path 34 formed above the differential carrier 12. The introduction channel 34 is formed in a state where the upper part of the lubricating oil chamber 32 and the upper part of the oil reservoir 30 are communicated with each other, and is formed in a shape that allows the lubricating oil L introduced into the introduction channel 34 to flow down by its own weight. ing. In the case of this embodiment, it is formed in a shape that is inclined downward with respect to the oil reservoir 30.
As seen in FIG. 1, the rotational direction of the differential ring gear 14 is rotating in the counterclockwise direction as seen in FIG. 1 when moving forward, and along with this rotation, the lubricating oil L also follows and scatters in the counterclockwise direction. The oil is introduced from the upper opening of the passage 34 and flows down to the oil reservoir 30.

オイル溜り３０に導入された潤滑油Ｌにより、その両側に配置されたフロント軸受２６及びリヤ軸受２８を潤滑する。その潤滑は、フロント軸受２６は、内輪部材２６ａの小径端部側である小鍔部２６ａ−１側から大径端部側である大鍔部２６ａ−２側方向に潤滑油Ｌが流通して潤滑する。同じく、リヤ軸受２８は、内輪部材２８ａの小径端部側である小鍔部２８ａ−１側から大径端部側である大鍔部２８ａ−２側方向に潤滑油Ｌが流通して潤滑する。
これを換言すれば、フロント軸受２６は、円すいころ２６ｂの小径部２６ｂ−１側から大径部２６ｂ−２側方向に潤滑油Ｌが流通して潤滑する。同じく、リヤ軸受２８は、円すいころ２８ｂの小径部２８ｂ−１側から大径部２８ｂ−２側方向に潤滑油Ｌが流通して潤滑する。
フロント軸受２６及びリヤ軸受２８の内輪部材２６ａ、２８ａの小径端部側である小鍔部２６ａ−１、２８ａ−１側からの潤滑油Ｌの流通は、この円すいころ軸受のポンプ作用と呼ばれる油の引き込み現象によって行われる。すなわち、軸受内に流入した潤滑油Ｌは、円すいころの自転及び公転の回転に伴う遠心力で軸受内を流通して大鍔部２６ａ−２、２８ａ−２側に排出される。こうして、オイル溜り３０の潤滑油Ｌは、フロント軸受２６及びリヤ軸受２８の内輪部材２６ａ、２８ａの小径端部側である小鍔部２６ａ−１、２８ａ−１側から大径端部側である大鍔部２６ａ−２、２８ａ−２側に流通して潤滑が行われる。 The front bearing 26 and the rear bearing 28 disposed on both sides thereof are lubricated by the lubricating oil L introduced into the oil reservoir 30. In the front bearing 26, the lubricating oil L flows from the small flange portion 26a-1 side which is the small diameter end portion side of the inner ring member 26a to the large flange portion 26a-2 side which is the large diameter end portion side. Lubricate. Similarly, in the rear bearing 28, the lubricating oil L flows and lubricates from the small flange portion 28a-1 side which is the small diameter end portion side of the inner ring member 28a to the large flange portion 28a-2 side which is the large diameter end portion side. .
In other words, the lubricating oil L flows and lubricates the front bearing 26 from the small diameter portion 26b-1 side to the large diameter portion 26b-2 side of the tapered roller 26b. Similarly, in the rear bearing 28, the lubricating oil L flows and lubricates from the small diameter portion 28b-1 side to the large diameter portion 28b-2 side of the tapered roller 28b.
The flow of the lubricating oil L from the small flange portions 26a-1 and 28a-1 side which are the small diameter end portions of the inner ring members 26a and 28a of the front bearing 26 and the rear bearing 28 is an oil called a pump action of the tapered roller bearing. This is done by the pulling phenomenon. That is, the lubricating oil L that has flowed into the bearing flows through the bearing by the centrifugal force associated with the rotation and revolution of the tapered rollers, and is discharged to the large collar portions 26a-2 and 28a-2. Thus, the lubricating oil L in the oil reservoir 30 is on the large diameter end portion side from the small flange portions 26a-1 and 28a-1 side which are the small diameter end portions side of the inner ring members 26a and 28a of the front bearing 26 and the rear bearing 28. Lubricating is performed by flowing to the large collar portions 26a-2 and 28a-2.

そして、フロント軸受２６を潤滑した潤滑油Ｌは、その内輪部材２６ａの大径端部側である大鍔部２６ａ−２側（換言すれば、円すいころ２６ｂの大径部２６ｂ−２側）から潤滑油室３２に戻る。リヤ軸受２８を潤滑した潤滑油Ｌは、その内輪部材２８ａの大径端部側である大鍔部２８ａ−２側（換言すれば、円すいころ２８ｂの大径部２８ｂ−２側）からオイル戻し溜り３６に排出する。なお、本実施例における潤滑油室３２及びオイル戻し溜り３６が本発明の「潤滑油貯留部」に相当する。
オイル戻し溜り３６はリヤ軸受２８から排出した潤滑油Ｌによりオイルシール３８を潤滑するための役割を果たすとともに、デファレンシャル装置１０の始動時で、導入流路３４から導入される潤滑油量が少なくオイル溜り３０の潤滑油残存量が少ないときにリヤ軸受を潤滑するためのものである。オイルシール３８は図１で見てオイル戻し溜り３６の後方位置に配置されており、コンパニオンフランジ２０のスリーブ２２に嵌合状態で配設されており、その外径部がデファレンシャルキャリア１２に固定支持されている。したがって、オイルシール３８の内径部がスリーブ２２に回転可能状態にシール密接しており、このシール部分の潤滑が必要なものである。
オイル戻し溜り３６と潤滑油室３２との間は、図示を省略するリターン流路により流路連結されており、オイル戻し溜り３６に滞留する潤滑油Ｌを潤滑油室３２に戻すようになっている。リターン流路（図示省略）はデファレンシャルキャリア１２の最下方位置に形成されており、オイル戻し溜り３６に滞留する潤滑油Ｌを良好に戻すようになっている。 And the lubricating oil L which lubricated the front bearing 26 is from the large collar part 26a-2 side (in other words, the large diameter part 26b-2 side of the tapered roller 26b) which is the large diameter end part side of the inner ring member 26a. Return to the lubricating oil chamber 32. The lubricating oil L that has lubricated the rear bearing 28 is returned from the large collar portion 28a-2 side (in other words, the large diameter portion 28b-2 side of the tapered roller 28b), which is the large diameter end portion side of the inner ring member 28a. Drain into the reservoir 36. In this embodiment, the lubricating oil chamber 32 and the oil return reservoir 36 correspond to the “lubricating oil reservoir” of the present invention.
The oil return reservoir 36 serves to lubricate the oil seal 38 with the lubricating oil L discharged from the rear bearing 28, and the amount of lubricating oil introduced from the introduction passage 34 is small when the differential device 10 is started. This is for lubricating the rear bearing when the residual amount of lubricating oil in the reservoir 30 is small. The oil seal 38 is disposed at the rear position of the oil return reservoir 36 as viewed in FIG. 1, and is fitted in the sleeve 22 of the companion flange 20, and its outer diameter portion is fixedly supported by the differential carrier 12. Has been. Therefore, the inner diameter portion of the oil seal 38 is in close contact with the sleeve 22 in a rotatable state, and the seal portion needs to be lubricated.
The oil return reservoir 36 and the lubricating oil chamber 32 are connected by a return flow path (not shown) so that the lubricating oil L staying in the oil return reservoir 36 is returned to the lubricating oil chamber 32. Yes. A return flow path (not shown) is formed at the lowermost position of the differential carrier 12 so that the lubricating oil L staying in the oil return reservoir 36 can be satisfactorily returned.

次に、フロント軸受２６及びリヤ軸受２８において、潤滑油貯留部（潤滑油室３２及びオイル戻し溜り３６）側に配設される、温度上昇しやすい内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２側を放熱させる冷却部材２７、２９の構造について説明する。
図２は、ドライブピニオンシャフト１８を支持するフロント軸受２６及びリヤ軸受２８の部位を拡大した断面図である。また、図３は、ドライブピニオンシャフト１８を支持するリヤ軸受２８の構成を示した分解斜視図である。図４は、ドライブピニオンシャフト１８を支持するリヤ軸受２８の内輪部材２８ａの大径端部側である大鍔部２８ａ−２側における冷却部材２９の斜視図である。なお、図３において、フロント軸受２６及びリヤ軸受２８において、共に同様の構成であるため、代表としてリヤ軸受２８の構成について示している。また、内部の構成を分かり易く図示するために一部切断した状態で図示されている。また、図４において、冷却部材は、フロント軸受２６及びリヤ軸受２８において、共に同様の構成であるため、代表してリヤ軸受２８における冷却部材２９について示しており、リヤ軸受２８の図示は省略している。また、フロント軸受２６及びこの冷却部材２７の図示を省略している。 Next, in the front bearing 26 and the rear bearing 28, on the side of the large diameter end of the inner ring members 26a and 28a, which are disposed on the side of the lubricating oil reservoir (the lubricating oil chamber 32 and the oil return reservoir 36) and easily rise in temperature. The structure of the cooling members 27 and 29 that dissipate heat from the large collar portions 26a-2 and 28a-2 will be described.
FIG. 2 is an enlarged cross-sectional view of the front bearing 26 and the rear bearing 28 that support the drive pinion shaft 18. FIG. 3 is an exploded perspective view showing the configuration of the rear bearing 28 that supports the drive pinion shaft 18. FIG. 4 is a perspective view of the cooling member 29 on the large flange portion 28a-2 side, which is the large diameter end portion side of the inner ring member 28a of the rear bearing 28 that supports the drive pinion shaft 18. As shown in FIG. In FIG. 3, since both the front bearing 26 and the rear bearing 28 have the same configuration, the configuration of the rear bearing 28 is shown as a representative. Also, the internal configuration is shown in a partially cut state for easy understanding. In FIG. 4, since the cooling member has the same configuration in both the front bearing 26 and the rear bearing 28, the cooling member 29 in the rear bearing 28 is representatively shown, and the illustration of the rear bearing 28 is omitted. ing. Further, illustration of the front bearing 26 and the cooling member 27 is omitted.

図２に図示されるように、潤滑油貯留部としての潤滑油室３２は、フロント軸受２６を潤滑した潤滑油Ｌが排出される内輪部材２６ａの大径端部側である大鍔部２６ａ−２側（換言すれば、円すいころ２６ｂの大径部２６ｂ−２側）に形成されている。また、潤滑油貯留部としてのオイル戻し溜り３６は、リヤ軸受２８を潤滑した潤滑油Ｌが排出される内輪部材２８ａの大径端部側である大鍔部２８ａ−２側（換言すれば、円すいころ２８ｂの大径部２８ｂ−２側）に形成されている。
そして、潤滑油室３２、オイル戻し溜り３６には、共に軸受内を流通した潤滑油Ｌが貯留されている。 As shown in FIG. 2, the lubricating oil chamber 32 serving as a lubricating oil reservoir is a large collar portion 26 a-that is the large diameter end portion side of the inner ring member 26 a from which the lubricating oil L that has lubricated the front bearing 26 is discharged. It is formed on the second side (in other words, on the large diameter portion 26b-2 side of the tapered roller 26b). In addition, the oil return reservoir 36 as the lubricating oil reservoir is a large collar portion 28a-2 side (in other words, the large diameter end portion side of the inner ring member 28a from which the lubricating oil L that lubricated the rear bearing 28 is discharged) It is formed on the large diameter portion 28b-2 side of the tapered roller 28b.
The lubricating oil chamber 32 and the oil return reservoir 36 store the lubricating oil L that has circulated in the bearing.

このフロント軸受２６及びリヤ軸受２８の内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２には、環状に形成された冷却部材２７、２９が大鍔部２６ａ−２、２８ａ−２に接触可能に配設されている。この冷却部材２７、２９の大鍔部２６ａ−２、２８ａ−２への接触構成について図３、図４を用いて示す。なお、フロント軸受２６及びリヤ軸受２８において、共に同様の構成であるため代表としてリヤ軸受２８の構成について示す。
図３に図示されるように、冷却部材２９は、円板形状に形成されており、中心部に貫通孔２９ａが形成された環状のものである。そして、内周面が内輪部材２８ａの大径端部側である大鍔部２８ａ−２の径方向外方端の外周面２８ａ−３と略同一直径に形成されている。そして、大鍔部２８ａ−２の外周面２８ａ−３に圧入して嵌め込まれて固定支持されている。これにより、冷却部材２９は、内輪部材２８ａの大鍔部２８ａ−２に熱伝達可能な構成状態として接触可能に配設されている。なお、本実施例における外周面２８ａ−３が本発明の「外周面」に相当する。 On the large flange portions 26a-2 and 28a-2 which are the large diameter end portions of the inner ring members 26a and 28a of the front bearing 26 and the rear bearing 28, annularly formed cooling members 27 and 29 are formed as large flange portions 26a. -2, 28a-2. A contact configuration of the cooling members 27 and 29 with the large collar portions 26a-2 and 28a-2 will be described with reference to FIGS. Since the front bearing 26 and the rear bearing 28 have the same configuration, the configuration of the rear bearing 28 is shown as a representative.
As shown in FIG. 3, the cooling member 29 is formed in a disc shape, and has an annular shape in which a through hole 29 a is formed at the center. The inner peripheral surface is formed to have substantially the same diameter as the outer peripheral surface 28a-3 at the radially outer end of the large collar portion 28a-2 which is the large diameter end portion side of the inner ring member 28a. And it is press-fitted into the outer peripheral surface 28a-3 of the large collar portion 28a-2 and is fixedly supported. Thereby, the cooling member 29 is arrange | positioned so that contact is possible as a structure state which can be heat-transferred to the large collar part 28a-2 of the inner ring member 28a. In addition, the outer peripheral surface 28a-3 in a present Example corresponds to the "outer peripheral surface" of this invention.

また、図３において、冷却部材２９の内周面が、大鍔部２８ａ−２の外周面２８ａ−３に圧入して嵌め込まれることにより、冷却部材２９が大鍔部２８ａ−２に接触可能に配設されている構成について示した。この構成以外に次の構成でもよい。すなわち、冷却部材２９の内周面がドライブピニオンシャフト１８（図１参照）又は、コンパニオンフランジ２０のスリーブ２２（図１参照）と略同一直径に形成されて、ドライブピニオンシャフト１８又は、コンパニオンフランジ２０のスリーブ２２に挿入して嵌め込まれて固定支持される構成である。この構成によって冷却部材２９は、内輪部材２８ａの大径端部側である大鍔部２８ａ−２の軸方向の端部の端面２８ａ−４に接触可能に配設される。なお、本実施例における端面２８ａ−４が本発明の「端面」に相当する。   Further, in FIG. 3, the cooling member 29 can come into contact with the large collar part 28a-2 by press-fitting the inner circumferential surface of the cooling member 29 into the outer circumferential surface 28a-3 of the large collar part 28a-2. The arrangement is shown. In addition to this configuration, the following configuration may be used. That is, the inner peripheral surface of the cooling member 29 is formed to have substantially the same diameter as the drive pinion shaft 18 (see FIG. 1) or the sleeve 22 (see FIG. 1) of the companion flange 20, and the drive pinion shaft 18 or the companion flange 20 It is the structure which is inserted and inserted into the sleeve 22 and fixedly supported. With this configuration, the cooling member 29 is disposed so as to be able to contact the end surface 28a-4 of the end portion in the axial direction of the large collar portion 28a-2 which is the large diameter end portion side of the inner ring member 28a. In addition, the end surface 28a-4 in a present Example is equivalent to the "end surface" of this invention.

図３及び図４に図示されるように、この冷却部材２９の外周形状は、凹凸形状に形成されている。図３に図示されるように、詳細には、冷却部材２９の外周形状は、冷却部材２９の中心部から外方に向かって放射状に凸部２９ｂが複数配列されており、３層に構成されて、一体に形成された凹凸形状のものである。図４（Ａ）に図示されたものがこの構成のものである。これにより、潤滑油Ｌとの接触面積を大きくすることができる。またこれ以外の形状として、図４（Ｂ）に図示されるように、冷却部材２９の外周形状は潤滑油Ｌとの接触面積を大きくする構成であれば良い。例えば、一層形状の略スリット構造に形成されたものでも良い。また、この一層形状のものを複数重ねて構成されたものでも良い。
また、冷却部材２９は、放熱性の良好な金属で形成されている。換言すれば、熱伝導性の高い金属で形成されている。この放熱性の良好な金属は、銅、アルミニウム等である。 As shown in FIGS. 3 and 4, the outer peripheral shape of the cooling member 29 is formed in an uneven shape. As shown in FIG. 3, in detail, the outer peripheral shape of the cooling member 29 includes a plurality of convex portions 29 b arranged radially from the center of the cooling member 29 to the outside, and is configured in three layers. Thus, it is an integrally formed uneven shape. The configuration shown in FIG. 4A is that of this configuration. Thereby, a contact area with the lubricating oil L can be enlarged. As other shapes, as shown in FIG. 4B, the outer peripheral shape of the cooling member 29 may be configured to increase the contact area with the lubricating oil L. For example, it may be formed in a one-layer substantially slit structure. Further, a structure in which a plurality of the single-layer shapes are stacked may be used.
The cooling member 29 is made of a metal with good heat dissipation. In other words, it is made of a metal having high thermal conductivity. The metal with good heat dissipation is copper, aluminum or the like.

図２に図示されるように、冷却部材２９の外周形状の配設位置は、凸部２９ｂが潤滑油貯留部として構成されているオイル戻し溜り３６に貯留した潤滑油Ｌに接触可能な位置とされている。なお、このオイル戻し溜り３６に貯留した潤滑油Ｌに接触可能な位置とは、デファレンシャル装置１０の作動状態における潤滑油Ｌが貯留している状態に対してである。これにより、ドライブピニオンシャフト１８の回転に伴って貯留される潤滑油Ｌが少なくなってもフロント軸受２６及びリヤ軸受２８の内輪部材２６ａ、２８ａの放熱を確実に行うことができる。
図１に戻って説明する。図１に図示されるように、すなわち、本実施例のデファレンシャル装置１０は、デファレンシャルキャリア１２内にデファレンシャルリングギヤ１４とドライブピニオン１６が噛合して配置されて構成されている。ドライブピニオン１６はドライブピニオンシャフト１８の図１で見て左端に一体的に形成されている。ドライブピニオンシャフト１８の図１で見て右端はコンパニオンフランジ２０のスリーブ２２がナット２４により締め付けられて回転連結されている。コンパニオンフランジ２０は不図示の継手やプロペラシャフトを介してフロントエンジンに駆動連結されており、フロントエンジンの駆動力が伝達されてくるようになっている。そして、ドライブピニオンシャフト１８はフロント軸受２６及びリヤ軸受２８によりデファレンシャルキャリア１２に支持されており、フロント軸受２６及びリヤ軸受２８の内輪部材２６ａ、２８ａがドライブピニオンシャフト１８に嵌合した状態で配置されている。
この構成により、フロントエンジンの駆動力が伝達されてドライブピニオンシャフト１８が回転すると、これに伴ってフロント軸受２６及びリヤ軸受２８の内輪部材２６ａ、２８ａもドライブピニオンシャフト１８の軸を中心に回転する。
ここで、冷却部材２９の凸部２９ｂが潤滑油貯留部としてのオイル戻し溜り３６に貯留した潤滑油Ｌに接触する位置状態として配設されている。そのため、内輪部材２６ａ、２８ａがドライブピニオンシャフト１８の軸を中心に回転するのに伴い、内輪部材２６ａ、２８ａの周方向に蓄積された摺動摩擦熱が順次放熱される。 As shown in FIG. 2, the arrangement position of the outer peripheral shape of the cooling member 29 is a position where the convex portion 29b can come into contact with the lubricating oil L stored in the oil return reservoir 36 configured as a lubricating oil storage portion. Has been. The position at which the lubricating oil L stored in the oil return reservoir 36 can be contacted is a state where the lubricating oil L in the operating state of the differential device 10 is stored. Thereby, even if the lubricating oil L stored with the rotation of the drive pinion shaft 18 decreases, the heat dissipation of the inner ring members 26a and 28a of the front bearing 26 and the rear bearing 28 can be reliably performed.
Returning to FIG. As shown in FIG. 1, that is, the differential device 10 of this embodiment is configured such that a differential ring gear 14 and a drive pinion 16 are arranged in a differential carrier 12 so as to mesh with each other. The drive pinion 16 is formed integrally with the left end of the drive pinion shaft 18 as viewed in FIG. The right end of the drive pinion shaft 18 as viewed in FIG. 1 is rotationally connected to a sleeve 22 of a companion flange 20 that is fastened by a nut 24. The companion flange 20 is drivingly connected to the front engine via a joint and a propeller shaft (not shown) so that the driving force of the front engine is transmitted. The drive pinion shaft 18 is supported on the differential carrier 12 by a front bearing 26 and a rear bearing 28, and the inner ring members 26 a and 28 a of the front bearing 26 and the rear bearing 28 are arranged in a state of being fitted to the drive pinion shaft 18. ing.
With this configuration, when the driving force of the front engine is transmitted and the drive pinion shaft 18 rotates, the inner ring members 26a and 28a of the front bearing 26 and the rear bearing 28 also rotate around the axis of the drive pinion shaft 18 accordingly. .
Here, the convex portion 29b of the cooling member 29 is disposed in a position in contact with the lubricating oil L stored in the oil return reservoir 36 as the lubricating oil storage portion. Therefore, as the inner ring members 26a and 28a rotate around the axis of the drive pinion shaft 18, the sliding frictional heat accumulated in the circumferential direction of the inner ring members 26a and 28a is sequentially released.

次に、本実施例の上記構成における潤滑作用を説明する。
図１に図示されるように、先ず、デファレンシャル装置１０は、デファレンシャルリングギヤ１４とドライブピニオン１６が噛合って駆動回転することにより、主にデファレンシャルリングギヤ１４により潤滑油室３２内の潤滑油Ｌが攪拌されて飛散し、この飛散した潤滑油Ｌによりデファレンシャル装置１０内の各潤滑箇所の全体の潤滑が行われる。
上記潤滑油室３２の潤滑において、デファレンシャルリングギヤ１４により上方まで掻き揚げられた飛散状態の潤滑油Ｌが導入流路３４を通ってオイル溜り３０に導入される。この導入された潤滑油Ｌによりフロント軸受２６及びリヤ軸受２８の円すいころ２６ｂ、２８ｂの小径部２６ｂ−１、２８ｂ−１側からの潤滑油Ｌの流通がポンプ作用と呼ばれる油の引き込み現象によって行われる。 Next, the lubricating action in the above-described configuration of the present embodiment will be described.
As shown in FIG. 1, first, the differential device 10 agitates the lubricating oil L in the lubricating oil chamber 32 mainly by the differential ring gear 14 when the differential ring gear 14 and the drive pinion 16 are engaged and rotated. Then, the entire lubrication location in the differential device 10 is lubricated by the scattered lubricating oil L.
In the lubrication of the lubricating oil chamber 32, the scattered lubricating oil L lifted up by the differential ring gear 14 is introduced into the oil reservoir 30 through the introduction flow path 34. The flow of the lubricating oil L from the small diameter portions 26b-1 and 28b-1 side of the tapered rollers 26b and 28b of the front bearing 26 and the rear bearing 28 by the introduced lubricating oil L is caused by an oil drawing phenomenon called pumping action. Is called.

一般的に、潤滑油は、使用温度が高い状態では粘度は低く、使用温度が低い状態では粘度が高いことが知られている。
また、デファレンシャル装置１０に用いられる潤滑油Ｌの粘度は使用温度によって変化する。例えば、長時間連続運転に伴いデファレンシャル装置１０内は高温状態となる。そのため、潤滑油Ｌの潤滑効率の低下を抑制するためにブリーザ装置によってデファレンシャル装置内の内圧を抑制したり、オイルクーラーによって潤滑油Ｌを冷却して、デファレンシャルリングギヤ１４により掻き揚げられて潤滑油オイル溜り３０に導入される潤滑油Ｌの使用温度状態を適温にすることが図られている。
しかしながら、フロント軸受２６及びリヤ軸受２８は、円すいころ２６ｂ、２８ｂがドライブピニオンシャフト１８の外周面上を転動する際に、円すいころ２６ｂ、２８ｂの外周面と内輪部材２６ａ、２８ａ及び外輪部材２６ｃ、２８ｃの円すい面が摺動するため摺動摩擦熱が発生する。特に、円すいころ２６ｂ、２８ｂの大径部２６ｂ−２、２８ｂ−２の端面と内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２の接触面において温度が上昇しやすい。このフロント軸受２６及びリヤ軸受２８内が高温状態で潤滑油Ｌが流入すると、潤滑油Ｌの粘度が低下する。
そして、潤滑油Ｌの粘度が低い状態では、円すいころ軸受に構成される円すいころ２６ｂ、２８ｂと、内輪部材２６ａ、２８ａ及び外輪部材２６ｃ、２８ｃの間において潤滑油Ｌの流通が不十分な状態となって金属接触を起こす転動状態となるおそれがあり、異常磨耗や焼きつきが発生しやすくなる。
すなわち、潤滑油オイル溜り３０に導入される潤滑油Ｌの使用温度状態が適温であっても、上記フロント軸受２６及びリヤ軸受２８内が摺動摩擦熱に伴って高温状態であると、この軸受内に流入した潤滑油Ｌが高温となり潤滑油Ｌの粘度が低下する。そのため良好な潤滑ができない状態となり、更には、この高温状態の潤滑油Ｌがデファレンシャル装置内を循環して再びフロント軸受２６及びリヤ軸受２８内に流入されると、より一層良好な潤滑ができない状態となる。 Generally, it is known that a lubricating oil has a low viscosity at a high use temperature and a high viscosity at a low use temperature.
Further, the viscosity of the lubricating oil L used in the differential device 10 varies depending on the operating temperature. For example, the inside of the differential apparatus 10 is in a high temperature state with continuous operation for a long time. Therefore, in order to suppress the reduction in the lubrication efficiency of the lubricating oil L, the internal pressure in the differential device is suppressed by the breather device, or the lubricating oil L is cooled by the oil cooler and is swept up by the differential ring gear 14 to be used as the lubricating oil oil. The use temperature state of the lubricating oil L introduced into the reservoir 30 is set to an appropriate temperature.
However, the front bearing 26 and the rear bearing 28 are arranged such that when the tapered rollers 26b, 28b roll on the outer peripheral surface of the drive pinion shaft 18, the outer peripheral surfaces of the tapered rollers 26b, 28b, the inner ring members 26a, 28a, and the outer ring member 26c. Since the conical surface of 28c slides, sliding frictional heat is generated. In particular, the temperature at the contact surfaces of the large diameter portions 26b-2, 28b-2 of the tapered rollers 26b, 28b and the large flange portions 26a-2, 28a-2 on the large diameter end side of the inner ring members 26a, 28a. Easy to rise. When the lubricating oil L flows in the front bearing 26 and the rear bearing 28 at a high temperature, the viscosity of the lubricating oil L decreases.
When the viscosity of the lubricating oil L is low, the lubricating oil L is not sufficiently distributed between the tapered rollers 26b and 28b configured in the tapered roller bearing and the inner ring members 26a and 28a and the outer ring members 26c and 28c. This may result in a rolling state that causes metal contact, and abnormal wear and seizure are likely to occur.
That is, even if the operating temperature state of the lubricating oil L introduced into the lubricating oil reservoir 30 is an appropriate temperature, if the inside of the front bearing 26 and the rear bearing 28 is in a high temperature state due to sliding frictional heat, The lubricating oil L that has flowed into the tank becomes high temperature, and the viscosity of the lubricating oil L decreases. For this reason, it becomes a state where good lubrication cannot be performed, and furthermore, when this high temperature lubricating oil L circulates in the differential device and flows again into the front bearing 26 and the rear bearing 28, even better lubrication cannot be achieved. It becomes.

そこで、フロント軸受２６及びリヤ軸受２８において、潤滑油貯留部（潤滑油室３２及びオイル戻し溜り３６）側には、温度上昇しやすい内輪部材２６ａ、２８ａの大鍔部２６ａ−２、２８ａ−２側を放熱させる冷却部材２７、２９が、その大鍔部２６ａ−２、２８ａ−２側に接触して配設されている。
この冷却部材２７、２９の外周形状は、潤滑油Ｌとの接触面積を大きくすることができるように凹凸形状に形成されている。また、冷却部材２７、２９は、放熱性の良好な金属で形成されている。また、冷却部材２７、２９の外周形状の配設位置は、凸部が潤滑油貯留部として構成されている潤滑油室３２及びオイル戻し溜り３６に貯留した潤滑油Ｌに接触可能な位置とされている。
そのため、フロントエンジンの駆動力が伝達されてドライブピニオンシャフト１８が回転すると、これに伴ってフロント軸受２６及びリヤ軸受２８の内輪部材２６ａ、２８ａもドライブピニオンシャフト１８の軸を中心に回転し、冷却部材２７、２９の凸部が潤滑油貯留部としての潤滑油室３２及びオイル戻し溜り３６に貯留した潤滑油Ｌに接触する。そして、内輪部材２６ａ、２８ａがドライブピニオンシャフト１８の軸を中心に回転するのに伴い、内輪部材２６ａ、２８ａの周方向に蓄積された摺動摩擦熱が順次放熱される。 Therefore, in the front bearing 26 and the rear bearing 28, on the side of the lubricating oil reservoir (the lubricating oil chamber 32 and the oil return reservoir 36), the large collar portions 26a-2 and 28a-2 of the inner ring members 26a and 28a that are likely to rise in temperature. Cooling members 27 and 29 that dissipate heat are disposed in contact with the large collar portions 26a-2 and 28a-2.
The outer peripheral shape of the cooling members 27 and 29 is formed in an uneven shape so that the contact area with the lubricating oil L can be increased. The cooling members 27 and 29 are made of a metal with good heat dissipation. In addition, the arrangement positions of the outer peripheral shapes of the cooling members 27 and 29 are positions where the convex portions can come into contact with the lubricating oil L stored in the lubricating oil chamber 32 and the oil return reservoir 36 which are configured as the lubricating oil storing portion. ing.
Therefore, when the driving force of the front engine is transmitted and the drive pinion shaft 18 is rotated, the inner ring members 26a and 28a of the front bearing 26 and the rear bearing 28 are also rotated around the axis of the drive pinion shaft 18 and cooled. The convex portions of the members 27 and 29 are in contact with the lubricating oil L stored in the lubricating oil chamber 32 and the oil return reservoir 36 as the lubricating oil storage portion. As the inner ring members 26a, 28a rotate around the axis of the drive pinion shaft 18, the sliding frictional heat accumulated in the circumferential direction of the inner ring members 26a, 28a is sequentially released.

これらの構成によれば、潤滑油Ｌが排出されるフロント軸受２６及びリヤ軸受２８の内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２側には、潤滑油Ｌを貯留可能な潤滑油貯留部として潤滑油室３２及びオイル戻し溜り３６が形成されている。そして、環状に形成された冷却部材２７、２９が内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２に接触可能に配設されている。この冷却部材２７、２９の外周形状の配設位置は、少なくともその外周端部が潤滑油貯留部に貯留した潤滑油Ｌに接触可能な位置とされている。
すなわち、温度上昇しやすい内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２の摺動摩擦熱が、冷却部材２７、２９を介して潤滑油室３２及びオイル戻し溜り３６に貯留した潤滑油Ｌに放熱させることができる。そのため、内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２の温度上昇が抑制されるため軸受内に流入した潤滑油Ｌの温度上昇を抑制することができ、潤滑性の低下を抑制することができる。 According to these structures, the large flange portions 26a-2 and 28a-2, which are the large diameter end portions of the inner ring members 26a and 28a of the front bearing 26 and the rear bearing 28 from which the lubricating oil L is discharged, are lubricated. A lubricating oil chamber 32 and an oil return reservoir 36 are formed as a lubricating oil reservoir that can store the oil L. The annularly formed cooling members 27 and 29 are disposed so as to come into contact with the large collar portions 26a-2 and 28a-2 which are the large diameter end portions of the inner ring members 26a and 28a. The arrangement positions of the outer peripheral shapes of the cooling members 27 and 29 are positions where at least the outer peripheral end portions thereof can contact the lubricating oil L stored in the lubricating oil storage portion.
That is, the sliding frictional heat of the large flange portions 26a-2 and 28a-2 on the large-diameter end side of the inner ring members 26a and 28a that are likely to rise in temperature is supplied to the lubricating oil chamber 32 and the oil return via the cooling members 27 and 29. Heat can be radiated to the lubricating oil L stored in the reservoir 36. Therefore, since the temperature rise of the large flange portions 26a-2 and 28a-2 on the large diameter end side of the inner ring members 26a and 28a is suppressed, the temperature rise of the lubricating oil L flowing into the bearing can be suppressed. It is possible to suppress a decrease in lubricity.

また、環状に形成された冷却部材２７、２９は、大鍔部２６ａ−２、２８ａ−２に接触可能に配設される位置として、大鍔部２６ａ−２、２８ａ−２の端面２８ａ−４又は外周面２８ａ−３の少なくとも一方において接触可能な位置とされている。これにより、冷却部材２７、２９を環状に形成する際の加工は複雑になることがない。また、冷却部材２７、２９を配設することに伴い、軸受を支持する支持部材側の加工が必要となる場合でも、この支持部材側の加工が複雑にならない。すなわち、加工の容易性を図りつつ、冷却部材２７、２９を内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２に接触可能に配設することができる。   Further, the cooling members 27 and 29 formed in an annular shape are arranged so as to be able to come into contact with the large collar portions 26a-2 and 28a-2, and the end faces 28a-4 of the large collar portions 26a-2 and 28a-2. Or it is set as the position which can contact in at least one of the outer peripheral surfaces 28a-3. Thereby, the process at the time of forming the cooling members 27 and 29 annularly does not become complicated. In addition, when the cooling members 27 and 29 are disposed, even when processing on the support member side that supports the bearing is required, processing on the support member side is not complicated. That is, the cooling members 27 and 29 can be disposed so as to be able to come into contact with the large collar portions 26a-2 and 28a-2 on the large diameter end side of the inner ring members 26a and 28a while facilitating processing.

また、冷却部材２７、２９は、放熱性の良好な金属で形成されている。これにより、フロント軸受２６及びリヤ軸受２８において、温度上昇しやすい内輪部材２６ａ、２８ａの大径端部側である大鍔部２６ａ−２、２８ａ−２の放熱をより一層向上させることができる。
また、冷却部材２７、２９の形状は、潤滑油室３２及びオイル戻し溜り３６に貯留した潤滑油Ｌに接触可能な部位の形状が凹凸形状で形成されている。これにより、冷却部材２７、２９は、潤滑油室３２及びオイル戻し溜り３６に貯留した潤滑油Ｌと接触する面積が大きい形状で形成されるためより一層効率的に、潤滑油Ｌへの放熱を行うことができる。 The cooling members 27 and 29 are made of a metal with good heat dissipation. Thereby, in the front bearing 26 and the rear bearing 28, it is possible to further improve the heat radiation of the large flange portions 26a-2 and 28a-2 which are the large diameter end portions of the inner ring members 26a and 28a that are likely to rise in temperature.
In addition, the cooling members 27 and 29 are formed in a concave-convex shape at a portion that can contact the lubricating oil L stored in the lubricating oil chamber 32 and the oil return reservoir 36. As a result, the cooling members 27 and 29 are formed in a shape having a large area in contact with the lubricating oil L stored in the lubricating oil chamber 32 and the oil return reservoir 36, so that heat can be radiated to the lubricating oil L more efficiently. It can be carried out.

以上、本発明の一実施例について説明したが、本発明はその他各種の実施形態が考えられるものである。
例えば、上記の実施例では、冷却部材２９は、外周形状において潤滑油Ｌとの接触面積を大きくするために、潤滑油Ｌが流入可能な状態の凹凸形状に形成されているものとして、中心部から外方に向かって放射状に凸部２９ｂが複数配列されているものについて説明したが、この凸部は、必ずしも一定の形状に限定されないものである。
また、上記の実施例では、冷却部材２７、２９は、この凹凸形状が３層に構成されて、一体に形成されたものを示した。しかしながら、これに限定されるものではなく、図４（Ｂ）に図示されるように、冷却部材２７、２９の外周形状は潤滑油Ｌとの接触面積を大きくする構成であれば良い。例えば、一層形状の略スリット構造に形成されたものでも良い。また、この一層形状のものを複数重ねて構成されたものでも良い。
また、上記の実施例では、デファレンシャル装置１０は四輪駆動の駆動形態自動車に適用されたデファレンシャル装置のうちフロントデファレンシャル装置を例にして説明したが、リヤデファレンシャル装置にも適用できる。また、フロントエンジンフロントドライブの駆動形態やフロントエンジンリヤドライブの駆動形態等、その他各種の駆動形態に適用可能なものである。 As mentioned above, although one Example of this invention was described, this invention can consider various other embodiment.
For example, in the above-described embodiment, the cooling member 29 is assumed to be formed in a concavo-convex shape into which the lubricating oil L can flow in order to increase the contact area with the lubricating oil L in the outer peripheral shape. A description has been given of the case where a plurality of convex portions 29b are arranged radially outward from the outer side, but the convex portions are not necessarily limited to a certain shape.
In the above-described embodiment, the cooling members 27 and 29 are formed integrally with the uneven shape formed in three layers. However, the present invention is not limited to this, and the outer peripheral shape of the cooling members 27 and 29 may be configured to increase the contact area with the lubricating oil L as shown in FIG. For example, it may be formed in a one-layer substantially slit structure. Further, a structure in which a plurality of the single-layer shapes are stacked may be used.
In the above-described embodiment, the differential apparatus 10 has been described by taking the front differential apparatus as an example of the differential apparatus applied to a four-wheel drive vehicle. However, the differential apparatus 10 can also be applied to a rear differential apparatus. Further, the present invention can be applied to various other driving modes such as a driving mode of a front engine front drive and a driving mode of a front engine rear drive.

デファレンシャル装置の全体構成を概略的に示す一実施例の断面図である。1 is a cross-sectional view of an embodiment schematically showing an overall configuration of a differential apparatus. 本実施例としてのデファレンシャル装置のドライブピニオンシャフトを支持するフロント軸受及びリヤ軸受の部位を拡大した断面図である。It is sectional drawing to which the site | part of the front bearing and rear bearing which support the drive pinion shaft of the differential apparatus as a present Example was expanded. 本実施例としてのデファレンシャル装置のドライブピニオンシャフトを支持するリヤ軸受の構成を示した分解斜視図である。It is the disassembled perspective view which showed the structure of the rear bearing which supports the drive pinion shaft of the differential apparatus as a present Example. 本実施例としてのデファレンシャル装置のドライブピニオンシャフトを支持するリヤ軸受の内輪部材の大径端部側である大鍔部側における潤滑油の冷却部材の斜視図である。It is a perspective view of the cooling member of the lubricating oil in the large collar part side which is the large diameter edge part side of the inner ring member of the rear bearing which supports the drive pinion shaft of the differential device as this example. 従来におけるデファレンシャル装置の全体構成を概略的に示す断面図である。It is sectional drawing which shows roughly the whole structure of the conventional differential apparatus.

符号の説明Explanation of symbols

１０ デファレンシャル装置
１２ デファレンシャルキャリア
１３ ドライブシャフト
１４ デファレンシャルリングギヤ
１６ ドライブピニオン
１８ ドライブピニオンシャフト
２０ コンパニオンフランジ
２２ スリーブ
２４ ナット
２６ フロント軸受
２６ａ 内輪部材
２６ａ−１ 小鍔部
２６ａ−２ 大鍔部
２６ｂ 円すいころ
２６ｂ−１ 小径部
２６ｂ−２ 大径部
２６ｃ 外輪部材
２６ｄ 保持器
２７ 冷却部材
２８ リヤ軸受
２８ａ 内輪部材
２８ａ−１ 小鍔部
２８ａ−２ 大鍔部
２８ｂ 円すいころ
２８ｂ−１ 小径部
２８ｂ−２ 大径部
２８ｃ 外輪部材
２８ｄ 保持器
２９ 冷却部材
２９ａ 貫通孔
２９ｂ 凸部
３０ オイル溜り
３２ 潤滑油室
３４ 導入流路
３６ オイル戻し溜り
３８ オイルシール
Ｆ 自動車の前進時における進行方向
Ｌ 潤滑油
DESCRIPTION OF SYMBOLS 10 Differential apparatus 12 Differential carrier 13 Drive shaft 14 Differential ring gear 16 Drive pinion 18 Drive pinion shaft 20 Companion flange 22 Sleeve 24 Nut 26 Front bearing 26a Inner ring member 26a-1 Small collar part 26a-2 Large collar part 26b Tapered roller 26b-1 Small diameter portion 26b-2 Large diameter portion 26c Outer ring member 26d Cage 27 Cooling member 28 Rear bearing 28a Inner ring member 28a-1 Small flange portion 28a-2 Large flange portion 28b Tapered roller 28b-1 Small diameter portion 28b-2 Large diameter portion 28c Outer ring member 28d Cage 29 Cooling member 29a Through hole 29b Convex part 30 Oil reservoir 32 Lubricating oil chamber 34 Introduction flow path 36 Oil return reservoir 38 Oil seal F Traveling direction L during forward movement of automobile L Lubricating oil

Claims (4)

外周面が円すい面状に形成され、該外周面における大径端部側には鍔状の大鍔部が形成された内輪部材と、
該内輪部材の外周面の円すい面状に対向して、内周面が円すい面状に形成された外輪部材と、
前記内輪部材と前記外輪部材の間に円すいころが複数配列されており、
前記円すいころの転動を円滑にする潤滑油が、該内輪部材の小径端部側から流入し、大鍔部側に排出される円すいころ軸受装置であって、
前記潤滑油が排出される前記大鍔部側には、該潤滑油を貯留可能な潤滑油貯留部が形成されており、
前記内輪部材の大鍔部に、環状に形成された冷却部材が接触可能に配設されており、
該冷却部材の外周形状の配設位置は、少なくともその外周端部が前記潤滑油貯留部に貯留した潤滑油に接触可能な位置とされていることを特徴とする円すいころ軸受装置。 An inner ring member in which an outer peripheral surface is formed in a conical surface shape, and a flange-shaped large collar portion is formed on a large diameter end portion side of the outer peripheral surface;
Opposing the outer ring surface of the inner ring member to a conical surface, the outer ring member having an inner peripheral surface formed into a conical surface,
A plurality of tapered rollers are arranged between the inner ring member and the outer ring member,
A taper roller bearing device in which the lubricating oil for smooth rolling of the tapered roller flows from the small diameter end side of the inner ring member and is discharged to the large collar side,
On the large collar portion side from which the lubricating oil is discharged, a lubricating oil storage portion capable of storing the lubricating oil is formed,
A cooling member formed in an annular shape is disposed so as to be able to contact the large collar portion of the inner ring member,
The tapered roller bearing device is characterized in that the outer peripheral shape of the cooling member is disposed at a position where at least an outer peripheral end thereof can contact the lubricating oil stored in the lubricating oil storage section. 請求項１記載の円すいころ軸受装置であって、
前記冷却部材の配設位置は、前記内輪部材の大鍔部の端面又は外周面の少なくとも一方に接触可能な位置とされていることを特徴とする円すいころ軸受装置。 The tapered roller bearing device according to claim 1,
The tapered roller bearing device is characterized in that the cooling member is disposed at a position capable of contacting at least one of an end surface or an outer peripheral surface of the large collar portion of the inner ring member. 請求項１又は請求項２に記載の円すいころ軸受装置であって、
前記冷却部材は、放熱性の良好な金属で形成されていることを特徴とする円すいころ軸受装置。 The tapered roller bearing device according to claim 1 or 2,
The tapered roller bearing device, wherein the cooling member is made of a metal having good heat dissipation. 請求項１又は請求項２に記載の円すいころ軸受装置であって、
前記冷却部材の形状は、前記潤滑油貯留部に貯留した潤滑油に接触可能な部位の形状が凹凸形状で形成されていることを特徴とする円すいころ軸受装置。
The tapered roller bearing device according to claim 1 or 2,
The tapered roller bearing device is characterized in that the shape of the cooling member is formed in a concave-convex shape at a portion that can contact the lubricating oil stored in the lubricating oil storage section.
JP2008262967A 2008-10-09 2008-10-09 Conical roller bearing device Pending JP2010091054A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020067166A (en) * 2018-10-26 2020-04-30 日本精工株式会社 Rolling bearing unit for supporting wheel

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020067166A (en) * 2018-10-26 2020-04-30 日本精工株式会社 Rolling bearing unit for supporting wheel
JP7147467B2 (en) 2018-10-26 2022-10-05 日本精工株式会社 Rolling bearing unit for wheel support

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