JP4314430B2 - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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JP4314430B2
JP4314430B2 JP2003302353A JP2003302353A JP4314430B2 JP 4314430 B2 JP4314430 B2 JP 4314430B2 JP 2003302353 A JP2003302353 A JP 2003302353A JP 2003302353 A JP2003302353 A JP 2003302353A JP 4314430 B2 JP4314430 B2 JP 4314430B2
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inner ring
diameter
tapered roller
small
cage
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JP2005069421A (en
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賢一 尾野
邦彦 横田
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JTEKT Corp
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JTEKT Corp
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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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
    • F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
    • 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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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Of Bearings (AREA)
  • Rolling Contact Bearings (AREA)

Description

この発明は、円すいころ軸受、さらに詳しくは、自動車の最終減速装置部分などに配されて、その装置の内部に収容されるオイルを利用して潤滑を行う円すいころ軸受に関する。   The present invention relates to a tapered roller bearing, and more particularly, to a tapered roller bearing that is disposed in a final reduction gear portion of an automobile and performs lubrication using oil contained in the device.

外輪、内輪、両輪の間に配置された複数の円すいころ、およびこれらの円すいころを保持する保持器を有する円すいころ軸受は、コンパクトで、大きなラジアル荷重およびアキシャル荷重を支持することができ、しかも、高速回転で使用することができるため、広く使用されている。しかしながら、玉軸受に比べると、トルク損失が大きく、エネルギー節約の観点から、そのトルクの減少が課題となっている。   A tapered roller bearing having a plurality of tapered rollers arranged between an outer ring, an inner ring, and both wheels, and a cage for holding these tapered rollers is compact and can support a large radial load and an axial load. Because it can be used at high speed, it is widely used. However, torque loss is larger than ball bearings, and the reduction of the torque is a problem from the viewpoint of energy saving.

従来の円すいころ軸受(21)としては、図２に示すように、外輪(22)、内輪(23)、両輪(22)(23)の間に配置された複数の円すいころ(24)、およびこれらの円すいころ(24)を保持する保持器(25)を有し、保持器(25)の小径側端部が径方向内方に折り曲げられて、折曲げ部(25a)が内輪(23)の小鍔部(23a)に間隙をおいて臨まされているものが一般的である。   As shown in FIG. 2, the conventional tapered roller bearing (21) includes an outer ring (22), an inner ring (23), a plurality of tapered rollers (24) disposed between both rings (22) and (23), and It has a cage (25) that holds these tapered rollers (24), the small diameter side end of the cage (25) is bent radially inward, and the bent portion (25a) is an inner ring (23). In general, it is faced with a gap in the gutter part (23a).

また、特許文献１には、保持器の折曲げ部と内輪の小鍔部との隙間について考慮した円すいころが記載されている。
特開平１０−８９３５３号公報 Patent Document 1 describes a tapered roller considering a gap between a bent portion of a cage and a small collar portion of an inner ring.
Japanese Patent Laid-Open No. 10-89353

上記図２に示した一般的な円すいころ軸受では、軸受回転に伴うポンプ作用によって内輪小径側からオイルが軸受内部に流入して大径側より排出される。回転トルク発生要因として、円すいころと内輪との間の抵抗のほかに、オイルの撹拌による抵抗があり、特に高回転領域で使用される円すいころ軸受では、後者の抵抗が回転トルクの大きな部分を占めているものと考えられる。   In the general tapered roller bearing shown in FIG. 2, oil flows from the inner ring small diameter side into the bearing and is discharged from the large diameter side by the pump action accompanying the bearing rotation. In addition to the resistance between the tapered roller and the inner ring, the cause of rotational torque is resistance due to oil agitation. Especially in the tapered roller bearings used in the high rotation range, the latter resistance causes a large part of the rotational torque. It is thought that it occupies.

上記特許文献１に記載の円すいころ軸受は、潤滑オイルの流れを考慮することにより、軸受はくりを防止したものであるが、この軸受では、回転中に保持器の折曲げ端部が内輪に接触しないように、折曲げ端部と内輪外径との隙間を管理する必要があり、ばらつきを極めて小さく抑えて製造しなければならないという問題がある。   The tapered roller bearing described in Patent Document 1 prevents the bearing from being broken by considering the flow of lubricating oil. In this bearing, the bent end of the cage is rotated to the inner ring during rotation. It is necessary to manage the gap between the bent end and the outer diameter of the inner ring so that they do not come into contact with each other, and there is a problem that manufacturing must be performed with extremely small variations.

この発明の目的は、軸受内のオイルの流れを適正化することにより回転トルクを減少し、しかも、製造時のばらつきをある程度許容することができる円すいころ軸受を提供することにある。   An object of the present invention is to provide a tapered roller bearing that can reduce rotational torque by optimizing the flow of oil in the bearing, and can tolerate variations during manufacturing to some extent.

この発明による円すいころ軸受は、外輪、内輪、両輪の間に配置された複数の円すいころ、およびこれらの円すいころを保持する保持器を有する円すいころ軸受において、内輪の小径側端部は、径方向外方に凸形状で円すいころの軸方向外方に位置して円すいころの軸方向の移動を規制する小径鍔部と、同部より小径で同部の軸方向外方に連なる円筒部とからなり、保持器の小径側端部は、径方向内方に折り曲げられて小径鍔部よりも軸方向外方において内輪の円筒部の外径に間隙をおいて臨まされる折曲げ部を有しており、内輪の小径鍔部の外径＞保持器の折曲げ部の内径とされることにより、折曲げ部は、内輪の円筒部の外径との間に径方向のラビリンスを形成するとともに、内輪の小径鍔部端面との間に軸方向のラビリンスを形成していることを特徴とするものである。 A tapered roller bearing according to the present invention is a tapered roller bearing having an outer ring, an inner ring, a plurality of tapered rollers disposed between both rings, and a retainer for holding these tapered rollers. A small-diameter flange portion that is convex outward in the direction and is positioned outwardly in the axial direction of the tapered roller and restricts axial movement of the tapered roller, and a cylindrical portion that is smaller in diameter than the same portion and that extends outward in the axial direction. The end portion on the small diameter side of the cage has a bent portion that is bent inward in the radial direction and faces the outer diameter of the cylindrical portion of the inner ring with a gap in the axial direction outward from the small diameter flange portion. And the outer diameter of the small-diameter flange portion of the inner ring is set to be larger than the inner diameter of the bent portion of the cage, so that the bent portion forms a radial labyrinth with the outer diameter of the cylindrical portion of the inner ring. In addition, an axial labyrinth is formed between the inner ring and the small-diameter collar end surface. And it is characterized in Rukoto.

内輪ならびに保持器の大径側端部形状および外輪の形状は、特に、限定されるものではなく、従来の種々の形状が適宜適用される。   The shape of the inner ring and the large-diameter side end portion of the cage and the shape of the outer ring are not particularly limited, and various conventional shapes are appropriately applied.

保持器の折曲げ端と内輪との位置関係は、オイル流入口にラビリンスを形成して流入量を低減することを可能とする範囲で適宜設定されるが、より具体的には、小径鍔部の端面と折曲げ部との軸方向の間隔が１．５〜３ｍｍ程度、折曲げ部の内径と円筒部の外径との間隔が１〜２ｍｍ程度とされる。これらの間隔は、製造時の中心寸法とされ、製造時の誤差による多少のばらつきが許容される。   The positional relationship between the bent end of the cage and the inner ring is appropriately set within a range in which a labyrinth can be formed at the oil inlet and the amount of inflow can be reduced. The axial distance between the end face and the bent part is about 1.5 to 3 mm, and the distance between the inner diameter of the bent part and the outer diameter of the cylindrical part is about 1 to 2 mm. These intervals are the center dimensions at the time of manufacture, and some variation due to errors at the time of manufacture is allowed.

この発明の円すいころ軸受によると、オイル流入口である保持器と内輪との間にラビリンスが形成されているので、軸受へのオイル流入量が低減し、これにより、オイルの撹拌抵抗が低減し、軸受のトルク損失が低減する。しかも、保持器と内輪との間隙がある程度の範囲内にあれば、上記効果が発揮されることから、製造時のばらつきがある程度許容され、製造が容易となる。   According to the tapered roller bearing of the present invention, since the labyrinth is formed between the cage that is the oil inlet and the inner ring, the amount of oil flowing into the bearing is reduced, thereby reducing the oil stirring resistance. The torque loss of the bearing is reduced. In addition, if the gap between the cage and the inner ring is within a certain range, the above-described effect is exhibited, so that variations during manufacturing are allowed to some extent, and manufacturing is facilitated.

以下、図面を参照して、この発明の実施形態について説明する。以下の説明において、左右は、図の左右をいうものとする。   Embodiments of the present invention will be described below with reference to the drawings. In the following description, the left and right refer to the left and right in the figure.

図１に示すこの発明による円すいころ軸受(1)は、外輪(2)、内輪(3)、両輪(2)(3)の間に配置された複数の円すいころ(4)、および円すいころ(4)を保持する保持器(5)を有している。   A tapered roller bearing (1) according to the present invention shown in FIG. 1 includes an outer ring (2), an inner ring (3), a plurality of tapered rollers (4) disposed between both rings (2) and (3), and a tapered roller ( It has a cage (5) that holds 4).

内輪(3)は、円すい状の軌道面(11)と、軌道面(1)の左端部に設けられた小径側端部(12)と、軌道面(13)の右端部に設けられた大径側端部(13)とを有している。内輪(3)の小径側端部(12)は、円すいころ(4)の軸方向の移動を規制する小径鍔部(14)と、同部(14)より小径でかつ同部(14)の軸方向外方に連なる円筒部(15)とからなり、内輪(3)の大径側端部(13)は、円すいころ(4)の軸方向の移動を規制する大径鍔部からなる。   The inner ring (3) has a conical raceway surface (11), a small-diameter end (12) provided at the left end of the raceway surface (1), and a large end provided at the right end of the raceway surface (13). And a radial end (13). The end (12) on the small diameter side of the inner ring (3) has a small diameter flange (14) that restricts the axial movement of the tapered roller (4), and a diameter smaller than that of the same (14). It consists of a cylindrical portion (15) that extends outward in the axial direction, and the large-diameter side end portion (13) of the inner ring (3) consists of a large-diameter flange that restricts the axial movement of the tapered roller (4).

外輪(2)は、円すい軌道面(16)を有しており、その右端面は、内輪(3)の右端面よりも内方にあり、その左端面は、内輪(3)の左端面と面一とされている。   The outer ring (2) has a conical raceway surface (16), its right end surface is inward of the right end surface of the inner ring (3), and its left end surface is the left end surface of the inner ring (3). It is considered to be the same.

保持器(5)は、円すいころ(4)よりも右方に突出する大径側端部(17)と、同左方に突出する小径側端部(18)とを有している。保持器(5)の小径側端部(18)は、径方向内方に折り曲げられた折曲げ部(19)を有しており、折曲げ部(19)は、内輪(3)の小径側端部(12)との間にラビリンスを形成するように、内輪(3)の小径側端部(12)の円筒部(15)の外径に間隙をおいて臨まされている。   The cage (5) has a large-diameter side end (17) projecting to the right of the tapered roller (4) and a small-diameter side end (18) projecting to the left. The small diameter side end (18) of the cage (5) has a bent portion (19) bent radially inward, and the bent portion (19) is a small diameter side of the inner ring (3). The outer diameter of the cylindrical portion (15) of the small-diameter side end portion (12) of the inner ring (3) is provided with a gap so as to form a labyrinth with the end portion (12).

図１において、内輪(3)の小径鍔部(14)の左面（端面）と保持器(5)の小径側の折曲げ部(19)の右面との間には、軸方向のラビリンスとしての間隙Ａが設けられており、内輪(3)の小径側の円筒部(15)の外径と保持器(5)の小径側の折曲げ部(19)の内径との間には、径方向のラビリンスとしての間隙Ｒが設けられている。ここで、軸方向の間隙Ａは、１．５〜３ｍｍ程度とされ、径方向の間隙Ｒは、１〜２ｍｍとされている。 In FIG. 1, there is an axial labyrinth between the left surface (end surface) of the small-diameter flange portion (14) of the inner ring (3) and the right surface of the small-diameter side bent portion (19) of the cage (5) . A gap A is provided between the outer diameter of the cylindrical portion (15) on the smaller diameter side of the inner ring (3) and the inner diameter of the bent portion (19) on the smaller diameter side of the cage (5). A gap R is provided as a labyrinth . Here, the gap A in the axial direction is about 1.5 to 3 mm, and the gap R in the radial direction is 1 to 2 mm.

この発明の円すいころ軸受(1)は、ファイナル・ギア装置やデファレンシャル・ギア装置を有する自動車の最終減速装置において、ピニオン・シャフトをデファレンシャル・キャリアに回転自在に支持したり、デファレンシャル・ケースをデファレンシャル・キャリアに回転自在に支持したりする軸受として好適に使用される。このような軸受では、自動車の最終減速装置の内部に収容されるオイルを利用して潤滑が行なわれ、特に高回転領域で使用された場合に、オイルの流れによる抵抗に伴うトルク損失の増大が問題となっている。   The tapered roller bearing (1) of the present invention is a final reduction device for an automobile having a final gear device or a differential gear device, and supports the pinion shaft rotatably on the differential carrier or the differential case on the differential case. It is preferably used as a bearing that is rotatably supported by a carrier. In such a bearing, lubrication is performed using oil contained in the final reduction gear of the automobile, and particularly when used in a high rotation region, torque loss increases due to resistance due to oil flow. It is a problem.

この発明の円すいころ軸受(1)によると、軸受回転に伴うポンプ作用によって内輪小径側からオイルが軸受内部に流入して大径側より排出されるが、軸方向間隙Ａおよび径方向間隙Ｒにより、オイル流入口である保持器(5)の小径側端部(18)と内輪(3)小径側端部(12)との間にラビリンスが形成されているので、上記の自動車の最終減速装置で使用された場合、軸受内へのオイル流入量が低減し、この結果、オイルの撹拌抵抗が低減することから、トルク損失を低減することができる。   According to the tapered roller bearing (1) of the present invention, oil flows from the inner ring small diameter side into the bearing and is discharged from the large diameter side by the pump action accompanying the bearing rotation, but the axial gap A and the radial gap R Since the labyrinth is formed between the small diameter side end (18) and the inner ring (3) small diameter side end (12) of the cage (5), which is an oil inflow port, the above-described final reduction device of the automobile In this case, the amount of oil flowing into the bearing is reduced, and as a result, the oil stirring resistance is reduced, so that torque loss can be reduced.

図１は、この発明の円すいころ軸受の実施形態を示す上半部の縦断面図である。FIG. 1 is a longitudinal sectional view of an upper half portion showing an embodiment of a tapered roller bearing of the present invention. 図２は、従来の円すいころ軸受を示す図である。FIG. 2 is a view showing a conventional tapered roller bearing.

符号の説明Explanation of symbols

(1) 円すいころ軸受
(2) 外輪
(3) 内輪
(4) 円すいころ
(5) 保持器
(12) 小径側端部
(14) 小径鍔部
(15) 円筒部
(18) 小径側端部
(19) 折曲げ部
(A) 軸方向間隙
(R) 径方向間隙 (1) Tapered roller bearing
(2) Outer ring
(3) Inner ring
(4) Tapered rollers
(5) Cage
(12) Small diameter end
(14) Small diameter collar
(15) Cylindrical part
(18) Small diameter end
(19) Bending part
(A) Axial clearance
(R) Radial gap

Claims (1)

外輪、内輪、両輪の間に配置された複数の円すいころ、およびこれらの円すいころを保持する保持器を有する円すいころ軸受において、
内輪の小径側端部は、径方向外方に凸形状で円すいころの軸方向外方に位置して円すいころの軸方向の移動を規制する小径鍔部と、同部より小径で同部の軸方向外方に連なる円筒部とからなり、保持器の小径側端部は、径方向内方に折り曲げられて小径鍔部よりも軸方向外方において内輪の円筒部の外径に間隙をおいて臨まされる折曲げ部を有しており、
内輪の小径鍔部の外径＞保持器の折曲げ部の内径とされることにより、折曲げ部は、内輪の円筒部の外径との間に径方向のラビリンスを形成するとともに、内輪の小径鍔部端面との間に軸方向のラビリンスを形成していることを特徴とする円すいころ軸受。 In a tapered roller bearing having an outer ring, an inner ring, a plurality of tapered rollers arranged between both wheels, and a cage for holding these tapered rollers,
The inner ring has a small-diameter end that protrudes radially outward and is positioned axially outward of the tapered roller to restrict axial movement of the tapered roller, and has a smaller diameter than the same part. The end of the cage on the small-diameter side is bent radially inward so that there is a gap in the outer diameter of the cylindrical portion of the inner ring in the axially outward direction from the small-diameter flange . And has a bent part
By setting the outer diameter of the small-diameter flange portion of the inner ring> the inner diameter of the bent portion of the cage, the bent portion forms a labyrinth in the radial direction between the outer diameter of the cylindrical portion of the inner ring and the inner ring A tapered roller bearing characterized in that an axial labyrinth is formed between the end surface of the small-diameter flange portion.
JP2003302353A 2003-08-27 2003-08-27 Tapered roller bearing Expired - Lifetime JP4314430B2 (en)

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JP2003302353A JP4314430B2 (en) 2003-08-27 2003-08-27 Tapered roller bearing

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JP2005069421A JP2005069421A (en) 2005-03-17
JP4314430B2 true JP4314430B2 (en) 2009-08-19

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JP6520061B2 (en) 2013-12-25 2019-05-29 株式会社ジェイテクト Ball bearing
JP6458458B2 (en) 2013-12-25 2019-01-30 株式会社ジェイテクト Tapered roller bearing
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