JP5256871B2 - Bottom shell-type full complement roller bearing and universal joint - Google Patents

Bottom shell-type full complement roller bearing and universal joint Download PDF

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JP5256871B2
JP5256871B2 JP2008155309A JP2008155309A JP5256871B2 JP 5256871 B2 JP5256871 B2 JP 5256871B2 JP 2008155309 A JP2008155309 A JP 2008155309A JP 2008155309 A JP2008155309 A JP 2008155309A JP 5256871 B2 JP5256871 B2 JP 5256871B2
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outer ring
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JP2009299797A (en
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政人 樋口
弘明 大沢
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NSK Ltd
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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
    • F16C33/58—Raceways; Race rings
    • F16C33/588—Races of sheet metal
    • 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
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F16C21/005—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement the external zone of a bearing with rolling members, e.g. needles, being cup-shaped, with or without a separate thrust-bearing disc or ring, e.g. for universal joints
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/26—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected
    • F16D3/38—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another
    • F16D3/40—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes
    • F16D3/41—Hooke's joints or other joints with an equivalent intermediate member to which each coupling part is pivotally or slidably connected with a single intermediate member with trunnions or bearings arranged on two axes perpendicular to one another with intermediate member provided with two pairs of outwardly-directed trunnions on intersecting axes with ball or roller bearings

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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

本発明は、有底筒状のシェル型の外輪（板金を絞り加工して形成した外輪）を有する底付きシェル型総ころ軸受、および、その軸受を使用したユニバーサルジョイントに関する。   The present invention relates to a bottomed shell-type full roller bearing having a bottomed cylindrical shell-type outer ring (an outer ring formed by drawing a sheet metal), and a universal joint using the bearing.

従来のユニバーサルジョイントとして、底付きシェル型総ころ軸受を使用したものが考案されている（例えば、特許文献１〜３参照。）。   As a conventional universal joint, one using a shell-type full roller bearing with a bottom has been devised (for example, see Patent Documents 1 to 3).

例えば、図９に示すように、ユニバーサルジョイントは、各々二股アーム５１を有する一対のヨーク５０（片側のみ図示）と、これらヨーク５０を傾動自在に連結する十字型のスパイダ６０とを有する。ヨーク５０の各アーム５１の先端には軸受孔５２が設けられ、スパイダ６０には、中央のブロック６５から互いに直交する方向に一対の軸部６１、６２が突設されている。そして、それらスパイダ６０の軸部６１、６２がそれぞれアーム５１の軸受孔５２内に挿入されると共に、各軸受孔５２内に固定された底付きの軸受１１０によって回転自在に支持されている。   For example, as shown in FIG. 9, the universal joint has a pair of yokes 50 (only one side is shown) each having a bifurcated arm 51 and a cross-shaped spider 60 that connects the yokes 50 so as to be tiltable. A bearing hole 52 is provided at the tip of each arm 51 of the yoke 50, and a pair of shaft portions 61, 62 project from the central block 65 in a direction orthogonal to each other. The shaft portions 61 and 62 of the spiders 60 are inserted into the bearing holes 52 of the arms 51, respectively, and are rotatably supported by bearings 110 with bottoms fixed in the bearing holes 52.

この場合の軸受１１０として使用されるシェル型総ころ軸受は、一端が開口し他端が塞がれた有底筒状のシェル型の外輪１１１と、この外輪１１１の内周に転動自在に配列された多数のころ１１２とを有する。外輪１１１は、底壁１１３と周壁１１５とを有し、外輪１１１の開口側の周壁１１５の端部を、内周方向に約９０度に折り曲げることでフランジ部１１６を形成し、このフランジ部１１６でころ１１２を抜け止めしている。   The shell-type full complement roller bearing used as the bearing 110 in this case has a bottomed cylindrical shell-shaped outer ring 111 that is open at one end and closed at the other end, and can freely roll on the inner periphery of the outer ring 111. It has a large number of rollers 112 arranged. The outer ring 111 has a bottom wall 113 and a peripheral wall 115, and a flange portion 116 is formed by bending an end portion of the peripheral wall 115 on the opening side of the outer ring 111 at about 90 degrees in the inner peripheral direction. The roller 112 is retained.

また、図１１に示すように、特許文献３に記載のユニバーサルジョイントに使用されるシェル型総ころ軸受１１０ａでは、有底筒状のシェル型の外輪１１１が、その周壁１１５の開口側の端部１１６ａをストレートに形成する。そして、シール部材１２１を有する環状体１２０はその折り返し部１２０ａをスパイダの軸部６１に設けられた段部６１ｂに係合することで、軸部６１に嵌められる。さらに、軸部６１の外周面に他のシール部材１２２が設けられており、これらシール部材１２１，１２２によって周壁１１５の開口側の端部１１６ａを密封する。   Further, as shown in FIG. 11, in the shell-type full roller bearing 110a used in the universal joint described in Patent Document 3, the bottomed cylindrical shell-type outer ring 111 has an end portion on the opening side of the peripheral wall 115 thereof. 116a is formed straight. The annular body 120 having the seal member 121 is fitted into the shaft portion 61 by engaging the folded portion 120a with a step portion 61b provided in the shaft portion 61 of the spider. Further, another seal member 122 is provided on the outer peripheral surface of the shaft portion 61, and the end portion 116 a on the opening side of the peripheral wall 115 is sealed by these seal members 121 and 122.

さらに、従来のシェル型ころ軸受１１０ｂとして、図１２に示すように、ころ１１２を保持器１３０を用いて保持するものが考案されている（例えば、特許文献４参照。）。また、この外輪１１１の軸方向両端部には、一対の折り返し部１３１が設けられており、折り返し部１３１の端面１３１ａをころ１１２に対向させている。
特開２００４−３６７０１号公報 国際公開第０６／０７９３８１号パンフレット 国際公開第０５／０１２７４７号パンフレット 特開平０６−２６４９３０号公報 Furthermore, as a conventional shell-type roller bearing 110b, as shown in FIG. 12, one that holds a roller 112 using a cage 130 has been devised (see, for example, Patent Document 4). In addition, a pair of folded portions 131 are provided at both axial ends of the outer ring 111, and the end surface 131 a of the folded portion 131 is opposed to the rollers 112.
JP 2004-36701 A International Publication No. 06/077931 Pamphlet International Publication No. 05/012747 Pamphlet Japanese Patent Laid-Open No. 06-264930

ところで、図９に示すように、ユニバーサルジョイントに総ころ軸受１１０を使用した場合、ころ１１２のスキュー時に、ころ１１２にスラスト力が発生し、そのスラスト力が外輪１１１のフランジ部１１６に集中する。例えば、スキュー方向が矢印Ａ方向である場合、矢印Ｂ方向のスラスト力がころ１１２に作用する。スキュー方向は、ユニバーサルジョイントが揺動運動するため、逆の場合もある。このスラスト力は、ユニバーサルジョイントの入力トルクに比例して増加し、ある領域まで増加した場合には、図１０に示すように、外輪１１１のフランジ部１１６の強度が不足して破損するという問題があった。特許文献１〜４に記載のシェル型軸受は、このような問題を何ら考慮しておらず、保持器を有する特許文献４に記載のシェル型軸受では、上記課題すら存在しない。   As shown in FIG. 9, when the full roller bearing 110 is used for the universal joint, a thrust force is generated in the roller 112 when the roller 112 is skewed, and the thrust force is concentrated on the flange portion 116 of the outer ring 111. For example, when the skew direction is the arrow A direction, the thrust force in the arrow B direction acts on the rollers 112. The skew direction may be reversed because the universal joint swings. This thrust force increases in proportion to the input torque of the universal joint. When the thrust force increases to a certain region, there is a problem that the strength of the flange portion 116 of the outer ring 111 is insufficient and breaks as shown in FIG. there were. The shell-type bearings described in Patent Documents 1 to 4 do not consider such problems at all, and the shell-type bearing described in Patent Document 4 having a cage does not have the above-described problem.

本発明は、上述した事情に鑑みてなされたものであり、その目的は、シェル型外輪の破損防止を図り、高入力トルクの要求に対応可能な底付きシェル型総ころ軸受、及び、その軸受を使用したユニバーサルジョイントを提供することにある。   The present invention has been made in view of the above-described circumstances, and an object of the present invention is to prevent damage to the shell-type outer ring and to provide a shell-type full-roller bearing with a bottom that can meet the demand for high input torque, and the bearing. It is to provide a universal joint using.

前述した目的を達成するために、本発明に係る底付きシェル型総ころ軸受は、下記（１）〜（５）を特徴としている。
（１） 一端が開口し他端が塞がれた有底筒状のシェル型の外輪と、該外輪に組み込まれる複数のころと、を有し、前記複数のころが前記外輪の内周面と軸部材の外周面との間で転動自在に配置される底付きシェル型総ころ軸受において、
前記外輪の開口側には、該軸部材の段部によってスラスト方向に位置決めされる状態で前記軸部材の外周面に嵌合されるリングが設けられ、
該リングは、前記ころの軸方向一端面に対向するストッパ部を形成すると共に、その肉厚が前記外輪の肉厚よりも厚く、
前記段部は、前記リングの外径よりも大きいことを特徴とする底付きシェル型総ころ軸受。
（２） 前記リングの外周面には、前記外輪の開口と前記軸部材との隙間を密封するシール部材が嵌合されることを特徴とする（１）に記載の底付きシェル型総ころ軸受。
（３） 前記リングの外周面には段部が設けられており、該段部によって前記シール部材が軸方向に位置決めされることを特徴とする（２）に記載の底付きシェル型総ころ軸受。
（４） 前記リングは、前記外輪の開口側の端部よりも軸方向に延在しており、
前記シール部材は、前記外輪の開口側の端部の内周面と押圧接触する第１シール部と、前記外輪の開口側の端部の外周面と押圧接触する第２シール部と、を有することを特徴とする（２）又は（３）に記載の底付きシェル型総ころ軸受。
（５） 前記外輪の開口側の端部が内方に傾斜していることを特徴とする（１）〜（４）のいずれかに記載の底付きシェル型総ころ軸受。 In order to achieve the above-described object, the bottomed shell type full complement roller bearing according to the present invention is characterized by the following ( 1 ) to ( 5 ).
( 1 ) A bottomed cylindrical shell-shaped outer ring having one end opened and the other end closed, and a plurality of rollers incorporated in the outer ring, wherein the plurality of rollers are inner peripheral surfaces of the outer ring. In a bottomed shell-type full complement roller bearing that is arranged to freely roll between the outer peripheral surface of the shaft member,
On the opening side of the outer ring, a ring that is fitted to the outer peripheral surface of the shaft member in a state of being positioned in the thrust direction by the step portion of the shaft member is provided,
The ring forms a stopper portion facing one end surface in the axial direction of the roller, and the thickness thereof is thicker than the thickness of the outer ring,
The bottomed shell-type full roller bearing, wherein the stepped portion is larger than an outer diameter of the ring.
( 2 ) A bottomed shell-type full roller bearing according to ( 1 ), wherein a seal member that seals a gap between the opening of the outer ring and the shaft member is fitted to the outer peripheral surface of the ring. .
( 3 ) The bottomed shell-type full roller bearing according to ( 2 ), wherein a step is provided on the outer peripheral surface of the ring, and the seal member is positioned in the axial direction by the step. .
( 4 ) The ring extends in an axial direction from an end portion on the opening side of the outer ring,
The seal member includes a first seal portion that is in press contact with an inner peripheral surface of an end portion on the opening side of the outer ring, and a second seal portion that is in press contact with an outer peripheral surface of an end portion on the opening side of the outer ring. ( 2 ) or ( 3 ), a shell-type full roller bearing with a bottom according to ( 2 ) or ( 3 ).
( 5 ) The bottomed shell-type full roller bearing according to any one of ( 1 ) to ( 4 ), wherein an end of the outer ring on the opening side is inclined inward.

（１）の構成のシェル型総ころ軸受によれば、軸部材に嵌合したリングによって、ころのスラスト力を受けるようにしたので、従来の９０度に折り曲げたフランジ部でスラスト力を受ける場合に比べて、大きなスラスト力に耐えることができる。従って、高入力トルクの要求に対応することが可能となる。
（２）の構成のシェル型総ころ軸受によれば、前記リングの外周に、外輪の開口と軸部材の隙間を密封するシール部材を嵌合したので、潤滑条件を良好に維持することができる。
（３）の構成のシェル型総ころ軸受によれば、シール部材の位置決めを確実に行うことができる。
（４）の構成のシェル型総ころ軸受によれば、より確実に軸受内部を密閉することができる。
（５）の構成のシェル型総ころ軸受によれば、外輪をその開口側からユニバーサルジョイントのヨークの軸受孔に容易に嵌合することができる。 According to the shell-type full roller bearing having the configuration of ( 1 ), since the thrust force of the roller is received by the ring fitted to the shaft member, the conventional flange portion bent at 90 degrees receives the thrust force. Can withstand a large thrust force. Therefore, it is possible to meet the demand for high input torque.
According to the shell type full complement roller bearing configured as ( 2 ), since the seal member that seals the gap between the opening of the outer ring and the shaft member is fitted to the outer periphery of the ring, the lubrication condition can be maintained well. .
According to the shell-type full roller bearing having the configuration ( 3 ), the sealing member can be reliably positioned.
According to the shell type full complement roller bearing having the configuration of ( 4 ), the inside of the bearing can be sealed more reliably.
According to the shell-type full roller bearing having the configuration of ( 5 ), the outer ring can be easily fitted into the bearing hole of the universal joint yoke from the opening side.

前述した目的を達成するために、本発明に係るユニバーサルジョイントは、下記（６）を特徴としている。
（６） （１）〜（５）のいずれかに記載の底付きシェル型総ころ軸受と、各々二股アームを有する一対のヨークと、両ヨークを揺動自在に連結する、前記軸部材としての十字型のスパイダと、を有するユニバーサルジョイントにおいて、
前記外輪は前記二股アームの軸受孔に圧入され、前記ころは前記外輪の内周面と前記スパイダの軸部の外周面との間で転動自在に配置されることを特徴とするユニバーサルジョイント。 In order to achieve the above-mentioned object, the universal joint according to the present invention is characterized by the following ( 6 ).
( 6 ) As the shaft member, the bottomed shell-type full roller bearing according to any one of (1) to ( 5 ), a pair of yokes each having a bifurcated arm, and both the yokes are swingably connected. In a universal joint having a cross-shaped spider,
The outer ring is press-fitted into a bearing hole of the bifurcated arm, and the roller is arranged to roll between an inner peripheral surface of the outer ring and an outer peripheral surface of a shaft portion of the spider.

（６）の構成のユニバーサルジョイントによれば、外輪の破損を無くすことができて、高入力トルクの要求に対応することが可能となる。 According to the universal joint having the configuration ( 6 ), it is possible to eliminate the damage of the outer ring and to meet the demand for high input torque.

本発明によれば、シェル型の外輪の破損防止を図ることができ、高入力トルクの要求に対応することが可能になる。   According to the present invention, it is possible to prevent damage to the shell-type outer ring, and it is possible to meet the demand for high input torque.

以下、本発明の各実施形態に係る底付きシェル型総ころ軸受、及びユニバーサルジョイントを図面に基づいて詳細に説明する。   Hereinafter, a bottomed shell-type full roller bearing and a universal joint according to each embodiment of the present invention will be described in detail with reference to the drawings.

＜第１実施形態＞
図１は、第１実施形態の底付きシェル型総ころ軸受を使用したユニバーサルジョイントの一部構成を示す断面図、図２（ａ）は、図１のシェル型総ころ軸受を取り出して示す拡大断面図、図２（ｂ）は（ａ）のＩＩ部拡大図である。 <First Embodiment>
FIG. 1 is a cross-sectional view showing a partial configuration of a universal joint using a shell-type full roller bearing with a bottom according to the first embodiment, and FIG. 2A is an enlarged view showing the shell-type full roller bearing of FIG. Sectional drawing and FIG.2 (b) are the II section enlarged views of (a).

図１に示すように、本実施形態のユニバーサルジョイントは、各々二股アーム５１を有する一対のヨーク５０（片側のみ図示）と、これらヨーク５０を傾動自在に連結する十字型のスパイダ６０と、を有している。ヨーク５０の各アーム５１の先端には軸受孔５２が設けられ、スパイダ６０には、中央のブロック６５から互いに直交する方向に一対の軸部（軸部材）６１、６２が突設されている。そして、スパイダ６０の各軸部６１、６２がそれぞれアーム５１の軸受孔５２内に挿入され、各軸受孔５２とスパイダ６０の軸部６１（６２）との間に、底付きシェル型総ころ軸受１０が設けられ、これら軸受１０により、スパイダ６０の軸部６１（６２）がアーム５１に回転自在に支持されている。   As shown in FIG. 1, the universal joint of the present embodiment includes a pair of yokes 50 (only one side is shown) each having a bifurcated arm 51, and a cross-shaped spider 60 that connects the yokes 50 so as to be tiltable. doing. A bearing hole 52 is provided at the tip of each arm 51 of the yoke 50, and a pair of shaft portions (shaft members) 61 and 62 project from the central block 65 in a direction orthogonal to each other. The shafts 61 and 62 of the spider 60 are inserted into the bearing holes 52 of the arm 51, respectively, and the bottomed shell-type full roller bearing is interposed between the bearing holes 52 and the shaft 61 (62) of the spider 60. 10, and the shaft portion 61 (62) of the spider 60 is rotatably supported by the arm 51 by these bearings 10.

底付きシェル型総ころ軸受１０は、図２に示すように、一端が開口し他端が塞がれた有底筒状のシェル型の外輪１１と、この外輪１１の内周に転動自在に配列された多数のころ１２とを有する。外輪１１は、鋼板を底壁１３と周壁１５とを有するカップ状に絞り加工することで構成されている。外輪１１の周壁１５の開口側の端部には、該端部を内周側に折り返すことにより環状の折り返し部１６が形成され、その環状の折り返し部１６の先端１６ａが、ころ１２の軸方向一端面に対向するストッパ部を形成し、スキュー時にころ１２に作用するスラスト力を受け止める。また、外輪１１の底壁１３の内面外周付近には、ころ１２の他端を軸方向に位置決めする環状凸部１４が設けられている。図において、矢印Ａはスキュー方向、矢印Ｂはスラスト力のかかる方向を示している。スキュー方向はユニバーサルジョイントの揺動方向に応じて逆方向にもなる。   As shown in FIG. 2, the bottomed shell type full complement roller bearing 10 is rollable to a bottomed cylindrical shell-type outer ring 11 having one end opened and the other end closed, and an inner periphery of the outer ring 11. And a large number of rollers 12 arranged in a row. The outer ring 11 is configured by drawing a steel plate into a cup shape having a bottom wall 13 and a peripheral wall 15. At the end of the outer ring 11 on the opening side of the peripheral wall 15, an end portion 16 is formed by turning the end portion back to the inner peripheral side, and the tip 16 a of the end portion 16 is formed in the axial direction of the roller 12. A stopper portion facing one end surface is formed to receive a thrust force acting on the roller 12 during skew. Further, an annular convex portion 14 that positions the other end of the roller 12 in the axial direction is provided near the inner periphery of the bottom wall 13 of the outer ring 11. In the figure, an arrow A indicates a skew direction, and an arrow B indicates a direction in which a thrust force is applied. The skew direction is also reversed depending on the swing direction of the universal joint.

折り返し部１６は、周壁１５の開口側の縁端を約１８０°の角度で折り返すことにより形成されており、図２（ｂ）に示す標準タイプのものでは、折り返し部１６の根元の折り曲げ半径Ｒの大きさが、Ｒ＝０．０５〜０．２０ｍｍの範囲に設定され、それにより、折り返し部１６と周壁１５の内周面との間に隙間１７が確保されている。また、折り返し部１６の板厚Ｔは、周壁１５のものより薄肉に形成されており、折り返し部１６の板厚Ｔに対する折り返し部１６の長さＳは、Ｓ＝３Ｔ〜６Ｔの範囲に設定されている。   The folded portion 16 is formed by folding the edge of the peripheral wall 15 on the opening side at an angle of about 180 °. In the standard type shown in FIG. 2B, the folding radius R at the base of the folded portion 16 is formed. Is set in a range of R = 0.05 to 0.20 mm, whereby a gap 17 is secured between the folded portion 16 and the inner peripheral surface of the peripheral wall 15. Moreover, the plate | board thickness T of the folding | turning part 16 is formed thinner than the thing of the surrounding wall 15, and the length S of the folding | turning part 16 with respect to the board thickness T of the folding | turning part 16 is set to the range of S = 3T-6T. ing.

このように、ころ１２のスラスト力を受ける部分を、従来のフランジ部の代わりに、折り返し部１６にしたことにより、従来よりも大きなスラスト力に耐えることができるようになる。従って、高入力トルクの要求に対応することが可能となる。また、折り返し部１６の寸法を標準タイプに設定することにより、良好なプレス成形性を維持しながら、高い強度を発揮することができる。例えば、シミュレーション解析した結果によれば、従来品よりも、破損箇所において、応力を５０％低減できることが確認できた。   As described above, the portion that receives the thrust force of the roller 12 is the folded portion 16 instead of the conventional flange portion, so that it is possible to withstand a larger thrust force than the conventional one. Therefore, it is possible to meet the demand for high input torque. Moreover, by setting the dimension of the folded portion 16 to the standard type, high strength can be exhibited while maintaining good press formability. For example, according to the result of the simulation analysis, it was confirmed that the stress can be reduced by 50% at the damaged portion as compared with the conventional product.

従って、本実施形態の軸受と従来の軸受を比較した場合、スキュー時のスラスト力に対する強度や外輪１１の剛性については、本実施形態の方が従来品よりも格段に性能を高めることができると言える。また、外輪の加工については、従来品と同様にプレスで行うことができるので、従来品と同等の加工性を維持することができると言える。また、ヨーク５０に対する軸受１０の圧入方向については、従来品の場合、開口側がフランジ部を有しており、強く押せないことから、密閉側からのみの圧入に制限されていたが、本実施形態の軸受の場合は、フランジ部ではなくて折り返し部１６があることにより、外輪１１の開口側の軸方向剛性が格段に高くなるので、密閉側ばかりでなく、開口側からも軸受をヨークに圧入できるというメリットが得られる。   Therefore, when the bearing of this embodiment is compared with the conventional bearing, the present embodiment can significantly improve the performance with respect to the strength against the thrust force at the time of skew and the rigidity of the outer ring 11 than the conventional product. I can say that. Further, since the outer ring can be processed by a press in the same manner as the conventional product, it can be said that the workability equivalent to that of the conventional product can be maintained. In addition, the press-fitting direction of the bearing 10 with respect to the yoke 50 is limited to press-fitting only from the sealed side because the opening side has a flange portion and cannot be pressed strongly in the case of the conventional product. In the case of this bearing, since the folded portion 16 is provided instead of the flange portion, the axial rigidity on the opening side of the outer ring 11 is remarkably increased, so that the bearing is pressed into the yoke not only from the sealed side but also from the opening side. The advantage that you can do it.

なお、折り返し部１６の寸法条件は、図２（ｂ）に示すような標準タイプであることが望ましいが、折り曲げ半径Ｒの大小や、周壁１５に対する折り返し部１６の角度の違いが多少あっても、軸受の機能を損なわない範囲において、自由に変更可能である。   The dimensional condition of the folded portion 16 is preferably a standard type as shown in FIG. 2B, but even if there is a slight difference in the bending radius R and the angle of the folded portion 16 with respect to the peripheral wall 15. The bearing can be freely changed as long as the function of the bearing is not impaired.

例えば、図３（ａ）に示すタイプのものでは、折り曲げ半径Ｒを０．０５未満に小さくしている。このタイプでは、折り曲げ部に対する応力集中が大きくなるため、標準タイプのほうがより高強度である。   For example, in the type shown in FIG. 3A, the bending radius R is made smaller than 0.05. In this type, since the stress concentration on the bent portion is increased, the standard type is stronger.

また、図３（ｂ）に示すタイプのものでは、折り曲げ半径Ｒをゼロにしている。このタイプに比べると、標準タイプのほうがより高強度であり、プレス成形性も良好である。   In the type shown in FIG. 3B, the bending radius R is set to zero. Compared to this type, the standard type has higher strength and better press formability.

また、図３（ｃ）に示すタイプのものでは、折り曲げ半径Ｒを０．２０ｍｍを超える大きさにしている。このタイプでは、折り曲げ部の応力集中は低減できるが、折り曲げ部１６が開きやすくなり、そのために応力が大きくなる傾向がある。   Moreover, in the type shown in FIG.3 (c), the bending radius R is made into the magnitude | size exceeding 0.20 mm. In this type, although the stress concentration at the bent portion can be reduced, the bent portion 16 tends to open, and the stress tends to increase.

また、図３（ｄ）に示すタイプのものでは、周壁１５の先端を１８０°よりも小さい角度（例えば、１５０°〜１７０°）だけ折り返すことで、傾き角度の付いた状態で折り返し部１６を形成している。この場合、折り曲げ部１６が開きやすくなり、そのために応力が大きくなる傾向がある。   Further, in the type shown in FIG. 3 (d), the folded portion 16 can be folded with an inclination angle by folding the tip of the peripheral wall 15 by an angle smaller than 180 ° (for example, 150 ° to 170 °). Forming. In this case, the bent portion 16 is easy to open, and the stress tends to increase.

＜第２実施形態＞
図４は第２実施形態の底付きシェル型総ころ軸受を使用したユニバーサルジョイントの一部構成を示す断面図、図５は図４のシェル型総ころ軸受を取り出して示す拡大断面図である。なお、第１実施形態と同一または同等部分については、同一符号を付して説明を省略或いは簡略化する。 Second Embodiment
FIG. 4 is a cross-sectional view showing a partial configuration of a universal joint using the bottomed shell-type full roller bearing of the second embodiment, and FIG. 5 is an enlarged cross-sectional view showing the shell-type full roller bearing of FIG. Note that portions that are the same as or equivalent to those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted or simplified.

図４に示すユニバーサルジョイントでは、アーム５１の各軸受孔５２とスパイダ６０の軸部６１（６２）との間に、底付きシェル型総ころ軸受２０が設けられており、これら軸受２０により、スパイダ６０の軸部６１（６２）がアーム５１に回転自在に支持されている。   In the universal joint shown in FIG. 4, a shell-type full roller bearing 20 with a bottom is provided between each bearing hole 52 of the arm 51 and the shaft portion 61 (62) of the spider 60. 60 shaft portions 61 (62) are rotatably supported by the arm 51.

底付きシェル型総ころ軸受２０は、図５に示すように、一端が開口し他端が塞がれた有底筒状のシェル型の外輪２１と、この外輪２１の内周に転動自在に配列された多数のころ１２とを有するもので、外輪２１は、鋼板を底壁２３と周壁２５とを有するカップ状に絞り加工することで構成されている。外輪２１の周壁２５の開口側の端部２６はフランジ部は形成されず、略肉厚一様でストレートに延びている。また、外輪２１の底壁２３の内面外周付近には、ころ１２の他端を軸方向に位置決めする環状凸部２４が設けられている。   As shown in FIG. 5, the bottomed shell-type full complement roller bearing 20 is rollable to a bottomed cylindrical shell-type outer ring 21 having one end opened and the other end closed, and an inner periphery of the outer ring 21. The outer ring 21 is formed by drawing a steel plate into a cup shape having a bottom wall 23 and a peripheral wall 25. The end portion 26 on the opening side of the peripheral wall 25 of the outer ring 21 is not formed with a flange portion, and has a substantially uniform thickness and extends straight. An annular convex portion 24 that positions the other end of the roller 12 in the axial direction is provided near the inner periphery of the bottom wall 23 of the outer ring 21.

外輪２１の開口側には、軸部６１とブロック６５の境界の段部６６によってスラスト方向に位置決めされる状態で、スパイダ６０の軸部６１の外周面にリング２７が嵌合される。これにより、リング２７の端面が、ころ１２の軸方向一端面に対向するストッパ部を形成し、スキュー時にころ１２に作用するスラスト力を受け止める。また、リング２７の外周面には、外輪２１の開口とスパイダの軸部６１との隙間を密封するシール部材２８が嵌合されており、外輪２１の開口側の端部２６の内周面を押圧接触する。   On the opening side of the outer ring 21, the ring 27 is fitted to the outer peripheral surface of the shaft portion 61 of the spider 60 in a state positioned in the thrust direction by the step portion 66 at the boundary between the shaft portion 61 and the block 65. As a result, the end surface of the ring 27 forms a stopper portion facing the one end surface in the axial direction of the roller 12, and receives the thrust force acting on the roller 12 during skew. A seal member 28 that seals a gap between the opening of the outer ring 21 and the spider shaft 61 is fitted to the outer peripheral surface of the ring 27, and the inner peripheral surface of the end 26 on the opening side of the outer ring 21 is fitted. Press contact.

このように、スパイダ６０の軸部６１に嵌合したリング２７によって、ころ１２のスラスト力を受けるようにしているので、従来の９０度に折り曲げたフランジ部でスラスト力を受ける場合に比べて、大きなスラスト力に耐えることができる。従って、高入力トルクの要求に対応することが可能となる。また、リング２７の外周に、外輪２１の開口とスパイダ６０の軸部６１の隙間を密封するシール部材２８を嵌合したので、ころ１２が転動する領域の潤滑条件を良好に維持することができる。   Thus, since the ring 27 fitted to the shaft portion 61 of the spider 60 is adapted to receive the thrust force of the roller 12, compared with the case where the conventional flange portion bent at 90 degrees receives the thrust force. Can withstand large thrust forces. Therefore, it is possible to meet the demand for high input torque. In addition, since the seal member 28 that seals the gap between the opening of the outer ring 21 and the shaft portion 61 of the spider 60 is fitted to the outer periphery of the ring 27, it is possible to maintain good lubrication conditions in the region where the roller 12 rolls. it can.

＜第３実施形態＞
図６は、ユニバーサルジョイントに使用される第３実施形態の底付きシェル型総ころ軸受を示す拡大断面図である。この実施形態では、シェル型総ころ軸受２０Ｂの外輪２１の開口側の端部２６を、内方に僅かに傾斜させている。傾斜角度は、シール部材２８を傷つけない範囲であればよい。このようにすることで、外輪２１をヨーク５０の軸受孔５２に組み込むときの組み込み性を向上させることができる。
なお、その他の構成については第２実施形態と同様であり、第２実施形態と同一または同等部分については、同一符号を付して説明を省略或いは簡略化する。 <Third Embodiment>
FIG. 6 is an enlarged cross-sectional view showing a bottomed shell-type full roller bearing of a third embodiment used for a universal joint. In this embodiment, the end 26 on the opening side of the outer ring 21 of the shell-type full roller bearing 20B is slightly inclined inward. The inclination angle may be in a range that does not damage the seal member 28. By doing so, it is possible to improve the assemblability when the outer ring 21 is incorporated into the bearing hole 52 of the yoke 50.
In addition, about another structure, it is the same as that of 2nd Embodiment, About the same or equivalent part as 2nd Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

＜第４実施形態＞
図７は、ユニバーサルジョイントに使用される第４実施形態のシェル型総ころ軸受を示す拡大断面図である。この実施形態では、シェル型総ころ軸受２０Ｃのリング２７の外周に段部２７ａを設け、その段部２７ａによってシール部材２８が軸方向に位置決めされる。従って、シール部材２８の位置決めを確実に行うことができる。
なお、その他の構成については第２実施形態と同様であり、第２実施形態と同一または同等部分については、同一符号を付して説明を省略或いは簡略化する。 <Fourth embodiment>
FIG. 7 is an enlarged sectional view showing a shell-type full roller bearing of a fourth embodiment used for a universal joint. In this embodiment, a step portion 27a is provided on the outer periphery of the ring 27 of the shell-type full roller bearing 20C, and the seal member 28 is positioned in the axial direction by the step portion 27a. Therefore, the sealing member 28 can be positioned reliably.
In addition, about another structure, it is the same as that of 2nd Embodiment, About the same or equivalent part as 2nd Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

＜第５実施形態＞
図８は、ユニバーサルジョイントに使用される第５実施形態のシェル型総ころ軸受を示す拡大断面図である。この実施形態では、シェル型総ころ軸受２０Ｄのシール部材２９に、外輪２１の周壁２５の開口側の端部２６の内周面に押圧接触する第１シール部２９ａと、外輪２１の周壁２５の開口側の端部２６の外周面に押圧接触する第２シール部２９ｂとを設けている。これにより、より確実にころ１２が転動する領域を密閉することができる。
なお、その他の構成については第２実施形態と同様であり、第２実施形態と同一または同等部分については、同一符号を付して説明を省略或いは簡略化する。 <Fifth Embodiment>
FIG. 8 is an enlarged sectional view showing a shell-type full roller bearing of a fifth embodiment used for a universal joint. In this embodiment, the seal member 29 of the shell-type full roller bearing 20 </ b> D is pressed against the inner peripheral surface of the end portion 26 on the opening side of the peripheral wall 25 of the outer ring 21, and the peripheral wall 25 of the outer ring 21. A second seal portion 29b is provided in pressure contact with the outer peripheral surface of the opening-side end portion. Thereby, the area | region where the roller 12 rolls more reliably can be sealed.
In addition, about another structure, it is the same as that of 2nd Embodiment, About the same or equivalent part as 2nd Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

尚、本発明は、上述した実施形態に限定されるものではなく、適宜、変形、改良、等が可能である。例えば、上述した実施形態は、実施可能な範囲において、任意に組み合わせて構成してもよい。   In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. For example, the above-described embodiments may be arbitrarily combined within the practicable range.

本発明の第１実施形態のシェル型総ころ軸受を使用したユニバーサルジョイントの一部構成を示す断面図である。It is sectional drawing which shows a partial structure of the universal joint which uses the shell type full roller bearing of 1st Embodiment of this invention. （ａ）は図１のシェル型総ころ軸受だけを取り出して示す拡大断面図であり、（ｂ）は(ａ)のＩＩ部の拡大図である。(A) is an enlarged sectional view showing only the shell-type full roller bearing of FIG. 1, and (b) is an enlarged view of the II part of (a). （ａ）〜（ｄ）は、図２（ｂ）と同部分のその他の例を示す図である。(A)-(d) is a figure which shows the other example of the same part as FIG.2 (b). 本発明の第２実施形態のシェル型総ころ軸受を使用したユニバーサルジョイントの一部構成を示す断面図である。It is sectional drawing which shows a partial structure of the universal joint which uses the shell type full roller bearing of 2nd Embodiment of this invention. 図４のシェル型総ころ軸受周辺の拡大断面図である。FIG. 5 is an enlarged cross-sectional view around the shell-type full roller bearing of FIG. 4. 本発明の第３実施形態のシェル型総ころ軸受を使用したユニバーサルジョイントの図５と同様の部分を示す拡大図である。It is an enlarged view which shows the part similar to FIG. 5 of the universal joint which uses the shell type full roller bearing of 3rd Embodiment of this invention. 本発明の第４実施形態のシェル型総ころ軸受を使用したユニバーサルジョイントの図５と同様の部分を示す拡大図である。It is an enlarged view which shows the part similar to FIG. 5 of the universal joint which uses the shell type full roller bearing of 4th Embodiment of this invention. 本発明の第５実施形態のシェル型総ころ軸受を使用したユニバーサルジョイントの図５と同様の部分を示す拡大図である。It is an enlarged view which shows the part similar to FIG. 5 of the universal joint which uses the shell type full roller bearing of 5th Embodiment of this invention. 従来のユニバーサルジョイントの一部構成を示す断面図である。It is sectional drawing which shows a partial structure of the conventional universal joint. 図９のユニバーサルジョイントにおける軸受の破損時の状態を示す部分拡大図である。FIG. 10 is a partially enlarged view showing a state when the bearing in the universal joint of FIG. 9 is broken. 他の従来のユニバーサルジョイントに使用される軸受の拡大断面図である。It is an expanded sectional view of the bearing used for another conventional universal joint. さらに他の従来のシェル型ころ軸受を示す断面図である。It is sectional drawing which shows the other conventional shell type roller bearing.

符号の説明Explanation of symbols

１０ シェル型総ころ軸受
１１ 外輪
１２ ころ
１５ 周壁
１６ 折り返し部
２０，２０Ｂ，２０Ｃ，２０Ｄ シェル型総ころ軸受
２７ リング
２７ａ 段部
２８，２９ シール部材
２９ａ 第１シール部
２９ｂ 第２シール部
５０ ヨーク
５１ アーム
５２ 軸受孔
６０ スパイダ
６１，６２ 軸部（軸部材）
６６ 段部 DESCRIPTION OF SYMBOLS 10 Shell type full roller bearing 11 Outer ring 12 Roller 15 Perimeter wall 16 Folding part 20, 20B, 20C, 20D Shell type full roller bearing 27 Ring 27a Step part 28, 29 Seal member 29a First seal part 29b Second seal part 50 Yoke 51 Arm 52 Bearing hole 60 Spider 61, 62 Shaft (shaft member)
66 steps

Claims (6)

一端が開口し他端が塞がれた有底筒状のシェル型の外輪と、該外輪に組み込まれる複数のころと、を有し、前記複数のころが前記外輪の内周面と軸部材の外周面との間で転動自在に配置される底付きシェル型総ころ軸受において、
前記外輪の開口側には、該軸部材の段部によってスラスト方向に位置決めされる状態で前記軸部材の外周面に嵌合されるリングが設けられ、
該リングは、前記ころの軸方向一端面に対向するストッパ部を形成すると共に、その肉厚が前記外輪の肉厚よりも厚く、
前記段部は、前記リングの外径よりも大きいことを特徴とする底付きシェル型総ころ軸受。 A bottomed cylindrical shell-shaped outer ring having one end opened and the other end closed, and a plurality of rollers incorporated in the outer ring, the plurality of rollers being an inner peripheral surface of the outer ring and a shaft member In a bottomed shell-type full roller bearing that is arranged so as to freely roll between the outer peripheral surface of
On the opening side of the outer ring, a ring that is fitted to the outer peripheral surface of the shaft member in a state of being positioned in the thrust direction by the step portion of the shaft member is provided,
The ring forms a stopper portion facing one end surface in the axial direction of the roller, and the thickness thereof is thicker than the thickness of the outer ring,
The bottomed shell-type full roller bearing, wherein the stepped portion is larger than an outer diameter of the ring. 前記リングの外周面には、前記外輪の開口と前記軸部材との隙間を密封するシール部材が嵌合されることを特徴とする請求項１に記載の底付きシェル型総ころ軸受。 2. The bottomed shell-type full roller bearing according to claim 1 , wherein a seal member that seals a gap between the opening of the outer ring and the shaft member is fitted to the outer peripheral surface of the ring. 前記リングの外周面には段部が設けられており、該段部によって前記シール部材が軸方向に位置決めされることを特徴とする請求項２に記載の底付きシェル型総ころ軸受。 The bottomed shell-type full roller bearing according to claim 2 , wherein a step portion is provided on an outer peripheral surface of the ring, and the seal member is positioned in the axial direction by the step portion. 前記リングは、前記外輪の開口側の端部よりも軸方向に延在しており、
前記シール部材は、前記外輪の開口側の端部の内周面と押圧接触する第１シール部と、前記外輪の開口側の端部の外周面と押圧接触する第２シール部と、を有することを特徴とする請求項２又は３に記載の底付きシェル型総ころ軸受。 The ring extends in an axial direction from an end portion on the opening side of the outer ring,
The seal member includes a first seal portion that is in press contact with an inner peripheral surface of an end portion on the opening side of the outer ring, and a second seal portion that is in press contact with an outer peripheral surface of an end portion on the opening side of the outer ring. The bottomed shell-type full roller bearing according to claim 2 or 3 , 前記外輪の開口側の端部が内方に傾斜していることを特徴とする請求項１〜４のいずれかに記載の底付きシェル型総ころ軸受。 The bottomed shell-type full roller bearing according to any one of claims 1 to 4 , wherein an end of the outer ring on the opening side is inclined inward. 請求項１〜５のいずれかに記載の底付きシェル型総ころ軸受と、各々二股アームを有する一対のヨークと、両ヨークを揺動自在に連結する、前記軸部材としての十字型のスパイダと、を有するユニバーサルジョイントにおいて、
前記外輪は前記二股アームの軸受孔に圧入され、前記ころは前記外輪の内周面と前記スパイダの軸部の外周面との間で転動自在に配置されることを特徴とするユニバーサルジョイント。 A bottomed shell-type full roller bearing according to any one of claims 1 to 5 , a pair of yokes each having a bifurcated arm, and a cruciform spider as the shaft member that slidably connects the two yokes. In a universal joint having
The outer ring is press-fitted into a bearing hole of the bifurcated arm, and the roller is arranged to roll between an inner peripheral surface of the outer ring and an outer peripheral surface of a shaft portion of the spider.
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