JP3905283B2 - Rotating shaft support structure - Google Patents

Rotating shaft support structure Download PDF

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Publication number
JP3905283B2
JP3905283B2 JP2000122523A JP2000122523A JP3905283B2 JP 3905283 B2 JP3905283 B2 JP 3905283B2 JP 2000122523 A JP2000122523 A JP 2000122523A JP 2000122523 A JP2000122523 A JP 2000122523A JP 3905283 B2 JP3905283 B2 JP 3905283B2
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Prior art keywords
ball
curvature
raceway
groove
radius
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JP2001304273A (en
Inventor
孝 岩田
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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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F16C19/166—Four-point-contact ball bearings
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/76—Osculation, i.e. relation between radii of balls and raceway groove

Description

【０００１】
【発明の属する技術分野】
この発明は、耐モーメント荷重性やモーメント剛性が優れた軽量でコンパクトな４点接触玉軸受を有する回転軸支持構造に関する。
【０００２】
【従来の技術】
自動車用エアコンディショナーで使用される電磁クラッチ用軸受あるいはプーリ用軸受には、耐モーメント荷重性やモーメント剛性が要求されるので、単列深溝玉軸受を採用できず、内,外輪一体タイプの複列斜接玉軸受が使用されている。
【０００３】
【発明が解決しようとする課題】
ところが、近年、周辺部品の設計自由度や軽量化,コストダウンの要求が強く、軸受を単列化する必要性が生じている。
【０００４】
しかし、通常の単列軸受では、上述のような厳しい条件では、使用できなかった。
【０００５】
そこで、この発明の目的は、耐モーメント荷重性やモーメント剛性が優れ、耐剥離性,耐焼付き性も優れた４点接触玉軸受を有する回転軸支持構造を提供することにある。
【０００６】
【課題を解決するための手段】
上記目的を達成するため、この発明の回転軸支持構造は、単列の玉軸受でモーメント荷重を含む荷重を支持する回転軸支持構造であって、
上記玉軸受は、
玉の中心の軸方向位置から軸方向の両側に延在する軌道溝を有する内輪と、上記玉の中心の軸方向位置から軸方向の両側に延在する軌道溝を有する外輪とを有する４点接触玉軸受であり、
上記内輪の軌道溝の軌道面の溝曲率半径を玉径の５２〜５３.５％とし、
上記外輪の軌道溝の軌道面の溝曲率半径を玉径の５３.５〜５６％とし、
かつ、上記内輪の軌道溝の軌道面の溝曲率半径を上記外輪の軌道溝の軌道面の溝曲率半径よりも小さくして、上記内輪の軌道溝の面圧と上記外輪の軌道溝の面圧とをバランスさせることを特徴としている。
【０００７】
この発明の回転軸支持構造では、４点接触玉軸受の内(外)輪の溝曲率半径を玉径の５２(５３.５)％以上にしたから、玉の肩乗り上げや焼付き寿命の低下を招くことがなく、内(外)輪の溝曲率半径を玉径の５３.５(５６)％以下としたから、剥離寿命やモーメント剛性を確保できる。これに対し、内(外)輪の溝曲率半径を玉径の５２(５３.５)％未満にすると、玉と内,外輪との接触楕円が大となり、差動すべりが大となって、発熱が大きくなったり、軌道溝からの離脱、いわゆる肩乗り上げが発生する。
【０００８】
また、一実施形態では、接触角を２０°以上にしたから、モーメント剛性の低下を招くことが無く、接触角を３０°以下にしたから、玉のスピンに起因する発熱や玉の肩乗り上げの問題を回避できる。これに対し、接触角が２０°を下回ると、アキシャルガタが大きくなって、モーメント剛性が小さくなる一方、接触角が３０°を上回ると、玉のスピンが増加して、発熱が大きくなる。
【０００９】
また、内輪の軌道面の溝曲率半径を５２〜５３.５Ｂｄ％(Ｂｄ％は玉の直径に対する百分率)として、外輪の軌道面の溝曲率半径(５３.５〜５６Ｂｄ％)よりも小さくしたから、内輪の軌道面の面圧と外輪の軌道面の面圧とをバランスさせて、剥離寿命の向上を図ることができる。なお、内輪の軌道面は、軸直角面で切断した断面が玉に対して凸であるのに対し、外輪の軌道面は、軸直角面で切断した断面が玉に対して凹であるから、外輪の溝曲率半径と内輪の溝曲率半径とを同じにすると、外輪よりも内輪の面圧の方が大きくなって、面圧がアンバランスになって、寿命が低下する。
【００１０】
したがって、この発明によれば、耐モーメント荷重性やモーメント剛性が優れ、耐剥離性,耐焼付き性も優れた４点接触玉軸受を有する回転軸支持構造を実現できる。
【００１１】
【発明の実施の形態】
以下、この発明を図示の実施の形態により詳細に説明する。
【００１２】
図１に、この発明の回転軸支持構造が有する４点接触玉軸受の実施形態の断面を示す。この実施形態は、内輪１と外輪２の間に複数の玉３が周方向に所定の間隔を隔てて配列されており、この玉３は保持器５で保持されている。外輪２の軸方向の両端部にはシール部材６が固定され、このシール部材６のシールリップ７は内輪１の軸方向両端に形成された窪みに摺接している。
【００１３】
内輪１は軌道溝１１を有し、この軌道溝１１は、玉３の中心Ｐ0から所定寸法(例えば、玉３の直径Ｂｄの１％)だけ軸方向の両側へ位置ずれした２つの曲率中心Ｐ11,Ｐ12を有している。図１において、右方へ位置ずれした曲率中心Ｐ12は、図１において、玉中心Ｐ0の左方の軌道溝１１Ｂの軌道面の曲率中心であり、左方へ位置ずれした曲率中心Ｐ11は、図において、玉中心Ｐ0の右方の軌道溝１１Ａの軌道面の曲率中心である。また、上記軌道溝１１Ａ,１１Ｂの曲率半径Ｒ１は、玉３の直径Ｂｄの５３.０％とした。そして、この玉３と軌道溝１１Ａとの接触角θ2を２５°とし、玉３と軌道溝１１Ｂとの接触角θ2を２５°とした。
【００１４】
また、外輪２は、軌道溝１２を有し、この軌道溝１２は、玉３の中心Ｐ0から所定寸法(例えば、玉３の直径Ｂｄの１％)だけ軸方向の両側へ位置ずれした２つの曲率中心Ｐ21,Ｐ22を有している。図１において、右方へ位置ずれした曲率中心Ｐ22は、図１において、玉中心Ｐ0の左方の軌道溝１２Ｂの軌道面の曲率中心であり、左方へ位置ずれした曲率中心Ｐ21は、図において、玉中心Ｐ0の右方の軌道溝１２Ａの軌道面の曲率中心である。また、上記軌道溝１２Ａ,１２Ｂの曲率半径Ｒ２は、玉３の直径Ｂｄの５５.０％とした。そして、この玉３と軌道溝１２Ａとの接触角θ1を２５°とし、玉３と軌道溝１２Ｂとの接触角θ1を２５°とした。
【００１５】
この実施形態の４点接触玉軸受によれば、内輪１の溝曲率半径Ｒ１を５３.０Ｂｄ％(５２Ｂｄ％以上で５３.５Ｂｄ％以下)にし、外輪２の溝曲率半径Ｒ２を５５.０Ｂｄ％(５３.５Ｂｄ％以上で５６Ｂｄ％以下)にした。これにより、玉３の肩乗り上げや焼付き寿命の低下を招くことなく、剥離寿命やモーメント剛性を確保できる。なお、内(外)輪１(２)の溝曲率半径Ｒ１(Ｒ２)を５２(５３.５)％Ｂｄ未満にすると、玉３と内,外輪１,２との接触楕円が大となり、作動すべりが大となって、発熱が大きくなったり肩乗り上げが発生する。
【００１６】
また、軌道溝１１の軌道溝１１Ａ,１１Ｂと玉３との接触角θ2を２５°(２０°〜３０°)とし、軌道溝１２の軌道溝１２Ａ,１２Ｂと玉３との接触角θ1を２５°としたから、モーメント剛性の低下を招くこと無く、玉３のスピンに起因する発熱や玉３の肩乗り上げの問題を回避できる。なお、接触角θ1,θ2が２０°を下回ると、アキシャルガタが大きくなって、モーメント剛性も小さくなる一方、接触角θ1,θ2が３０°を上回ると、玉３のスピンが増加して、発熱が大きくなる。
【００１７】
また、内輪１の軌道溝１１Ａ,１１Ｂの溝曲率半径Ｒ１(５３.０Ｂｄ％)を外輪２の軌道溝１２Ａ,１２Ｂの溝曲率半径(５５Ｂｄ％)よりも小さくしたから、内輪１の軌道溝１１Ａ,１１Ｂの面圧と外輪２の軌道溝１２Ａ,１２Ｂの面圧とをバランスさせて、剥離寿命を向上を図ることができる。なお、内輪１の軌道溝１１は、軸直角面で切断した断面が玉３に対して凸であるのに対し、外輪２の軌道溝１２は、軸直角面で切断した断面が玉３に対して凹である。このため、外輪２の溝曲率半径Ｒ２と内輪１の溝曲率半径Ｒ１とを同じにすると、外輪２よりも内輪１の面圧の方が大きくなって、面圧がアンバランスになって、寿命が低下する。
【００１８】
上記説明したように、この実施形態によれば、耐モーメント荷重性やモーメント剛性が優れ、耐剥離性や耐焼付き性も優れた４点接触玉軸受を有する回転軸支持構造を実現できる。
【００１９】
尚、上記実施形態では、内輪１の軌道溝１１の曲率半径を玉の直径の５３％としたが、５２〜５３.５％の範囲内に設定すれば、上述の効果が得られる。また、外輪２の軌道溝１２の曲率半径を玉の直径の５３.５％〜５６％の範囲内に設定すれば、同様の効果を得ることができる。
【００２０】
【発明の効果】
以上より明らかなように、この発明の回転軸支持構造の４点接触玉軸受は、内(外)輪の溝曲率半径を５２(５３.５)Ｂｄ％以上にしたから、玉の肩乗り上げや焼付き寿命の低下を招くことがなく、内(外)輪の溝曲率半径を５３.５(５６)Ｂｄ％以下としたから、剥離寿命やモーメント剛性を確保できる。
【００２１】
また、一実施形態では、接触角を２０°以上にしたから、モーメント剛性の低下を招くことが無く、接触角を３０°以下にしたから、玉のスピンに起因する発熱や玉の肩乗り上げの問題を回避できる。
【００２２】
また、内輪の軌道面の溝曲率半径(５２〜５３.５Ｂｄ％)を外輪の軌道面の溝曲率半径(５３.５〜５６Ｂｄ％)よりも小さくしたから、内輪の軌道面の面圧と外輪の軌道面の面圧とをバランスさせて、剥離寿命を向上を図ることができる。
【００２３】
したがって、この発明によれば、耐モーメント荷重性やモーメント剛性が優れ、耐剥離性や耐焼付き性が優れた４点接触玉軸受を有する回転軸支持構造を実現できる。
【図面の簡単な説明】
【図１】 この発明の４点接触玉軸受を有する回転軸支持構造の実施の形態の断面図である。
【符号の説明】
１…内輪、２…外輪、３…玉、５…保持器、６…シール部材、
７…シールリップ、１１,１２…軌道溝、
Ｐ0…玉中心、Ｐ11,Ｐ12,Ｐ21,Ｐ22…曲率中心、θ1,θ2…接触角。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a rotating shaft support structure having a lightweight and compact four-point contact ball bearing having excellent moment load resistance and moment rigidity.
[0002]
[Prior art]
Bearings for electromagnetic clutches or pulleys used in automotive air conditioners require moment load resistance and moment rigidity, so single row deep groove ball bearings cannot be used. Oblique contact ball bearings are used.
[0003]
[Problems to be solved by the invention]
However, in recent years, there are strong demands for design freedom, weight reduction, and cost reduction of peripheral parts, and there is a need for a single row bearing.
[0004]
However, ordinary single row bearings could not be used under the severe conditions described above.
[0005]
SUMMARY OF THE INVENTION An object of the present invention is to provide a rotating shaft support structure having a four-point contact ball bearing that is excellent in moment load resistance and moment rigidity, and excellent in peeling resistance and seizure resistance.
[0006]
[Means for Solving the Problems]
To achieve the above object, the rotating shaft support structure of the present invention is a rotating shaft support structure that supports a load including a moment load with a single row ball bearing,
The above ball bearing
Four points having an inner ring having a raceway groove extending from the axial position at the center of the ball to both sides in the axial direction and an outer ring having a raceway groove extending from the axial position at the center of the ball to both sides in the axial direction Contact ball bearings,
The radius of curvature of the raceway surface of the raceway groove of the inner ring is 52-53.5% of the ball diameter,
The radius of curvature of the raceway surface of the raceway groove of the outer ring is 53.5 to 56% of the ball diameter,
Further, the groove radius of curvature of the raceway surface of the inner ring raceway groove is made smaller than the radius of curvature of the raceway surface of the raceway groove of the outer ring, and the surface pressure of the raceway groove of the inner ring and the surface pressure of the raceway groove of the outer ring. It is characterized by balancing .
[0007]
In the rotary shaft support structure of the present invention, the groove radius of curvature of the inner (outer) ring of the four-point contact ball bearing is set to 52 (53.5)% or more of the ball diameter, so that the ball rides on the shoulder and the seizure life is reduced. Since the groove radius of curvature of the inner (outer) ring is 53.5 (56)% or less of the ball diameter, the peeling life and moment rigidity can be secured. On the other hand, if the groove radius of curvature of the inner (outer) ring is less than 52 (53.5)% of the ball diameter, the contact ellipse between the ball and the inner and outer rings becomes large, and the differential slip becomes large. Heat generation becomes large and separation from the raceway groove, so-called shoulder climbing, occurs.
[0008]
In one embodiment, since the contact angle is set to 20 ° or more, the moment rigidity is not reduced, and the contact angle is set to 30 ° or less. The problem can be avoided. On the other hand, when the contact angle is less than 20 °, the axial backlash is increased and the moment rigidity is reduced. On the other hand, when the contact angle is more than 30 °, the spin of the ball is increased and the heat generation is increased.
[0009]
Also, the groove radius of curvature of the inner ring raceway surface is 52-53.5 Bd% (Bd% is a percentage of the ball diameter), which is smaller than the groove radius of curvature of the outer ring raceway surface (53.5-56 Bd%). It is possible to improve the peeling life by balancing the surface pressure of the raceway surface of the inner ring and the surface pressure of the raceway surface of the outer ring. In addition, the raceway surface of the inner ring is convex with respect to the ball, and the cross section cut along the plane perpendicular to the axis is convex with respect to the ball. If the groove radius of curvature of the outer ring and the groove radius of curvature of the inner ring are the same, the surface pressure of the inner ring becomes larger than that of the outer ring, the surface pressure becomes unbalanced, and the life is shortened.
[0010]
Therefore, according to the present invention, it is possible to realize a rotating shaft support structure having a four-point contact ball bearing that is excellent in moment load resistance and moment rigidity, and excellent in peeling resistance and seizure resistance.
[0011]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.
[0012]
FIG. 1 shows a cross section of an embodiment of a four-point contact ball bearing included in the rotating shaft support structure of the present invention. In this embodiment, a plurality of balls 3 are arranged at a predetermined interval in the circumferential direction between the inner ring 1 and the outer ring 2, and the balls 3 are held by a cage 5. Seal members 6 are fixed to both ends of the outer ring 2 in the axial direction, and seal lips 7 of the seal member 6 are in sliding contact with recesses formed at both ends of the inner ring 1 in the axial direction.
[0013]
The inner ring 1 has a raceway groove 11, and this raceway groove 11 has two curvature centers that are displaced from the center P 0 of the ball 3 to both sides in the axial direction by a predetermined dimension (for example, 1% of the diameter Bd of the ball 3). P 11 and P 12 are included. In FIG. 1, the center of curvature P 12 displaced to the right is the center of curvature of the track surface of the track groove 11B on the left side of the ball center P 0 in FIG. 1, and the center of curvature P 11 displaced to the left. , in the figure, a center of curvature of the raceway surface of the raceway groove 11A of the right side of the ball center P 0. Further, the radius of curvature R1 of the raceway grooves 11A and 11B is 53.0% of the diameter Bd of the ball 3. Then, the balls 3 and the contact angle theta 2 between the raceway grooves 11A was a 25 °, the contact angle theta 2 between the balls 3 and the raceway groove 11B was 25 °.
[0014]
Further, the outer ring 2 has a raceway groove 12, the raceway grooves 12, a predetermined dimension from the center P 0 of the balls 3 (e.g., 1% of the diameter Bd of the balls 3) misaligned to only the axial direction on both sides 2 It has two curvature centers P 21 and P 22 . In FIG. 1, the center of curvature P 22 displaced to the right is the center of curvature of the track surface of the track groove 12B on the left of the ball center P 0 in FIG. 1, and the center of curvature P 21 displaced to the left. , in the figure, a center of curvature of the raceway surface of the raceway groove 12A of the right side of the ball center P 0. The radius of curvature R2 of the raceway grooves 12A and 12B was 55.0% of the diameter Bd of the ball 3. Then, the contact angle theta 1 between the balls 3 and the raceway groove 12A and 25 °, the contact angle theta 1 between the ball 3 and the raceway groove 12B was 25 °.
[0015]
According to the four-point contact ball bearing of this embodiment, the groove curvature radius R1 of the inner ring 1 is 53.0 Bd% (52 Bd% or more and 53.5 Bd% or less), and the groove curvature radius R2 of the outer ring 2 is 55.0 Bd%. (53.5 Bd% or more and 56 Bd% or less). Thereby, the peeling life and moment rigidity can be ensured without causing the ball 3 to ride on the shoulder and the seizure life to decrease. If the groove curvature radius R1 (R2) of the inner (outer) ring 1 (2) is less than 52 (53.5)% Bd, the contact ellipse between the ball 3 and the inner and outer rings 1, 2 becomes large, and the operation Slip becomes large, fever increases, and shoulder climbing occurs.
[0016]
Further, the contact angle θ 2 between the raceway grooves 11A and 11B of the raceway groove 11 and the ball 3 is set to 25 ° (20 ° to 30 °), and the contact angle θ 1 between the raceway grooves 12A and 12B of the raceway groove 12 and the ball 3 is set. Since the angle is set to 25 °, it is possible to avoid the problem of heat generation due to the spin of the ball 3 and the shoulder climb of the ball 3 without causing a decrease in moment rigidity. When the contact angles θ 1 and θ 2 are less than 20 °, the axial backlash increases and the moment rigidity decreases. On the other hand, when the contact angles θ 1 and θ 2 exceed 30 °, the spin of the ball 3 increases. As a result, heat generation increases.
[0017]
In addition, since the groove curvature radius R1 (53.0 Bd%) of the raceway grooves 11A and 11B of the inner ring 1 is made smaller than the groove curvature radius (55Bd%) of the raceway grooves 12A and 12B of the outer ring 2, the raceway groove 11A of the inner ring 1 is set. , 11B and the surface pressure of the raceway grooves 12A, 12B of the outer ring 2 can be balanced to improve the peeling life. The raceway groove 11 of the inner ring 1 is convex with respect to the ball 3 in a cross section cut along a plane perpendicular to the axis, whereas the raceway groove 12 of the outer ring 2 has a cross section cut along a plane perpendicular to the axis with respect to the ball 3. It is concave. For this reason, when the groove radius of curvature R2 of the outer ring 2 and the groove radius of curvature R1 of the inner ring 1 are the same, the surface pressure of the inner ring 1 becomes larger than the outer ring 2, the surface pressure becomes unbalanced, and the service life is increased. Decreases.
[0018]
As described above, according to this embodiment, it is possible to realize a rotating shaft support structure having a four-point contact ball bearing that is excellent in moment load resistance and moment rigidity, and excellent in peeling resistance and seizure resistance.
[0019]
In the above embodiment, the radius of curvature of the raceway groove 11 of the inner ring 1 is set to 53% of the diameter of the ball. However, if the radius is set in the range of 52 to 53.5%, the above-described effect can be obtained. Moreover, if the curvature radius of the raceway groove | channel 12 of the outer ring | wheel 2 is set in the range of 53.5%-56% of the diameter of a ball | bowl, the same effect can be acquired.
[0020]
【The invention's effect】
As is clear from the above, the four-point contact ball bearing of the rotating shaft support structure of the present invention has a groove radius of curvature of the inner (outer) ring of 52 (53.5) Bd% or more. Since the seizure life is not shortened and the groove radius of curvature of the inner (outer) ring is set to 53.5 (56) Bd% or less, the peeling life and moment rigidity can be secured.
[0021]
In one embodiment, since the contact angle is set to 20 ° or more, the moment rigidity is not reduced, and the contact angle is set to 30 ° or less. The problem can be avoided.
[0022]
Further, the groove radius of curvature of the inner ring raceway surface (52-53.5 Bd%) is made smaller than the groove radius of curvature of the raceway surface of the outer ring (53.5-56 Bd%). It is possible to improve the peeling life by balancing the surface pressure of the track surface.
[0023]
Therefore, according to the present invention, it is possible to realize a rotating shaft support structure having a four-point contact ball bearing that is excellent in moment load resistance and moment rigidity, and excellent in peel resistance and seizure resistance.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of an embodiment of a rotary shaft support structure having a four-point contact ball bearing of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Inner ring, 2 ... Outer ring, 3 ... Ball, 5 ... Cage, 6 ... Sealing member,
7 ... Seal lip, 11,12 ... Track groove,
P 0 ... ball center, P 11 , P 12 , P 21 , P 22 ... curvature center, θ 1 , θ 2 ... contact angle.

Claims (1)

単列の玉軸受でモーメント荷重を含む荷重を支持する回転軸支持構造であって、
上記玉軸受は、
玉の中心の軸方向位置から軸方向の両側に延在する軌道溝を有する内輪と、上記玉の中心の軸方向位置から軸方向の両側に延在する軌道溝を有する外輪とを有する４点接触玉軸受であり、
上記内輪の軌道溝の軌道面の溝曲率半径を玉径の５２〜５３.５％とし、
上記外輪の軌道溝の軌道面の溝曲率半径を玉径の５３.５〜５６％とし、
かつ、上記内輪の軌道溝の軌道面の溝曲率半径を上記外輪の軌道溝の軌道面の溝曲率半径よりも小さくして、上記内輪の軌道溝の面圧と上記外輪の軌道溝の面圧とをバランスさせることを特徴とする回転軸支持構造。 A rotating shaft support structure that supports a load including moment load with a single row ball bearing,
The above ball bearing
Four points having an inner ring having a raceway groove extending from the axial position at the center of the ball to both sides in the axial direction and an outer ring having a raceway groove extending from the axial position at the center of the ball to both sides in the axial direction Contact ball bearings,
The radius of curvature of the raceway surface of the raceway groove of the inner ring is 52-53.5% of the ball diameter,
The radius of curvature of the raceway surface of the raceway groove of the outer ring is 53.5 to 56% of the ball diameter,
Further, the groove radius of curvature of the raceway surface of the inner ring raceway groove is made smaller than the radius of curvature of the raceway surface of the raceway groove of the outer ring, and the surface pressure of the raceway groove of the inner ring and the surface pressure of the raceway groove of the outer ring. Rotating shaft support structure characterized by balancing
JP2000122523A 2000-04-24 2000-04-24 Rotating shaft support structure Expired - Fee Related JP3905283B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104956105A (en) * 2013-01-30 2015-09-30 日本精工株式会社 Multipoint contact ball bearing

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Publication number Priority date Publication date Assignee Title
US6827496B2 (en) * 2001-08-28 2004-12-07 Koyo Seiko Co., Ltd. Four-point contact ball bearing
US20060013519A1 (en) * 2002-12-16 2006-01-19 Masafumi Fukunaga Four-point contact ball bearing
CN104141691B (en) * 2013-05-07 2017-06-27 襄阳汽车轴承股份有限公司 A kind of commercial car penetrating bridge exports end bearing
CN106763157A (en) * 2016-11-29 2017-05-31 江苏万达特种轴承有限公司 The single spherical structure roller bearing of linear contact formula
CN106640559B (en) * 2017-01-10 2019-01-08 河南科技大学 The setting method and device of asymmetric double four-point contact ball asymmetry angle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104956105A (en) * 2013-01-30 2015-09-30 日本精工株式会社 Multipoint contact ball bearing

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