JP2010151152A - Revolving seat bearing - Google Patents

Revolving seat bearing Download PDF

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Publication number
JP2010151152A
JP2010151152A JP2008326862A JP2008326862A JP2010151152A JP 2010151152 A JP2010151152 A JP 2010151152A JP 2008326862 A JP2008326862 A JP 2008326862A JP 2008326862 A JP2008326862 A JP 2008326862A JP 2010151152 A JP2010151152 A JP 2010151152A
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Prior art keywords
peripheral surface
outer peripheral
raceway
raceway surface
ring groove
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JP2008326862A
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Japanese (ja)
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Shinichi Ono
新一 大野
Noboru Kashino
昇 樫野
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ANTEX CORP
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ANTEX CORP
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Priority to JP2008326862A priority Critical patent/JP2010151152A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/361—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers
    • F16C19/362—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with cylindrical rollers the rollers being crossed within the single 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/50—Crowning, e.g. crowning height or crowning radius

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a revolving seat bearing capable of preventing edge load from occurring on outer peripheral faces of main rollers and on outer peripheral faces of inverse rollers, and improving durability. <P>SOLUTION: The revolving seat bearing 10 includes an outer ring 11 having an outer ring groove part 21 with a substantially V-shaped cross section on the inner peripheral face side, and an inner ring 12 having an inner ring groove part 31 with a substantially V-shaped cross section on the outer peripheral face side. The main rollers 13 and the inverse rollers 14 are alternately disposed between the outer ring 11 and the inner ring 12. The outer ring groove part 21 has a first raceway surface 23 and a second raceway surface 24, and cut crowning faces 23a, 23b, 24a, 24b are formed on upper and lower both ends of the raceway surfaces 23, 24. The inner ring groove part 31 has a third raceway surface 33 and a fourth raceway surface 34, and cut crowning faces 33a, 33b, 34a, 34b are formed on upper and lower both ends of the raceway surfaces 33, 34. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、外輪と内輪との間に主ころおよび反転ころを配設した旋回座軸受に関するものである。   The present invention relates to a swivel bearing having a main roller and a reverse roller disposed between an outer ring and an inner ring.

従来、例えば下記の特許文献１に記載された旋回座軸受が知られている。   Conventionally, for example, a swivel bearing described in Patent Document 1 below is known.

この従来の旋回座軸受は、第１軌道面（上側軌道面）および第２軌道面（下側軌道面）が形成された断面略Ｖ字状の外輪溝部を内周面側に有する外輪と、外輪の内方に配設され第３軌道面（上側軌道面）および第４軌道面（下側軌道面）が形成された断面略Ｖ字状の内輪溝部を外周面側に有する内輪とを備えている。   This conventional swivel bearing has an outer ring having an outer ring groove portion having a substantially V-shaped cross section on the inner peripheral surface side, on which a first raceway surface (upper raceway surface) and a second raceway surface (lower raceway surface) are formed. An inner ring having a substantially V-shaped inner ring groove portion on the outer peripheral surface side, which is disposed inside the outer ring and has a third raceway surface (upper raceway surface) and a fourth raceway surface (lower raceway surface). ing.

また、この従来の旋回座軸受は、外輪溝部と内輪溝部との間に回転可能に配設され外周面が第１軌道面および第４軌道面に接触し主負荷が作用する略円柱状の複数の主ころと、外輪溝部と内輪溝部との間に回転可能に配設され外周面が第２軌道面および第３軌道面に接触し反転側負荷が作用する略円柱状の複数の反転ころとを備えている。   In addition, this conventional swivel bearing has a plurality of substantially cylindrical shapes that are rotatably disposed between the outer ring groove portion and the inner ring groove portion and whose outer peripheral surfaces are in contact with the first track surface and the fourth track surface and the main load acts. A plurality of substantially cylindrical reversing rollers which are rotatably disposed between the outer ring groove portion and the inner ring groove portion and whose outer peripheral surface is in contact with the second raceway surface and the third raceway surface and where a load on the reverse side acts. It has.

そして、外輪の内周面上部には円筒状の径小内周面が形成され、外輪の内周面下部には径小内周面より径大な円筒状の径大内周面が形成され、これら径小内周面と径大内周面との間に外輪溝部が位置している。また、内輪の外周面上部には円筒状の径小外周面が形成され、内輪の外周面下部には径小外周面より径大な円筒状の径大外周面が形成され、これら径小外周面と径大外周面との間に内輪溝部が位置している。
特開平１０−２２０４６６号公報 A cylindrical small inner peripheral surface is formed at the upper part of the inner peripheral surface of the outer ring, and a large cylindrical inner peripheral surface having a larger diameter than the small inner peripheral surface is formed at the lower part of the inner peripheral surface of the outer ring. The outer ring groove is positioned between the small-diameter inner peripheral surface and the large-diameter inner peripheral surface. In addition, a cylindrical small outer peripheral surface is formed on the upper outer peripheral surface of the inner ring, and a cylindrical large outer peripheral surface having a diameter larger than the small outer peripheral surface is formed on the lower outer peripheral surface of the inner ring. An inner ring groove is located between the surface and the large outer peripheral surface.
JP-A-10-220466

ところで、上記従来の旋回座軸受を製造する際に、例えば図８に示すように、内輪１の外周面のうち第４軌道面２の下端と径大外周面３の上端との間の部分にこれら第４軌道面２と径大外周面３とを滑らかに連続させる湾曲外周面５を形成した場合、第４軌道面２の湾曲外周面５分だけ中に入った位置Ａ付近と第４軌道面２の上端位置Ｂ付近とで、円筒ころである主ころ４の外周面にエッジロード（極端な面圧）が生じる問題がある。   By the way, when the conventional swivel bearing is manufactured, for example, as shown in FIG. 8, a portion between the lower end of the fourth raceway surface 2 and the upper end of the large-diameter outer peripheral surface 3 in the outer peripheral surface of the inner ring 1. When the curved outer peripheral surface 5 that smoothly connects the fourth raceway surface 2 and the large-diameter outer peripheral surface 3 is formed, the vicinity of the position A and the fourth raceway that are in the curved outer peripheral surface 5 of the fourth raceway surface 2 are included. There is a problem that an edge load (extreme surface pressure) is generated on the outer peripheral surface of the main roller 4 that is a cylindrical roller near the upper end position B of the surface 2.

本発明は、このような点に鑑みなされたもので、主ころの外周面および反転ころの外周面にエッジロードが生じることを防止でき、耐久性の向上を図ることができる旋回座軸受を提供することを目的とする。   The present invention has been made in view of the above points, and provides a swivel bearing capable of preventing edge load from occurring on the outer peripheral surface of the main roller and the outer peripheral surface of the reverse roller and improving durability. The purpose is to do.

請求項１記載の旋回座軸受は、第１軌道面および第２軌道面が形成された断面略Ｖ字状の外輪溝部を内周面側に有する外輪と、この外輪の内方に配設され、第３軌道面および第４軌道面が形成された断面略Ｖ字状の内輪溝部を外周面側に有する内輪と、前記外輪溝部と前記内輪溝部との間に回転可能に配設され、外周面が前記第１軌道面および前記第４軌道面に接触し、主負荷が作用する複数の主ころと、前記外輪溝部と前記内輪溝部との間に回転可能に配設され、外周面が前記第２軌道面および前記第３軌道面に接触し、反転側負荷が作用する複数の反転ころとを備え、前記外輪は、内周面のうち前記外輪溝部より上方の部分に形成された円筒状の径小内周面と、内周面のうち前記外輪溝部より下方の部分に形成され、前記径小内周面より径大な円筒状の径大内周面とを有し、前記内輪は、外周面のうち前記内輪溝部より上方の部分に形成された円筒状の径小外周面と、外周面のうち前記内輪溝部より下方の部分に形成され、前記径小外周面より径大な円筒状の径大外周面とを有し、前記第１軌道面、前記第２軌道面、前記第３軌道面および前記第４軌道面の各々には、上下両端部にカットクラウニング面が形成されているものである。   According to a first aspect of the present invention, there is provided a swivel bearing having an outer ring having an outer ring groove portion having a substantially V-shaped cross section on the inner peripheral surface side, on which the first raceway surface and the second raceway surface are formed, and an inner side of the outer ring. An inner ring having a substantially V-shaped inner ring groove portion formed on the outer peripheral surface side on which the third and fourth raceway surfaces are formed, and rotatably disposed between the outer ring groove portion and the inner ring groove portion. A surface is in contact with the first raceway surface and the fourth raceway surface, and is rotatably disposed between a plurality of main rollers on which a main load acts, the outer ring groove portion and the inner ring groove portion, A plurality of reversing rollers in contact with the second raceway surface and the third raceway surface and acting on the reversing side load, and the outer ring is a cylindrical shape formed in a portion of the inner peripheral surface above the outer ring groove portion A small inner peripheral surface of the inner peripheral surface, and a portion of the inner peripheral surface below the outer ring groove portion. A large cylindrical inner peripheral surface, and the inner ring includes a cylindrical small outer peripheral surface formed in a portion of the outer peripheral surface above the inner ring groove portion, and the inner ring groove portion of the outer peripheral surface. A cylindrical large-diameter outer peripheral surface that is formed in a lower portion and is larger in diameter than the small-diameter outer peripheral surface, and the first raceway surface, the second raceway surface, the third raceway surface, and the fourth Each of the raceway surfaces is formed with cut crowning surfaces at both upper and lower ends.

請求項２記載の旋回座軸受は、請求項１記載の旋回座軸受において、主ころおよび反転ころの各々は、外周面が略截頭円錐状に形成された円錐ころであるものである。   The swivel bearing according to claim 2 is the swivel bearing according to claim 1, wherein each of the main roller and the reverse roller is a tapered roller having an outer peripheral surface formed in a substantially frustoconical shape.

請求項１に係る発明によれば、第１軌道面、第２軌道面、第３軌道面および第４軌道面の各々には上下両端部にカットクラウニング面が形成されているため、主ころの外周面および反転ころの外周面にエッジロードが生じることを防止でき、耐久性の向上を図ることができる。   According to the first aspect of the present invention, since the first raceway surface, the second raceway surface, the third raceway surface, and the fourth raceway surface are formed with cut crowning surfaces at both upper and lower ends, Edge load can be prevented from occurring on the outer peripheral surface and the outer peripheral surface of the reversing roller, and durability can be improved.

請求項２に係る発明によれば、主ころおよび反転ころの各々は外周面が略截頭円錐状に形成された円錐ころであるため、耐久性の向上をより一層図ることができる。   According to the invention of claim 2, since each of the main roller and the reverse roller is a tapered roller having an outer peripheral surface formed in a substantially truncated cone shape, the durability can be further improved.

本発明の旋回座軸受の一実施の形態を図面を参照して説明する。   An embodiment of a swivel seat bearing according to the present invention will be described with reference to the drawings.

図１および図２において、10は大型の旋回座軸受で、この旋回座軸受10は、例えばトラッククレーンや油圧ショベル等の大型の作業装置に使用される略円形環状のクロスローラ型軸受型旋回座（交差ころ軸受型旋回座）である。   In FIGS. 1 and 2, reference numeral 10 denotes a large swivel bearing, and the swivel bearing 10 is a substantially circular ring-shaped cross roller bearing swivel seat used in a large working device such as a truck crane or a hydraulic excavator. (Crossed roller bearing type swivel seat).

旋回座軸受10は、この旋回座軸受10の中心を通る上下方向の旋回中心軸線を中心として旋回して作業をする旋回作業部（図示せず）とこの旋回作業部を支持する支持部（図示せず）との間に配設され、支持部が旋回作業部を旋回座軸受10を介して旋回中心軸線を中心として旋回可能に支持する。   The swivel seat bearing 10 includes a swivel working unit (not shown) that swivels around a swivel center axis in the vertical direction passing through the center of the swivel seat bearing 10 and a support unit (see FIG. (Not shown), and the support part supports the turning work part via the swivel seat bearing 10 so as to be turnable about the turning center axis.

旋回座軸受10は、旋回作業部の旋回中心軸線を中心とする略円形環状の外輪11と、この外輪11の内方に外輪11と同軸状に配設され旋回作業部の旋回中心軸線を中心とする略円形環状の内輪12とを備えている。   The swivel seat bearing 10 is a substantially circular annular outer ring 11 centered on the turning center axis of the turning work section, and is disposed coaxially with the outer ring 11 inside the outer ring 11 and is centered on the turning center axis of the turning work section. And a substantially circular annular inner ring 12.

また、旋回座軸受10は、外輪11と内輪12との間に回転中心軸線ａを中心として回転可能に配設され旋回作業部による作業時（負荷作用時）に主負荷が外周面に作用する略円柱状の複数のローラである主ころ13と、外輪11と内輪12との間に回転中心軸線ａと交差（例えば直交）する回転中心軸線ｂを中心として回転可能に配設され旋回作業部による作業時に反転負荷が外周面に作用する略円柱状の複数のローラである反転ころ14とを備えている。   Further, the swivel bearing 10 is disposed between the outer ring 11 and the inner ring 12 so as to be rotatable about the rotation center axis a, and the main load acts on the outer peripheral surface during work by the swivel working portion (load operation). A swivel working unit that is disposed between a main roller 13 that is a plurality of substantially cylindrical rollers and a rotation center axis b that intersects (for example, intersects with) the rotation center axis a between the outer ring 11 and the inner ring 12. And a reversing roller 14 which is a plurality of substantially cylindrical rollers on which the reversing load acts on the outer peripheral surface during the work.

これら主ころ13および反転ころ14は、外輪11と内輪12との間に周方向に沿って交互に並設され、主ころ13の回転中心軸線ａと反転ころ14の回転中心軸線ｂとが周方向に見て互いに交差、例えば直交している。また、周方向に隣接する主ころ13および反転ころ14間にはセパレータ等の間隔保持部材（図示せず）が配設され、各間隔保持部材にて各ころ13，14間の間隙が一定に保持されている。   The main roller 13 and the reverse roller 14 are alternately arranged along the circumferential direction between the outer ring 11 and the inner ring 12, and the rotation center axis a of the main roller 13 and the rotation center axis b of the reverse roller 14 are circumferential. They cross each other when viewed in the direction, for example, perpendicular to each other. Further, a spacing member (not shown) such as a separator is disposed between the main roller 13 and the reverse roller 14 adjacent in the circumferential direction, and the gap between the rollers 13 and 14 is made constant by each spacing member. Is retained.

なお、主ころ13の回転中心軸線ａと水平方向の線（旋回座軸受10の径方向に沿った線）とのなす角度αおよび反転ころ14の回転中心軸線ｂと水平方向の線とのなす角度βは、いずれも例えば４５°である。   The angle α formed between the rotation center axis a of the main roller 13 and the horizontal line (the line along the radial direction of the swivel bearing 10) and the rotation center axis b of the reverse roller 14 and the horizontal line. The angles β are all 45 °, for example.

ここで、外輪11は、図２および図３等に示されるように、この外輪11の周方向に沿って位置しこの外輪11の径方向内方に向って開口する断面略Ｖ字状の外輪溝部21を内周面側に有している。外輪溝部21の上側には主ころ13が転動する上側軌道面である第１軌道面23が形成され、外輪溝部21の下側には反転ころ14が転動する下側軌道面である第２軌道面24が形成されている。外輪溝部21の溝底部には、略円弧状の逃げ溝部25が形成されている。   Here, as shown in FIG. 2 and FIG. 3, the outer ring 11 is positioned along the circumferential direction of the outer ring 11 and opens toward the radially inner side of the outer ring 11. A groove portion 21 is provided on the inner peripheral surface side. A first raceway surface 23 that is an upper raceway surface on which the main roller 13 rolls is formed above the outer ring groove portion 21, and a lower raceway surface that is a lower raceway surface on which the reverse roller 14 rolls is formed below the outer ring groove portion 21. Two raceway surfaces 24 are formed. A substantially arc-shaped escape groove 25 is formed at the groove bottom of the outer ring groove 21.

また、外輪11の内周面のうち外輪溝部21より上方の部分である内周面上部には円筒状の径小内周面26が形成され、外輪11の内周面のうち外輪溝部21より下方の部分である内周面下部には径小内周面26より径大な円筒状の径大内周面27が形成されている。   In addition, a cylindrical small-diameter inner peripheral surface 26 is formed on the inner peripheral surface of the inner surface of the outer ring 11 above the outer ring groove 21, and the outer ring groove 21 out of the inner peripheral surface of the outer ring 11 is formed. A cylindrical large-diameter inner peripheral surface 27 having a diameter larger than that of the small-diameter inner peripheral surface 26 is formed at a lower portion of the inner peripheral surface that is a lower portion.

そして、第１軌道面23の上下両端部には、端縁側に向ってドロップ量が直接的に大きくなるカットクラウニングが施されることにより傾斜面状のカットクラウニング面23a，23bがそれぞれ形成されている。また、第１軌道面23のうちカットクラウニング面23a，23bが形成されていない平坦な部分が平坦軌道面23cとなっており、断面図で見た場合にカットクラウニング面23a，23bの平坦軌道面23cに対する傾斜角度θは例えば略２度である。なお、第１軌道面23の上端部のカットクラウニング面23aの上端は、湾曲面状の湾曲内周面である上側湾曲内周面（チャンファ面）28を介して径小内周面26の下端に滑らかに繋がっている。   The upper and lower ends of the first raceway surface 23 are respectively provided with cut crowning surfaces 23a and 23b having inclined surfaces by being subjected to cut crowning in which the drop amount increases directly toward the edge side. Yes. Further, a flat portion of the first raceway surface 23 where the cut crowning surfaces 23a and 23b are not formed is a flat raceway surface 23c, and the flat raceway surface of the cut crowning surfaces 23a and 23b when viewed in a cross-sectional view. The inclination angle θ with respect to 23c is approximately 2 degrees, for example. The upper end of the cut crowning surface 23a at the upper end of the first raceway surface 23 is the lower end of the small inner peripheral surface 26 via an upper curved inner peripheral surface (chamber surface) 28 that is a curved inner peripheral surface. It is connected smoothly.

同様に、第２軌道面24の上下両端部には、端縁側に向ってドロップ量が直接的に大きくなるカットクラウニングが施されることにより傾斜面状のカットクラウニング面24a，24bがそれぞれ形成され、この第２軌道面24のうちカットクラウニング面24a，24bが形成されていない平坦な部分が平坦軌道面24cとなっている。また、断面図で見た場合にカットクラウニング面24a，24bの平坦軌道面24cに対する傾斜角度は、前記傾斜角度θと同じ角度で、例えば略２度である。なお、第２軌道面24の下端部のカットクラウニング面24bの下端は、湾曲面状の湾曲内周面である下側湾曲内周面（チャンファ面）29を介して径大内周面27の上端に滑らかに繋がっている。   Similarly, inclined crown-shaped cut crowning surfaces 24a and 24b are formed at both upper and lower ends of the second raceway surface 24 by applying cut crowning that directly increases the drop amount toward the edge side. In the second raceway surface 24, a flat portion where the cut crowning surfaces 24a and 24b are not formed is a flat raceway surface 24c. When viewed in a cross-sectional view, the inclination angle of the cut crowning surfaces 24a, 24b with respect to the flat track surface 24c is the same angle as the inclination angle θ, for example, approximately 2 degrees. The lower end of the cut crowning surface 24b at the lower end portion of the second raceway surface 24 is connected to the large inner peripheral surface 27 via a lower curved inner peripheral surface (chamfer surface) 29 which is a curved inner peripheral surface. It is smoothly connected to the upper end.

また、外輪11には周方向に間隔をおいて並んで位置する複数の貫通孔30が上下面に貫通して形成されている。各貫通孔30にボルト等の取付部材（図示せず）が挿通され、これら取付部材にて作業装置の旋回作業部が外輪11に固定して取り付けられる。   Further, the outer ring 11 is formed with a plurality of through holes 30 that are arranged side by side in the circumferential direction so as to penetrate the upper and lower surfaces. A mounting member (not shown) such as a bolt is inserted into each through-hole 30, and the turning work portion of the working device is fixedly attached to the outer ring 11 with these mounting members.

さらに、外輪11にはころ投入用貫通孔（図示せず）が内外周面に貫通して形成され、組立て時にころ投入用貫通孔からころ13，14が投入され、投入後そのころ投入用貫通孔は閉塞部材にて閉塞される。   Further, a roller insertion through hole (not shown) is formed in the outer ring 11 so as to penetrate the inner and outer peripheral surfaces, and rollers 13 and 14 are inserted from the roller insertion through hole at the time of assembly. The hole is closed by a closing member.

内輪12は、この内輪12の周方向に沿って位置しこの内輪12の径方向外方に向って開口し外輪溝部21と離間対向する断面略Ｖ字状の内輪溝部31を外周面側に有している。内輪溝部31の上側には反転ころ14が転動する上側軌道面である第３軌道面33が形成され、内輪溝部31の下側には主ころ13が転動する下側軌道面である第４軌道面34が形成されている。内輪溝部31の溝底部には、略円弧状の逃げ溝部35が形成されている。   The inner ring 12 has an inner ring groove portion 31 having a substantially V-shaped cross section that is located along the circumferential direction of the inner ring 12 and that opens outward in the radial direction of the inner ring 12 and faces the outer ring groove portion 21 on the outer peripheral surface side. is doing. A third raceway surface 33, which is an upper raceway surface on which the reverse roller 14 rolls, is formed above the inner ring groove portion 31, and a lower raceway surface, on which the main roller 13 rolls, is formed below the inner ring groove portion 31. Four raceway surfaces 34 are formed. A substantially arc-shaped escape groove 35 is formed at the groove bottom of the inner ring groove 31.

また、内輪12の外周面のうち内輪溝部31より上方の部分である外周面上部には径小内周面26と間隙41を介して離間対向する円筒状の径小外周面36が形成され、内輪12の外周面のうち内輪溝部31より下方の部分である外周面下部には径大内周面27と間隙42を介して離間対向し径小外周面36より径大な円筒状の径大外周面37が形成されている。なお、内輪12の径大外周面37の径寸法は、外輪11の径小内周面26の径寸法より大きい。   In addition, a cylindrical small-diameter outer peripheral surface 36 is formed on the outer peripheral surface of the outer ring of the inner ring 12 that is above the inner ring groove 31 and is opposed to the small-diameter inner peripheral surface 26 with a gap 41 therebetween. Of the outer peripheral surface of the inner ring 12, the lower part of the outer peripheral surface, which is a part below the inner ring groove portion 31, is opposed to the large-diameter inner peripheral surface 27 via the gap 42, and is opposed to the large-diameter cylindrical surface larger than the small outer peripheral surface 36. An outer peripheral surface 37 is formed. The diameter dimension of the large-diameter outer peripheral surface 37 of the inner ring 12 is larger than the diameter dimension of the small-diameter inner peripheral surface 26 of the outer ring 11.

そして、第３軌道面33の上下両端部には、端縁側に向ってドロップ量が直接的に大きくなるカットクラウニングが施されることにより傾斜面状のカットクラウニング面33a，33bがそれぞれ形成され、この第３軌道面33のうちカットクラウニング面33a，33bが形成されていない平坦な部分が平坦軌道面33cとなっている。また、断面図で見た場合にカットクラウニング面33a，33bの平坦軌道面33cに対する傾斜角度は、前記傾斜角度θと同じ角度で、例えば略２度である。なお、第３軌道面33の上端部のカットクラウニング面33aの上端は、湾曲面状の湾曲外周面である上側湾曲外周面（チャンファ面）38を介して径小外周面36の下端に滑らかに繋がっている。   Then, at both the upper and lower ends of the third track surface 33, cut crowning surfaces 33a and 33b having inclined surface shapes are formed by performing cut crowning in which the drop amount increases directly toward the edge side, respectively. A flat portion of the third raceway surface 33 where the cut crowning surfaces 33a and 33b are not formed is a flat raceway surface 33c. When viewed in a cross-sectional view, the inclination angle of the cut crowning surfaces 33a and 33b with respect to the flat track surface 33c is the same as the inclination angle θ, for example, approximately 2 degrees. The upper end of the cut crowning surface 33a at the upper end portion of the third raceway surface 33 is smoothly provided on the lower end of the small-diameter outer peripheral surface 36 via the upper curved outer peripheral surface (chamber surface) 38, which is a curved outer peripheral surface. It is connected.

同様に、第４軌道面34の上下両端部には、端縁側に向ってドロップ量が直接的に大きくなるカットクラウニングが施されることにより傾斜面状のカットクラウニング面34a，34bがそれぞれ形成され、この第４軌道面34のうちカットクラウニング面34a，34bが形成されていない平坦な部分が平坦軌道面34cとなっている。また、断面図で見た場合にカットクラウニング面34a，34bの平坦軌道面34cに対する傾斜角度は、前記傾斜角度θと同じ角度で、例えば略２度である。なお、第４軌道面34の下端部のカットクラウニング面34bの下端は、湾曲面状の湾曲外周面である下側湾曲外周面（チャンファ面）39を介して径大外周面37の上端に滑らかに繋がっている。   Similarly, inclined crown-shaped cut crowning surfaces 34a and 34b are formed at both upper and lower ends of the fourth raceway surface 34 by applying cut crowning that directly increases the drop amount toward the edge side. Of the fourth raceway surface 34, a flat portion where the cut crowning surfaces 34a and 34b are not formed is a flat raceway surface 34c. When viewed in a cross-sectional view, the inclination angle of the cut crowning surfaces 34a, 34b with respect to the flat track surface 34c is the same angle as the inclination angle θ, for example, approximately 2 degrees. The lower end of the cut crowning surface 34b at the lower end of the fourth raceway surface 34 is smooth to the upper end of the large-diameter outer peripheral surface 37 via a lower curved outer peripheral surface (chamfer surface) 39 that is a curved outer peripheral surface. It is connected to.

また、内輪12に周方向に間隔をおいて並んで位置する複数の貫通孔40が上下面に貫通して形成されている。各貫通孔40にボルト等の取付部材（図示せず）が挿通され、これら取付部材にて作業装置の支持部が内輪12に固定して取り付けられる。さらに、内輪12の内周面には、作業装置の駆動手段（旋回用モータ等）の出力歯車が噛み合うギア部43が形成されている。   In addition, a plurality of through-holes 40 that are arranged side by side in the circumferential direction in the inner ring 12 are formed through the upper and lower surfaces. A mounting member (not shown) such as a bolt is inserted into each through hole 40, and the support portion of the working device is fixedly mounted to the inner ring 12 with these mounting members. Furthermore, a gear portion 43 is formed on the inner peripheral surface of the inner ring 12 so as to mesh with an output gear of driving means (such as a turning motor) of the working device.

主ころ13および反転ころ14は、いずれも同一の形状のもので、例えば外周面が略円筒状に形成され軸方向両端側にクラウニング面を有しない円筒ころ（クラウニング無しのストレートころ）である。そして、主ころ13は、外輪溝部21と内輪溝部31とで挟持され、外周面が第１軌道面23および第４軌道面34に線状に接触し、下方側の軸方向端面が第２軌道面24に面状に接触する。また、反転ころ14は、外輪溝部21と内輪溝部31とで挟持され、外周面が第２軌道面24および第３軌道面33に線状に接触し、下方側の軸方向端面が第４軌道面34に面状に接触する。さらに、各ころ13，14の外周面の軸方向両端部には湾曲面状、例えば円弧面状のチャンファ面（面取り面）51が形成され、この各ころ13，14の外周面のうちチャンファ面51が形成されていない部分が円筒状の円筒外周面53となっている。   The main roller 13 and the reverse roller 14 are both of the same shape, and are, for example, cylindrical rollers (straight rollers without crowning) whose outer peripheral surfaces are formed in a substantially cylindrical shape and do not have crowning surfaces on both ends in the axial direction. The main roller 13 is sandwiched between the outer ring groove portion 21 and the inner ring groove portion 31, the outer peripheral surface linearly contacts the first track surface 23 and the fourth track surface 34, and the lower axial end surface is the second track. The surface 24 comes into contact with the surface. The reversing roller 14 is sandwiched between the outer ring groove portion 21 and the inner ring groove portion 31, the outer peripheral surface linearly contacts the second track surface 24 and the third track surface 33, and the lower axial end surface is the fourth track. The surface 34 is brought into contact with the surface. Further, a chamfer surface (chamfered surface) 51 having a curved surface, for example, a circular arc surface, is formed at both axial ends of the outer peripheral surfaces of the rollers 13 and 14, and the chamfer surface of the outer peripheral surfaces of the rollers 13 and 14 is formed. A portion where 51 is not formed is a cylindrical outer peripheral surface 53 of a cylindrical shape.

なお、図３に示されるように、主ころ13の一方のチャンファ面51は第１軌道面23のカットクラウニング面23aと間隙51aを介して離間対向し、主ころ13の他方のチャンファ面51は第４軌道面34のカットクラウニング面34bと間隙51aを介して離間対向している。また各カットクラウニング面23a，23bの軸方向長さ（例えば６ｍｍ）は、平坦軌道面23cの軸方向長さ（例えば１８ｍｍ）の略３分の１が好ましい。他のカットクラウニング面24a，24b，33a，33b，34a，34bの軸方向長さに関しても同様である。   As shown in FIG. 3, one chamfer surface 51 of the main roller 13 is opposed to the cut crowning surface 23a of the first raceway surface 23 through a gap 51a, and the other chamfer surface 51 of the main roller 13 is The fourth track surface 34 is opposed to the cut crowning surface 34b through the gap 51a. Further, the axial length (for example, 6 mm) of each cut crowning surface 23a, 23b is preferably about one third of the axial length (for example, 18 mm) of the flat track surface 23c. The same applies to the axial lengths of the other cut crowning surfaces 24a, 24b, 33a, 33b, 34a, 34b.

そして、主ころ13に主負荷が作用した状態時、つまり旋回作業部による作業時には、図３に示すように、主ころ13の外周面に作用する面圧は軸方向略全長にわたって略一定で、主ころ13の外周面にエッジロードが生じない。またこのとき、反転ころ14には反転側負荷が作用するが、反転ころ14についても主ころ13と同様、反転ころ14の外周面に作用する面圧は軸方向略全長にわたって略一定で、反転ころ14の外周面にエッジロードが生じない。   And, when the main load is applied to the main roller 13, that is, when working by the swivel working part, as shown in FIG. 3, the surface pressure acting on the outer peripheral surface of the main roller 13 is substantially constant over substantially the entire length in the axial direction. Edge load does not occur on the outer peripheral surface of the main roller 13. At this time, the load on the reverse side acts on the reversing roller 14, but the surface pressure acting on the outer peripheral surface of the reversing roller 14 is also substantially constant over the entire length in the axial direction. No edge load occurs on the outer peripheral surface of the roller 14.

また、図４に示すように、主ころ13の外周面と第４軌道面34との有効接触長さLe1は、従来の有効接触長さLe2に比べてδ分だけ長くなっている。なお同様に主ころ13の外周面と第１軌道面34との有効接触長さLe1も従来の有効接触長さLe2に比べてδ分だけ長くなっている。   As shown in FIG. 4, the effective contact length Le1 between the outer peripheral surface of the main roller 13 and the fourth raceway surface 34 is longer by δ than the conventional effective contact length Le2. Similarly, the effective contact length Le1 between the outer peripheral surface of the main roller 13 and the first raceway surface 34 is longer by δ than the conventional effective contact length Le2.

次に、旋回座軸受10の作用等を説明する。   Next, the operation of the swivel seat bearing 10 will be described.

旋回座軸受10を備えた作業装置を使用して旋回作業部で作業をする場合、旋回座軸受10には主にアキシアル荷重およびモーメントが負荷され、旋回座軸受10の各ころ13，14には図５に矢印で示す荷重分布が生じる。   When working in the swivel working part using the working device equipped with the swivel bearing 10, the swivel bearing 10 is mainly subjected to an axial load and moment, and the rollers 13, 14 of the swivel bearing 10 are A load distribution indicated by an arrow in FIG. 5 is generated.

この場合、モーメント前方では、外輪11が上側軌道面である第１軌道面23で、内輪12が下側軌道面である第４軌道面34で主ころ13の荷重を受ける。モーメント後方では、外輪11が持ち上げられ下側軌道面である第２軌道面24で、内輪12が上側軌道面である第３軌道面33で反転ころ14の荷重を受ける。そして、前方部の主ころ13はQ1の最大荷重を受け、後方部の反転ころ14はQ2の最大荷重を受ける。このように、主負荷が作用する主ころ13は大きな荷重を受けるが、反転側負荷が作用する反転ころ14は小さな荷重しか受けない。このため、旋回座軸受10の許容荷重は、大きな荷重を受ける主ころ13で決定される。   In this case, in front of the moment, the load of the main roller 13 is received by the first raceway surface 23 in which the outer ring 11 is the upper raceway surface and the fourth raceway surface 34 in which the inner ring 12 is the lower raceway surface. Behind the moment, the outer ring 11 is lifted and the load of the reversing roller 14 is received by the second raceway surface 24 which is the lower raceway surface and the inner race 12 is received by the third raceway surface 33 which is the upper raceway surface. The main roller 13 at the front part receives the maximum load of Q1, and the reverse roller 14 at the rear part receives the maximum load of Q2. As described above, the main roller 13 to which the main load acts receives a large load, whereas the reverse roller 14 to which the reverse load acts receives only a small load. For this reason, the allowable load of the swivel seat bearing 10 is determined by the main roller 13 that receives a large load.

また、旋回作業部による作業時において旋回座軸受10にアキシアル荷重およびモーメントが負荷されても、各ころ13，14の外周面にはエッジロード（局部荷重）が生じない。   Further, even when an axial load and a moment are applied to the swivel bearing 10 during work by the swivel working part, no edge load (local load) is generated on the outer peripheral surfaces of the rollers 13 and 14.

そして、このように旋回座軸受10によれば、第１軌道面23、第２軌道面24、第３軌道面33および第４軌道面34の各々には上下両端部にカットクラウニング面23a，23b，24a，24b，33a，33b，34a，34bが形成されているため、旋回作業部による作業時（負荷作用時）に主ころ13の外周面および反転ころ14の外周面にエッジロードが生じることを防止でき、耐久性の向上を図ることができる。   As described above, according to the swivel bearing 10, the first raceway surface 23, the second raceway surface 24, the third raceway surface 33, and the fourth raceway surface 34 are cut crowned surfaces 23a and 23b at both upper and lower ends. , 24a, 24b, 33a, 33b, 34a, 34b are formed, and edge load is generated on the outer peripheral surface of the main roller 13 and the outer peripheral surface of the reverse roller 14 during work by the swivel working part (load operation). Can be prevented, and durability can be improved.

また、旋回作業部による作業時に主ころ13の外周面が有効接触長さLe1（＞Le2）をもって外輪11の第１軌道面23および内輪12の第４軌道面34に対して接触するため、従来に比べて負荷作用時の許容荷重を高めることができる。   Further, since the outer peripheral surface of the main roller 13 is in contact with the first raceway surface 23 of the outer ring 11 and the fourth raceway surface 34 of the inner ring 12 at the time of work by the turning work unit, the conventional contact surface Le1 (> Le2). The allowable load at the time of load action can be increased compared to.

さらに、クラウニング無しのころ13，14をエッジロードなしに使用できるため、ころ13，14に特殊な機械で手間のかかるクラウニング加工を行う必要がなく、各軌道面23，24，33，34に一般の機械で容易にクラウニング加工ができ、製造性も良好で、製造コストの低減を図ることができる。   Furthermore, since rollers 13 and 14 without crowning can be used without edge loading, it is not necessary to perform complicated crowning processing on rollers 13 and 14 with a special machine, and general use for each raceway surface 23, 24, 33 and 34 This machine can be easily crowned, has good manufacturability, and can reduce manufacturing costs.

なお、上記一実施の形態では、各ころ13，14は、外周面が略円筒状に形成された円筒ころである場合について説明したが、例えば図６に示すように、外周面が略截頭円錐状に形成されたクラウニング無し円錐ころであってもよい。   In the above-described embodiment, the case where each of the rollers 13 and 14 is a cylindrical roller having an outer peripheral surface formed in a substantially cylindrical shape has been described. However, for example, as shown in FIG. It may be a tapered roller without crowning formed in a conical shape.

つまりこの図６に示す截頭略円錐状の各ころ13，14は、いずれも同一の形状のもので、外周面の軸方向両端部に湾曲面状、例えば円弧面状のチャンファ面（面取り面）51が形成され、外周面のうちチャンファ面51が形成されていない部分が截頭円錐状の円錐外周面54となっている。   That is, each of the substantially conical rollers 13 and 14 shown in FIG. 6 has the same shape, and has a chamfered surface (a chamfered surface) having a curved surface, for example, an arc surface, at both axial ends of the outer peripheral surface. ) 51 and the portion of the outer peripheral surface where the chamfer surface 51 is not formed is a frustoconical conical outer peripheral surface 54.

また、主ころ13の大径側の端面（一方の端面）である大端面56は第３軌道面33と対向し、主ころ13の小径側の端面（他方の端面）である小端面57は第２軌道面24と対向している。反転ころ14の大径側の端面（一方の端面）である大端面58は第１軌道面23と対向し、反転ころ14の小径側の端面（他方の端面）である小端面59は第４軌道面34と対向している。なお、ころ13，14の大端面56，58は、非常に大きなＲ面または円錐面となっている。   A large end surface 56 that is an end surface (one end surface) on the large diameter side of the main roller 13 faces the third raceway surface 33, and a small end surface 57 that is an end surface on the small diameter side (the other end surface) of the main roller 13 is It faces the second raceway surface 24. A large end surface 58 that is an end surface (one end surface) on the large diameter side of the reversing roller 14 faces the first raceway surface 23, and a small end surface 59 that is an end surface on the small diameter side (the other end surface) of the reversing roller 14 is the fourth. Opposite the track surface 34. The large end surfaces 56 and 58 of the rollers 13 and 14 are very large R surfaces or conical surfaces.

図６に示す一例のころ13，14の寸法は、例えば外径（大）φ３０ｍｍ、外径（小）φ２８ｍｍ、全幅２９ｍｍ、円筒外周面54の軸方向長さ２７ｍｍ、チャンファ面51の軸方向長さ１ｍｍである。   6 are, for example, an outer diameter (large) φ30 mm, an outer diameter (small) φ28 mm, an overall width 29 mm, an axial length 27 mm of the cylindrical outer peripheral surface 54, and an axial length of the chamfer surface 51. The thickness is 1 mm.

そして、この図６の円錐ころ型クロスローラ旋回座（旋回座軸受10）であっても、第１軌道面23、第２軌道面24、第３軌道面33および第４軌道面34の各々には上下両端部にカットクラウニング面23a，23b，24a，24b，33a，33b，34a，34bが形成されているため、旋回作業部による作業時（負荷作用時）に主ころ13の外周面および反転ころ14の外周面にエッジロードが生じることを防止でき、耐久性の向上を図ることができる等、上記一実施の形態と同様の作用効果を奏することができる。   Even in the tapered roller type cross roller swivel seat (swivel seat bearing 10) of FIG. 6, the first raceway surface 23, the second raceway surface 24, the third raceway surface 33, and the fourth raceway surface 34 are provided. Since the cut crowning surfaces 23a, 23b, 24a, 24b, 33a, 33b, 34a, 34b are formed at both the upper and lower ends, the outer peripheral surface of the main roller 13 and the inversion are reversed during work by the swivel work part (load operation) It is possible to prevent the edge load from being generated on the outer peripheral surface of the roller 14 and to achieve the same effects as those of the above-described one embodiment, such as the improvement of durability.

しかもこの図６の構成では、主ころ13および反転ころ14の各々は外周面が略截頭円錐状に形成された円錐ころであるため、エッジ当たり等によるかじりが起こりにくく、耐久性の向上をより一層図ることができる。   In addition, in the configuration of FIG. 6, each of the main roller 13 and the reverse roller 14 is a tapered roller having an outer peripheral surface formed in a substantially frustoconical shape. More can be achieved.

つまり、図７（ａ）ではカットクラウニング面がない場合を示すが、内輪12および外輪11の荷重pi、poによって主ころ13が大径側に荷重fで押され、主ころ13の大端面56が内輪12の第３軌道面33に押し付けられ、エッジeで応力集中が起きる。これに対し、図７（ｂ）に示すように、内輪13の第３軌道面33にカットクラウニング面33b（カットクラウニング部分a2）があると、エッジでの当たりが発生せず、エッジ当たり等によるかじりが起こりにくい。図７（ｂ）中のa1、a2、c1、c2はカットクラウニング部分であり、bとdはストレート部分である。主ころ13の大端面56が非常に大きなＲ面または円すい面であっても同じ効果が期待できる、なお、反転ころ14に関しても同様であり、外輪11の第１軌道面23にカットクラウニング面23bがあると、エッジでの当たりが発生せず、エッジ当たり等によるかじりが起こりにくい。   That is, FIG. 7A shows a case where there is no cut crowning surface, but the main roller 13 is pushed to the large diameter side by the load f by the loads pi and po of the inner ring 12 and the outer ring 11, and the large end surface 56 of the main roller 13 Is pressed against the third raceway surface 33 of the inner ring 12, and stress concentration occurs at the edge e. On the other hand, as shown in FIG. 7 (b), if there is a cut crowning surface 33b (cut crowning portion a2) on the third raceway surface 33 of the inner ring 13, contact with the edge does not occur, but due to contact with the edge, etc. It is difficult to galling. In FIG. 7B, a1, a2, c1, and c2 are cut crown portions, and b and d are straight portions. The same effect can be expected even if the large end surface 56 of the main roller 13 is a very large R surface or conical surface. The same applies to the reversing roller 14, and the first raceway surface 23 of the outer ring 11 has a cut crowning surface 23b. If there is, there is no hit at the edge, and galling due to the edge is less likely to occur.

また、上記各実施の形態では、主ころ13と反転ころ14とが同一形状である場合について説明したが、例えば主ころ13と反転ころ14とが異なる形状であってもよく、例えば主ころ13の全幅が反転ころ14の全幅より短い場合や、逆に主ころ13の全幅が反転ころ14の全幅より長い場合でもよい。   In each of the above embodiments, the case where the main roller 13 and the reverse roller 14 have the same shape has been described. However, for example, the main roller 13 and the reverse roller 14 may have different shapes. For example, the main roller 13 The total width of the main roller 13 may be shorter than the total width of the reverse roller 14, or conversely, the total width of the main roller 13 may be longer than the total width of the reverse roller 14.

さらに、水平方向に対する回転中心軸線ａ，ｂの角度α，βは４５°には限定されず、例えば４５°より小さくてもよい。   Furthermore, the angles α and β of the rotation center axes a and b with respect to the horizontal direction are not limited to 45 °, and may be smaller than 45 °, for example.

また、各ころ13，14を外輪11および内輪12間に周方向に沿って１列配列した構成には限定されず、例えば周方向に沿って上下に複数段状（例えば２段）に配列した構成でもよい。   The rollers 13 and 14 are not limited to a configuration in which one row is arranged between the outer ring 11 and the inner ring 12 along the circumferential direction. For example, the rollers 13 and 14 are arranged in a plurality of stages (for example, two stages) vertically along the circumferential direction. It may be configured.

本発明の一実施の形態に係る旋回座軸受の断面図である。It is sectional drawing of the swivel seat bearing which concerns on one embodiment of this invention. 同上旋回座軸受の部分断面図である。It is a fragmentary sectional view of a slewing seat bearing same as the above. 同上旋回座軸受の部分断面図である。It is a fragmentary sectional view of a slewing seat bearing same as the above. 同上旋回座軸受の主ころの軌道面への接触状態を示す図である。It is a figure which shows the contact state to the raceway surface of the main roller of a slewing seat bearing same as the above. 同上旋回座軸受のころに生じる荷重分布を示す図である。It is a figure which shows the load distribution which arises in the roller of a slewing seat bearing same as the above. 本発明の他の実施の形態に係る旋回座軸受の部分断面図である。It is a fragmentary sectional view of the swivel seat bearing which concerns on other embodiment of this invention. （ａ）はカットクラウニング面がない場合における大端面の軌道面への接触状態を示す図であり、（ｂ）はカットクラウニング面がある場合における大端面の軌道面への接触状態を示す図である。(A) is a figure which shows the contact state to the track surface of a big end surface when there is no cut crowning surface, (b) is a figure which shows the contact state to the track surface of a big end surface when there is a cut crowning surface. is there. 従来の主ころの軌道面への接触状態を示す図である。It is a figure which shows the contact state to the track surface of the conventional main roller.

符号の説明Explanation of symbols

10 旋回座軸受
11 外輪
12 内輪
13 主ころ
14 反転ころ
21 外輪溝部
23 第１軌道面
23a，23b カットクラウニング面
24 第２軌道面
24a，24b カットクラウニング面
26 径小内周面
27 径大内周面
31 内輪溝部
33 第３軌道面
33a，33b カットクラウニング面
34 第４軌道面
34a，34b カットクラウニング面
36 径小外周面
37 径大外周面 10 Swivel seat bearing
11 Outer ring
12 Inner ring
13 Lord
14 Reverse roller
21 Outer ring groove
23 First track surface
23a, 23b Cut crowning surface
24 Second track surface
24a, 24b Cut crown surface
26 diameter small inner peripheral surface
27 diameter inner peripheral surface
31 Inner ring groove
33 Third track surface
33a, 33b Cut crowning surface
34 Fourth track surface
34a, 34b Cut crown surface
36 diameter small outer peripheral surface
37 diameter outer circumference

Claims (2)

第１軌道面および第２軌道面が形成された断面略Ｖ字状の外輪溝部を内周面側に有する外輪と、
この外輪の内方に配設され、第３軌道面および第４軌道面が形成された断面略Ｖ字状の内輪溝部を外周面側に有する内輪と、
前記外輪溝部と前記内輪溝部との間に回転可能に配設され、外周面が前記第１軌道面および前記第４軌道面に接触し、主負荷が作用する複数の主ころと、
前記外輪溝部と前記内輪溝部との間に回転可能に配設され、外周面が前記第２軌道面および前記第３軌道面に接触し、反転側負荷が作用する複数の反転ころとを備え、
前記外輪は、
内周面のうち前記外輪溝部より上方の部分に形成された円筒状の径小内周面と、
内周面のうち前記外輪溝部より下方の部分に形成され、前記径小内周面より径大な円筒状の径大内周面とを有し、
前記内輪は、
外周面のうち前記内輪溝部より上方の部分に形成された円筒状の径小外周面と、
外周面のうち前記内輪溝部より下方の部分に形成され、前記径小外周面より径大な円筒状の径大外周面とを有し、
前記第１軌道面、前記第２軌道面、前記第３軌道面および前記第４軌道面の各々には、上下両端部にカットクラウニング面が形成されている
ことを特徴とする旋回座軸受。 An outer ring having a substantially V-shaped outer ring groove portion on the inner peripheral surface side in which the first raceway surface and the second raceway surface are formed;
An inner ring that is disposed on the inner side of the outer ring and has an inner ring groove portion having a substantially V-shaped cross section on the outer peripheral surface side, on which the third raceway surface and the fourth raceway surface are formed;
A plurality of main rollers that are rotatably arranged between the outer ring groove portion and the inner ring groove portion, an outer peripheral surface is in contact with the first raceway surface and the fourth raceway surface, and a main load acts;
A plurality of reversing rollers that are rotatably disposed between the outer ring groove portion and the inner ring groove portion, have an outer peripheral surface in contact with the second raceway surface and the third raceway surface, and a load on the reversing side acts;
The outer ring is
A cylindrical small-diameter inner peripheral surface formed in a portion of the inner peripheral surface above the outer ring groove portion;
The inner peripheral surface is formed in a portion below the outer ring groove portion, and has a cylindrical large-diameter inner peripheral surface having a diameter larger than the small-diameter inner peripheral surface,
The inner ring is
A cylindrical small-diameter outer peripheral surface formed in a portion of the outer peripheral surface above the inner ring groove portion,
The outer peripheral surface is formed in a portion below the inner ring groove portion, and has a cylindrical large outer peripheral surface having a diameter larger than the small outer peripheral surface,
Each of the first raceway surface, the second raceway surface, the third raceway surface, and the fourth raceway surface has a cut crowning surface formed at both upper and lower ends. 主ころおよび反転ころの各々は、外周面が略截頭円錐状に形成された円錐ころである
ことを特徴とする請求項１記載の旋回座軸受。 The swivel bearing according to claim 1, wherein each of the main roller and the reverse roller is a tapered roller having an outer peripheral surface formed in a substantially truncated cone shape.
JP2008326862A 2008-12-24 2008-12-24 Revolving seat bearing Pending JP2010151152A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012002058A1 (en) 2010-07-01 2012-01-05 Ｕｄトラックス株式会社 Power storage cell and power storage module
JP2013160308A (en) * 2012-02-06 2013-08-19 Nippon Thompson Co Ltd Turning bearing
WO2017109826A1 (en) * 2015-12-21 2017-06-29 株式会社ハーモニック・ドライブ・システムズ Crossed roller bearing
WO2021006209A1 (en) * 2019-07-11 2021-01-14 Ntn株式会社 Cross roller bearing
WO2022149523A1 (en) * 2021-01-06 2022-07-14 Ntn株式会社 Cross roller bearing

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JPH05280537A (en) * 1992-03-31 1993-10-26 Nippon Thompson Co Ltd Rolling guide unit
JPH08232960A (en) * 1995-02-28 1996-09-10 Ntn Corp Double row roller bearing for railway rolling stock
JPH10220466A (en) * 1997-02-03 1998-08-21 Antetsukusu:Kk Slewing seat bearing
JP2004324733A (en) * 2003-04-23 2004-11-18 Ntn Corp Cross roller bearing

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05280537A (en) * 1992-03-31 1993-10-26 Nippon Thompson Co Ltd Rolling guide unit
JPH08232960A (en) * 1995-02-28 1996-09-10 Ntn Corp Double row roller bearing for railway rolling stock
JPH10220466A (en) * 1997-02-03 1998-08-21 Antetsukusu:Kk Slewing seat bearing
JP2004324733A (en) * 2003-04-23 2004-11-18 Ntn Corp Cross roller bearing

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012002058A1 (en) 2010-07-01 2012-01-05 Ｕｄトラックス株式会社 Power storage cell and power storage module
JP2013160308A (en) * 2012-02-06 2013-08-19 Nippon Thompson Co Ltd Turning bearing
WO2017109826A1 (en) * 2015-12-21 2017-06-29 株式会社ハーモニック・ドライブ・システムズ Crossed roller bearing
CN108368876A (en) * 2015-12-21 2018-08-03 谐波传动***有限公司 Crossed roller bearing
JPWO2017109826A1 (en) * 2015-12-21 2018-09-13 株式会社ハーモニック・ドライブ・システムズ Cross roller bearing
US10309453B2 (en) 2015-12-21 2019-06-04 Harmonic Drive Systems Inc. Crossed roller bearing
CN108368876B (en) * 2015-12-21 2019-07-30 谐波传动***有限公司 Crossed roller bearing
WO2021006209A1 (en) * 2019-07-11 2021-01-14 Ntn株式会社 Cross roller bearing
WO2022149523A1 (en) * 2021-01-06 2022-07-14 Ntn株式会社 Cross roller bearing

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