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WO2020246621A1 - Bearing - Google Patents

Bearing Download PDF

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Publication number
WO2020246621A1
WO2020246621A1 PCT/JP2020/023316 JP2020023316W WO2020246621A1 WO 2020246621 A1 WO2020246621 A1 WO 2020246621A1 JP 2020023316 W JP2020023316 W JP 2020023316W WO 2020246621 A1 WO2020246621 A1 WO 2020246621A1
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WIPO (PCT)
Prior art keywords
bearing
rolling element
ring
diameter
inscribed
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
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PCT/JP2020/023316
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French (fr)
Japanese (ja)
Inventor
隆志 浜口
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Individual
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Individual
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Priority claimed from JP2019114100A external-priority patent/JP6742573B1/en
Priority claimed from JP2019191509A external-priority patent/JP6742574B1/en
Application filed by Individual filed Critical Individual
Publication of WO2020246621A1 publication Critical patent/WO2020246621A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16C19/50—Other types of ball or roller bearings
    • F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
    • 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
    • F16C19/55—Systems consisting of a plurality of bearings with rolling friction with intermediate floating or independently-driven rings rotating at reduced speed or with other differential ball or roller 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
    • 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
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row of rollers

Definitions

  • the present invention relates to bearings.
  • the distance that the inner race wheel that is inscribed and the outer race wheel that is inscribed is the same is the same as that of the outer race track. Since the diameters of the ring and the inner raceway ring are different, the movement angle that moves around the central axis of the bearing of the outer raceway ring is smaller than the movement angle that moves around the central axis of the bearing of the inner raceway ring, so that the outer raceway ring.
  • the multipoint contact ball bearing of Patent Document 1 does not specify the contact position between the bearing wheel and the rolling element, the multipoint contact ball bearing of Patent Document 1 fixes the outer race ring and the inner race ring. It is not a bearing in which the rolling element does not move in the direction opposite to the rotation direction of the inner raceway ring even if the bearing rotates.
  • the present invention solves the above-mentioned conventional problems, and forms a bearing in which the outer raceway ring is fixed so that the rolling element does not move in the direction opposite to the rotation direction of the inner raceway ring even if the inner raceway ring rotates.
  • the purpose is.
  • a medium earth orbit ring is provided between the inner orbit ring, and the inner rolling element inscribed in the inner orbit ring and inscribed in the middle orbit ring, and the middle orbit ring It is a bearing with an abducting body inscribed in the outer orbital ring, and the medium earth orbit ring inscribed by the inward rolling element and circumscribing the abducting body rotates in the opposite direction to the inner orbital ring, thereby causing adduction.
  • the inner orbital ring inscribed in the moving body and the medium earth orbit ring inscribed in the inward rolling element are moved by the same distance, and the medium earth orbit ring inscribed in the abducting body and the outer orbital ring inscribed in the abducting body are the same distance.
  • the distance that the abductor moves is the same.
  • a middle raceway ring is provided between the inner raceway ring and the outer raceway ring, and an inner rolling element that is inscribed in the inner raceway ring and inscribed in the middle raceway ring, and an outer rolling element that is inscribed in the middle raceway ring and inscribed in the outer raceway ring
  • the bearing of the present invention when the medium earth orbit ring rotates in the opposite direction to the inner orbit ring, the distance between the inner orbit ring inscribed in the inward rolling element and the inscribed medium earth orbit ring in the inward rolling element is increased. Since the distance is the same, the distance that the abductor moves between the medium earth orbit ring that is inscribed in the abductor and the outer orbital ring that is inscribed in the abductor is the same distance.
  • the bearing is characterized in that the rolling element does not move due to the difference in the length of the wheels.
  • FIG. 1 is a front schematic view of a conventional bearing.
  • FIG. 2 is a vector diagram showing the movement of a rolling element of a conventional bearing.
  • FIG. 3 is a front schematic view of the bearing of the present invention.
  • FIG. 4 is a side sectional view of an embodiment of the ball bearing of the present invention.
  • FIG. 5 is a side sectional view of an embodiment of the roller bearing of the present invention.
  • FIG. 6 shows an embodiment of the roller bearing of the present invention, in which two bearings are doubly arranged and the inner raceway ring of the outer bearing is integrally fitted to the outer raceway ring of the inner bearing to function as the middle raceway ring. Side sectional view of the bearing.
  • the inner raceway ring 1 has a diameter of 50
  • the rolling element 2 has a diameter of 10
  • the outer raceway ring 3 has a diameter of 70.
  • the diameter is the diameter of the contact point between the rolling element and the raceway ring, and the number is the ratio, not the length.
  • the circumference ratio is ⁇ . Since the moving distance of the rolling element 2 is only half the moving distance of the raceway ring, When the outer orbital ring 3 having a diameter of 70 makes two rotations and moves a distance of 140 ⁇ , the inscribed rolling element 2 having a diameter of 10 moves 70 ⁇ around the outer orbital ring 3 and goes around the outer orbital ring 3 in seven rotations.
  • the circumscribing rolling element 2 having a diameter of 10 moves the inner raceway ring 1 by 50 ⁇ and goes around the inner raceway ring 1 in five rotations. If both raceway wheels rotate, the bearing will rotate without any problem, but as shown in FIG. 2, the rolling element 2 moves in the rotation direction of the long outer raceway ring 3 by a distance of 10 ⁇ for one rotation of the rolling element 2. I will.
  • the rolling element 2 also moves clockwise, but the rolling element 2 moves 10 ⁇ counterclockwise as shown in FIG. , Even if the inner raceway wheel 1 rotates 60 ⁇ clockwise, the rolling element 2 moves only 50 ⁇ clockwise.
  • the inner raceway ring 1 of the bearing is at the contact position between the inner raceway ring 1 of the bearing and the inner rolling element 15, and the angle 40+ from the position 20 to the position 22 about the rotation center axis 19 of the bearing.
  • the angle 41 is rotated clockwise, the inward rolling element 15 in contact with the inner raceway ring 1 of the bearing also moves clockwise around the rotation center axis 19 of the bearing, but the middle raceway ring 14 of the bearing is the bearing.
  • the distance at which the contact position between the inner track 34 of the inner race ring of the bearing and the adduction element 15 moves is the distance from position 25 to position 23-position from position 25.
  • the distance of 24 the distance from the position 24 to the position 23, and the distance from the position 20 of the moving distance of the contact position between the inner raceway ring 1 of the bearing and the inward rolling element 15 is the same as the position 22.
  • the middle raceway ring 14 of the bearing that rotates in the direction opposite to the inner raceway ring 1 of the bearing is arranged, and the middle raceway ring 1 of the bearing
  • the inward rolling element 15 inside and the abducting element 16 outside, the moving distance of the contact position of the bearing ring inscribed in the rolling element around the rotation center axis 19 of the bearing and the external contact with the rolling element. Since the moving distance of the contact position of the bearing wheel can be the same, the rolling element does not move due to the difference in the length of the wheel.
  • FIG. 4 is a side sectional view of an embodiment of the ball bearing of the present invention.
  • FIG. 5 is a side sectional view of an embodiment of the roller bearing of the present invention.
  • FIG. 6 is a side sectional view of a bearing in which two bearings are doubly arranged and the inner raceway of the outer bearing is integrally fitted to the outer raceway of the inner bearing to function as a medium earth orbit in the bearing embodiment of the present invention. ..
  • the contact position between the outer race wheel of the bearing and the rolling element is the rotation center axis of the bearing Circular orbit 14 when moving the outer race wheel of the bearing around Rotation center axis 20
  • Contact position between the inner race wheel of the bearing and the inner rolling element 21
  • Contact position between the inner race wheel of the bearing and the inner rolling element 22
  • Contact position between the inner race wheel of the bearing and the inner rolling element 23
  • the middle race wheel of the bearing Contact position of the inner rolling element 24 Contact position of the middle race wheel of the bearing and the inner rolling element 25
  • the middle race of the bearing Contact position between the wheel and the abductor 28 Contact position between the inner race wheel and the abductor of the bearing 29
  • Contact position between the outer race wheel and the abductor of the bearing 30
  • Contact position between the outer race wheel and the abductor of the bearing 31

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

In a bearing according to the related art, since the diameters of an inner bearing ring and an outer bearing ring are different from each other, a rolling element moves in an opposite direction to the rotation direction of the inner bearing ring when the outer bearing ring is fixed and the inner bearing ring rotates. However, a bearing according to the present invention is characterized in that by rotating, in an opposite direction to an inner bearing ring, a middle bearing ring provided between the inner bearing ring and an outer bearing ring, a distance by which an inner rolling element moves with respect to the inner bearing ring circumscribing the inner rolling element and a distance by which the inner rolling element moves with respect to the middle bearing ring inscribing the inner rolling element are the same, and a distance by which an outer rolling element moves with respect to the middle bearing ring circumscribing the outer rolling element and a distance by which the outer rolling element moves with respect to the outer bearing ring inscribing the outer rolling element are the same, so that there is no movement of the rolling element due to a difference in the length of the bearing ring.

Description

ベアリングbearing

本発明は、ベアリングに関する。 The present invention relates to bearings.

　従来のベアリングでは、転動体の外接する内軌道輪と内接する外軌道輪への接触位置の直径が同じため、外接する内軌道輪と内接する外軌道輪を移動する距離も同じだが、外軌道輪と内軌道輪では直径が違うので、外軌道輪のベアリングの中心軸を中心に移動する移動角度は、内軌道輪のベアリングの中心軸を中心に移動する移動角度より小さいため、外軌道輪を固定して内軌道輪が回転すると、転動体が内軌道輪の回転方向と逆方向に移動するため、転動体がベアリングの軌道輪を滑走するという欠点が有った。 In the conventional bearing, since the diameter of the contact position between the inner race ring that is inscribed by the rolling element and the outer race wheel that is inscribed is the same, the distance that the inner race wheel that is inscribed and the outer race wheel that is inscribed is the same is the same as that of the outer race track. Since the diameters of the ring and the inner raceway ring are different, the movement angle that moves around the central axis of the bearing of the outer raceway ring is smaller than the movement angle that moves around the central axis of the bearing of the inner raceway ring, so that the outer raceway ring When the inner raceway ring is rotated by fixing the bearing, the rolling element moves in the direction opposite to the rotation direction of the inner raceway ring, so that the rolling element slides on the bearing wheel.

　転動体がベアリングの軌道輪を滑走する事で、転動体と軌道輪の摩擦により、摩耗、騒音、発熱等の問題を生じるので、外軌道輪を固定して内軌道輪が回転しても転動体が内軌道輪の回転方向と逆方向に移動しないベアリングが望まれていた。 When the rolling element slides on the bearing wheel, the friction between the rolling element and the bearing causes problems such as wear, noise, and heat generation. Therefore, even if the outer wheel is fixed and the inner ring rotates, it rolls. A bearing in which the moving body does not move in the direction opposite to the rotation direction of the inner raceway ring has been desired.

特開２００３−３３６６４０Japanese Patent Application Laid-Open No. 2003-336640

　特許文献１の多点接触玉軸受は、ベアリングの軌道輪と転動体の接触位置を特定した物ではないため、特許文献１の多点接触玉軸受は、外軌道輪を固定して内軌道輪が回転しても転動体が内軌道輪の回転方向と逆方向に移動しないベアリングという物ではない。 Since the multipoint contact ball bearing of Patent Document 1 does not specify the contact position between the bearing wheel and the rolling element, the multipoint contact ball bearing of Patent Document 1 fixes the outer race ring and the inner race ring. It is not a bearing in which the rolling element does not move in the direction opposite to the rotation direction of the inner raceway ring even if the bearing rotates.

　本発明は前記のような従来の問題を解決するものであり、外軌道輪を固定して内軌道輪が回転しても転動体が内軌道輪の回転方向と逆方向に移動しないベアリングにすることを目的とする。 The present invention solves the above-mentioned conventional problems, and forms a bearing in which the outer raceway ring is fixed so that the rolling element does not move in the direction opposite to the rotation direction of the inner raceway ring even if the inner raceway ring rotates. The purpose is.

　前記目的を達成するために本発明のベアリングは、内軌道輪と外軌道輪の間に中軌道輪を設け、内軌道輪に外接し中軌道輪に内接する内転動体と、中軌道輪に外接し外軌道輪に内接する外転動体が介在されたベアリングであって、内転動体が内接し外転動体が外接する中軌道輪が内軌道輪と逆方向に回転することで、内転動体に外接する内軌道輪と内転動体に内接する中軌道輪を内転動体が移動する距離が同じ距離になり、外転動体に外接する中軌道輪と外転動体に内接する外軌道輪を外転動体が移動する距離が同じ距離になる。 In order to achieve the above object, in the bearing of the present invention, a medium earth orbit ring is provided between the inner orbit ring, and the inner rolling element inscribed in the inner orbit ring and inscribed in the middle orbit ring, and the middle orbit ring It is a bearing with an abducting body inscribed in the outer orbital ring, and the medium earth orbit ring inscribed by the inward rolling element and circumscribing the abducting body rotates in the opposite direction to the inner orbital ring, thereby causing adduction. The inner orbital ring inscribed in the moving body and the medium earth orbit ring inscribed in the inward rolling element are moved by the same distance, and the medium earth orbit ring inscribed in the abducting body and the outer orbital ring inscribed in the abducting body are the same distance. The distance that the abductor moves is the same.

　本発明のベアリングは内軌道輪と外軌道輪の間に中軌道輪を設け、内軌道輪に外接し中軌道輪に内接する内転動体と中軌道輪に外接し外軌道輪に内接する外転動体が介在されたベアリングであって、次の比率で軌道輪の直径と転動体の直径に設定されている事を特徴とするベアリング。
　内転動体が内接する中軌道輪の直径：外転動体が内接する外軌道輪の直径＝内転動体の直径：外転動体の直径。 In the bearing of the present invention, a middle raceway ring is provided between the inner raceway ring and the outer raceway ring, and an inner rolling element that is inscribed in the inner raceway ring and inscribed in the middle raceway ring, and an outer rolling element that is inscribed in the middle raceway ring and inscribed in the outer raceway ring A bearing in which a rolling element is interposed, characterized in that the diameter of the raceway ring and the diameter of the rolling element are set at the following ratios.
Diameter of the medium earth orbit ring inscribed by the adduction body: Diameter of the outer track ring inscribed by the abductor = Diameter of the adduction body: Diameter of the abductor.

　本発明のベアリングは、中軌道輪が内軌道輪と逆方向に回転することで、内転動体に外接する内軌道輪と内転動体に内接する中軌道輪を内転動体が移動する距離が同じ距離になり、外転動体に外接する中軌道輪と外転動体に内接する外軌道輪を外転動体が移動する距離が同じ距離になるので、転動体に内接する軌道輪と外接する軌道輪の長さの違いによる転動体の移動が無いベアリングにしたことを特徴とするベアリングである。 In the bearing of the present invention, when the medium earth orbit ring rotates in the opposite direction to the inner orbit ring, the distance between the inner orbit ring inscribed in the inward rolling element and the inscribed medium earth orbit ring in the inward rolling element is increased. Since the distance is the same, the distance that the abductor moves between the medium earth orbit ring that is inscribed in the abductor and the outer orbital ring that is inscribed in the abductor is the same distance. The bearing is characterized in that the rolling element does not move due to the difference in the length of the wheels.

　図１は従来のベアリングの正面概略図。
　図２は従来のベアリングの転動体の動きを示すベクトル図
　図３は本発明のベアリングの正面概略図。
　図４は本発明のボールベアリングでの実施例の側面断面図。
　図５は本発明のローラーベアリングでの実施例の側面断面図。
　図６は本発明のローラーベアリングでの実施例で、二つのベアリングを二重に配置し内側のベアリングの外軌道輪に外側のベアリングの内軌道輪を一体に嵌め合い中軌道輪として機能させたベアリングの側面断面図。 FIG. 1 is a front schematic view of a conventional bearing.
FIG. 2 is a vector diagram showing the movement of a rolling element of a conventional bearing. FIG. 3 is a front schematic view of the bearing of the present invention.
FIG. 4 is a side sectional view of an embodiment of the ball bearing of the present invention.
FIG. 5 is a side sectional view of an embodiment of the roller bearing of the present invention.
FIG. 6 shows an embodiment of the roller bearing of the present invention, in which two bearings are doubly arranged and the inner raceway ring of the outer bearing is integrally fitted to the outer raceway ring of the inner bearing to function as the middle raceway ring. Side sectional view of the bearing.

　図１では、内軌道輪１は直径５０、転動体２は直径１０、外軌道輪３は直径７０とします。
　直径は転動体と軌道輪の接触位置の直径であり、数字は長さではなく比率です。
　円周率はπとします。
　転動体２の移動距離は軌道輪の移動距離の半分の距離しか移動しないので、
　直径７０の外軌道輪３が２回転し距離１４０π移動すると、内接している直径１０の転動体２は、外軌道輪３を７０π移動して７回転で外軌道輪３を一周します。
　直径５０の内軌道輪１が２回転し距離１００π移動すると、外接している直径１０の転動体２は、内軌道輪１を５０π移動して５回転で内軌道輪１を一周します。
　両方の軌道輪が回転すればベアリングは問題なく回転しますが、図２の様に転動体２は距離の長い外軌道輪３の回転方向に、転動体２の１回転分の距離１０π移動します。
　外軌道輪３を固定して、内軌道輪１が時計回りに回転移動すると、転動体２も時計回りに移動しますが、転動体２は図２の様に反時計回りに１０π移動するので、内軌道輪１が６０π時計回りに回転しても、転動体２は５０πしか時計回りに移動しません。 In FIG. 1, the inner raceway ring 1 has a diameter of 50, the rolling element 2 has a diameter of 10, and the outer raceway ring 3 has a diameter of 70.
The diameter is the diameter of the contact point between the rolling element and the raceway ring, and the number is the ratio, not the length.
The circumference ratio is π.
Since the moving distance of the rolling element 2 is only half the moving distance of the raceway ring,
When the outer orbital ring 3 having a diameter of 70 makes two rotations and moves a distance of 140π, the inscribed rolling element 2 having a diameter of 10 moves 70π around the outer orbital ring 3 and goes around the outer orbital ring 3 in seven rotations.
When the inner raceway ring 1 having a diameter of 50 makes two rotations and moves a distance of 100π, the circumscribing rolling element 2 having a diameter of 10 moves the inner raceway ring 1 by 50π and goes around the inner raceway ring 1 in five rotations.
If both raceway wheels rotate, the bearing will rotate without any problem, but as shown in FIG. 2, the rolling element 2 moves in the rotation direction of the long outer raceway ring 3 by a distance of 10π for one rotation of the rolling element 2. I will.
When the outer orbital ring 3 is fixed and the inner orbital wheel 1 rotates clockwise, the rolling element 2 also moves clockwise, but the rolling element 2 moves 10π counterclockwise as shown in FIG. , Even if the inner raceway wheel 1 rotates 60π clockwise, the rolling element 2 moves only 50π clockwise.

　図３に示した本発明のベアリングは、ベアリングの内軌道輪１がベアリングの内軌道輪１と内転動体１５の接触位置でベアリングの回転中心軸１９を中心に位置２０から位置２２まで角度４０＋角度４１を時計回りに回転するとベアリングの内軌道輪１に接触している内転動体１５もベアリングの回転中心軸１９を中心に時計回りに移動するが、ベアリングの中軌道輪１４は、ベアリングの回転中心軸１９を中心に角度４１反時計回りに回転するので、ベアリングの中軌道輪内側軌道３４と内転動体１５の接触位置が移動する距離は位置２５から位置２３の距離−位置２５から位置２４の距離＝位置２４から位置２３の距離になり、ベアリングの内軌道輪１と内転動体１５の接触位置の移動距離の位置２０から位置２２と同じ距離になる。
　ベアリングの中軌道輪１４がベアリングの回転中心軸１９を中心に、角度４１＋角度４０反時計回りに回転すると、ベアリングの中軌道輪の外側軌道３５と外転動体１６の接触位置が移動する距離は、位置２８から位置２７の距離＋位置２７から位置２６の距離＝位置２８から位置２６の距離になり、ベアリングの外軌道輪３と外転動体１６の接触位置の移動距離の位置３０から位置２９と同じ距離になる。
　以上の説明の様にベアリングの内軌道輪１と外軌道輪３の間に、ベアリングの内軌道輪１と逆方向に回転するベアリングの中軌道輪１４を配置して、ベアリングの中軌道輪１の内側に内転動体１５と外側に外転動体１６を配置することで、ベアリングの回転中心軸１９を中心に転動体に内接するベアリングの軌道輪の接触位置の移動距離と転動体に外接するベアリングの軌道輪の接触位置の移動距離を同じ距離にする事ができるので、軌道輪の長さの違いによる転動体の移動はありません。 In the bearing of the present invention shown in FIG. 3, the inner raceway ring 1 of the bearing is at the contact position between the inner raceway ring 1 of the bearing and the inner rolling element 15, and the angle 40+ from the position 20 to the position 22 about the rotation center axis 19 of the bearing. When the angle 41 is rotated clockwise, the inward rolling element 15 in contact with the inner raceway ring 1 of the bearing also moves clockwise around the rotation center axis 19 of the bearing, but the middle raceway ring 14 of the bearing is the bearing. Since the rotation center axis 19 rotates counterclockwise at an angle of 41, the distance at which the contact position between the inner track 34 of the inner race ring of the bearing and the adduction element 15 moves is the distance from position 25 to position 23-position from position 25. The distance of 24 = the distance from the position 24 to the position 23, and the distance from the position 20 of the moving distance of the contact position between the inner raceway ring 1 of the bearing and the inward rolling element 15 is the same as the position 22.
When the center race wheel 14 of the bearing rotates counterclockwise at an angle of 41 + an angle of 40 around the rotation center axis 19 of the bearing, the distance that the contact position between the outer race wheel 35 of the bearing center race wheel and the abductor 16 moves is , The distance from position 28 to position 27 + the distance from position 27 to position 26 = the distance from position 28 to position 26, and the movement distance between the outer raceway ring 3 of the bearing and the abductor 16 is from position 30 to position 29. Will be the same distance as.
As described above, between the inner raceway ring 1 and the outer raceway ring 3 of the bearing, the middle raceway ring 14 of the bearing that rotates in the direction opposite to the inner raceway ring 1 of the bearing is arranged, and the middle raceway ring 1 of the bearing By arranging the inward rolling element 15 inside and the abducting element 16 outside, the moving distance of the contact position of the bearing ring inscribed in the rolling element around the rotation center axis 19 of the bearing and the external contact with the rolling element. Since the moving distance of the contact position of the bearing wheel can be the same, the rolling element does not move due to the difference in the length of the wheel.

　図４は、本発明のボールベアリングでの実施例の側面断面図である。 FIG. 4 is a side sectional view of an embodiment of the ball bearing of the present invention.

　図５は、本発明のローラーベアリングでの実施例の側面断面図である。 FIG. 5 is a side sectional view of an embodiment of the roller bearing of the present invention.

　図６は、本発明のベアリング実施例で、二つのベアリングを二重に配置し内側のベアリングの外軌道に外側のベアリングの内軌道を一体に嵌め合い中軌道として機能させたベアリングの側面断面図。 FIG. 6 is a side sectional view of a bearing in which two bearings are doubly arranged and the inner raceway of the outer bearing is integrally fitted to the outer raceway of the inner bearing to function as a medium earth orbit in the bearing embodiment of the present invention. ..

　以上実施例について詳細に説明したが、本発明はこのような実施例に限定されるものではなく、細部の構成、形状、配置、素材等において本発明の要旨を逸脱しない範囲において任意に変更実施できる。 Although the examples have been described in detail above, the present invention is not limited to such examples, and the details of the configuration, shape, arrangement, materials, etc. are arbitrarily modified without departing from the gist of the present invention. it can.

１　内軌道輪
２　転動体
３　外軌道輪
４　転動体の移動前の位置
５　転動体の移動後の位置
６　転動体の反時計回りの移動距離１０πを示すベクトル図
７　転動体が時計回りに内軌道輪を一周する距離５０πを示すベクトル図
８　転動体が反時計回りに外軌道輪を一周する距離７０πを示すベクトル図
９　内軌道輪が時計回りに移動する距離６０πを示すベクトル図
１０　外軌道輪が反時計回りに移動する距離６０πを示すベクトル図
１１　ベアリングの軌道輪と転動体の接触位置が転動体の回転中心軸を中心に転動体の外周を移動する時の接触位置の円軌道
１２　ベアリングの内軌道輪と転動体の接触位置がベアリングの回転中心軸を中心にベアリングの内軌道輪を移動する時の円軌道
１３　ベアリングの外軌道輪と転動体の接触位置がベアリングの回転中心軸を中心にベアリングの外軌道輪を移動する時の円軌道
１４　ベアリングの中軌道輪
１５　内転動体
１６　外転動体
１７　ベアリングの外軌道輪と転動体の接触位置
１８　転動体の回転中心軸
１９　ベアリングの回転中心軸
２０　ベアリングの内軌道輪と内転動体の接触位置
２１　ベアリングの内軌道輪と内転動体の接触位置
２２　ベアリングの内軌道輪と内転動体の接触位置
２３　ベアリングの中軌道輪と内転動体の接触位置
２４　ベアリングの中軌道輪と内転動体の接触位置
２５　ベアリングの中軌道輪と内転動体の接触位置
２６　ベアリングの中軌道輪と外転動体の接触位置
２７　ベアリングの中軌道輪と外転動体の接触位置
２８　ベアリングの中軌道輪と外転動体の接触位置
２９　ベアリングの外軌道輪と外転動体の接触位置
３０　ベアリングの外軌道輪と外転動体の接触位置
３１　ベアリングの外軌道輪と外転動体の接触位置
３２　内転動体の回転中心軸
３３　外転動体の回転中心軸
３４　ベアリングの中軌道輪の内側軌道（内転動体の接触位置がベアリングの回転中心軸を中心にベアリングの中軌道輪を移動する時の円軌道）
３５　ベアリングの中軌道輪の外側軌道（外転動体の接触位置がベアリングの回転中心軸を中心にベアリングの中軌道輪を移動する時の円軌道）
３６　ベアリングの外軌道輪と外転動体の接触位置がベアリングの回転中心軸を中心にベアリングの外軌道輪を移動する時の円軌道
３７　ベアリングの内軌道輪と内転動体の接触位置がベアリングの回転中心軸を中心にベアリングの内軌道輪を移動する時の円軌道
３８　内側のベアリングの外軌道輪
３９　外側のベアリングの内軌道輪
４０　移動角度
４１　移動角度 1 Inner orbital wheel 2 Rolling body 3 Outer orbital wheel 4 Position before movement of rolling element 5 Position after movement of rolling element 6 Vector showing the counterclockwise movement distance of the rolling element 10π Vector figure showing the distance 50π that goes around the orbital ring 8 Vector showing the distance 70π that the rolling element goes around the outer orbital ring counterclockwise Fig. 9 Vector showing the distance 60π that the inner orbital ring moves clockwise Fig. 10 Outer orbit Vector diagram showing a distance of 60π for the wheel to move counterclockwise Fig. 11 Circular orbit 12 of the contact position when the contact position between the bearing wheel and the rolling element moves around the outer circumference of the rolling element around the rotation center axis of the rolling element. Circular track when the contact position between the inner race wheel of the bearing and the rolling element moves around the rotation center axis of the bearing 13 The contact position between the outer race wheel of the bearing and the rolling element is the rotation center axis of the bearing Circular orbit 14 when moving the outer race wheel of the bearing around Rotation center axis 20 Contact position between the inner race wheel of the bearing and the inner rolling element 21 Contact position between the inner race wheel of the bearing and the inner rolling element 22 Contact position between the inner race wheel of the bearing and the inner rolling element 23 The middle race wheel of the bearing Contact position of the inner rolling element 24 Contact position of the middle race wheel of the bearing and the inner rolling element 25 Contact position of the middle race wheel of the bearing and the inner rolling element 26 Contact position of the middle race wheel of the bearing and the outer rolling element 27 The middle race of the bearing Contact position between the wheel and the abductor 28 Contact position between the inner race wheel and the abductor of the bearing 29 Contact position between the outer race wheel and the abductor of the bearing 30 Contact position between the outer race wheel and the abductor of the bearing 31 Contact position between the outer track ring and the abductor 32 Rotation center axis of the inner roller 33 Rotation center axis of the abductor 34 Inner orbit of the bearing center wheel (contact position of the inner roller is centered on the rotation center axis of the bearing Circular orbit when moving the middle orbital wheel of the bearing)
35 Outer orbit of the bearing's medium earth orbit ring (circular orbit when the contact position of the abductor moves around the bearing's center of rotation axis)
36 Circular orbit when the contact position between the outer race wheel of the bearing and the outer rolling element moves around the rotation center axis of the bearing 37 The contact position between the inner race ring of the bearing and the inner rolling element of the bearing Circular orbit when moving the inner bearing ring of the bearing around the center of rotation 38 Outer orbit ring of the inner bearing 39 Inner orbit ring of the outer bearing 40 Moving angle 41 Moving angle

Claims (2)

　内軌道輪と外軌道輪の間に中軌道輪を設け、前記内軌道輪に外接し前記中軌道輪に内接する内転動体と前記中軌道輪に外接し前記外軌道輪に内接する外転動体が介在されたベアリングであって、前記内転動体が内接し前記外転動体が外接する前記中軌道輪は一体の物であり、
　次の比率で軌道輪の直径と転動体の直径に設定されている事を特徴とするベアリング。
前記内転動体が内接する前記中軌道輪の直径：前記外転動体が内接する前記外軌道輪の直径＝前記内転動体の直径：前記外転動体の直径。 An inner raceway ring is provided between the inner raceway ring and the outer raceway ring, and an inward rolling element that is inscribed in the inner raceway ring and inscribed in the medium earth orbit ring and an abduction that is inscribed in the middle orbital ring and inscribed in the outer raceway ring. The medium earth orbit ring is a bearing in which a moving body is interposed, and the inward rolling element is inscribed and the abducting body is inscribed.
A bearing characterized in that the diameter of the raceway ring and the diameter of the rolling element are set at the following ratios.
Diameter of the medium earth orbit ring inscribed by the adduction body: Diameter of the outer track ring inscribed by the abduction body = Diameter of the adduction body: Diameter of the abduction body. 　内軌道輪と外軌道輪との間に転動体が介在された内側のベアリングの外軌道輪に一体に嵌め合う内軌道輪を有し、内軌道輪と外軌道輪との間に転動体が介在された外側のベアリングを配置することにより、前記内側のベアリングと前記外側のベアリングを二重に配置したベアリングであって、
　次の比率で軌道輪の直径と転動体の直径に、設定されている事を特徴とするベアリング。
前記内側のベアリングの転動体が内接する前記内側のベアリングの外軌道輪の直径：前記外側のベアリングの転動体が内接する前記外側のベアリングの外軌道輪の直径＝前記内側のベアリングの転動体の直径：前記外側のベアリングの転動体の直径。 It has an inner raceway ring that is integrally fitted to the outer raceway ring of the inner bearing with a rolling element interposed between the inner raceway ring and the outer raceway ring, and the rolling element is between the inner raceway ring and the outer raceway ring. By arranging the intervening outer bearing, the inner bearing and the outer bearing are doubly arranged.
A bearing characterized in that the diameter of the raceway ring and the diameter of the rolling element are set at the following ratios.
Diameter of the outer raceway ring of the inner bearing inscribed by the rolling element of the inner bearing: Diameter of the outer raceway ring of the outer bearing inscribed by the rolling element of the outer bearing = diameter of the rolling element of the inner bearing Diameter: The diameter of the rolling element of the outer bearing.
PCT/JP2020/023316 2019-06-03 2020-05-27 Bearing Ceased WO2020246621A1 (en)

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JP2019-114100 2019-06-03
JP2019114100A JP6742573B1 (en) 2019-06-03 2019-06-03 bearing
JP2019-191509 2019-10-01
JP2019191509A JP6742574B1 (en) 2019-10-01 2019-10-01 bearing

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US3597029A (en) * 1969-08-18 1971-08-03 Elias M Marcum Planetary bearing assembly
JPS6440709A (en) * 1987-08-04 1989-02-13 Mitsubishi Electric Corp Radial rolling bearing
JP2002333017A (en) * 2000-12-29 2002-11-22 Ge Medical Systems Global Technology Co Llc Multi-row bearing structure for x-ray tube
US20100192927A1 (en) * 2008-01-30 2010-08-05 Accessible Techonologies, Inc. method and apparatus for controlling a compound bearing assembly of a centrifugal compressor
GB2563706A (en) * 2017-03-01 2018-12-26 Ltj As Spherical bearing
DE102017123601A1 (en) * 2017-10-11 2019-04-11 Schaeffler Technologies AG & Co. KG ball-bearing

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