JP4536675B2 - Swing bearing - Google Patents

Swing bearing Download PDF

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JP4536675B2
JP4536675B2 JP2006087157A JP2006087157A JP4536675B2 JP 4536675 B2 JP4536675 B2 JP 4536675B2 JP 2006087157 A JP2006087157 A JP 2006087157A JP 2006087157 A JP2006087157 A JP 2006087157A JP 4536675 B2 JP4536675 B2 JP 4536675B2
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raceway
hole
bearing
rollers
shoulder
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JP2007263194A (en
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修一 梶川
貞経 風間
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NTN 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/067—Fixing them in a housing
    • 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
    • F16C19/502—Other types of ball or roller bearings with rolling elements in rows not forming a full circle
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Description

本発明は、固定部材に固定される軌道輪の凹円弧状の軌道面に複数のころを保持器に保持して配列し、可動部材の凸円弧状部を揺動自在に支持する揺動軸受に関する。   The present invention relates to a rocking bearing in which a plurality of rollers are held and arranged on a concave arcuate raceway surface of a raceway ring fixed to a fixed member, and a convex arcuate portion of a movable member is slidably supported. About.

建設機械や農業機械等に使用される油圧ポンプ、油圧モータ、ハイドロスタティックトランスミッション等には、固定部材に固定される軌道輪の凹円弧状の軌道面に複数のころを保持器に保持して配列し、斜板等の可動部材を揺動自在に支持する揺動軸受が組み込まれている。   For hydraulic pumps, hydraulic motors, hydrostatic transmissions, etc. used in construction and agricultural machinery, etc., a plurality of rollers are arranged in a cage on the concave arc-shaped raceway surface of a raceway ring fixed to a fixed member. In addition, a rocking bearing is built in which a movable member such as a swash plate is rockably supported.

この種の揺動軸受には、製造コストを低減するために、従来は金属の削り出し品とされていた内径面に凹円弧状の軌道面が設けられた軌道輪を金属板のプレス成形品として、軌道面にエンボス加工を施し、その裏面側の外径面に突出する突出部を成形して、この突出部を固定部材の凹円弧状部に設けた位置決め穴に係合させ、軌道輪を固定部材に位置決めするようにしたものがある（例えば、特許文献１参照）。   In order to reduce the manufacturing cost, this type of oscillating bearing is formed by pressing a bearing ring having a concave arc-shaped raceway surface on the inner diameter surface, which has conventionally been a metal machined product, into a metal plate press-molded product. The embossing is performed on the raceway surface, a projecting portion projecting to the outer diameter surface on the back surface side is formed, and the projecting portion is engaged with a positioning hole provided in the concave arc-shaped portion of the fixing member. Is positioned on the fixing member (for example, see Patent Document 1).

また、軌道輪を金属材料の削り出し品または金属板のプレス成形品として、軌道面に貫通孔を形成し、この貫通孔に裏面側の外径面に突出するピンを嵌め込んで、このピンを固定部材の凹円弧状部に設けた位置決め穴に係合させ、軌道輪を固定部材に位置決めするようにしたものもある（例えば、特許文献２参照）。   In addition, the race is made of a metal material cut or a metal plate press-molded product, and a through hole is formed in the race surface, and a pin protruding from the outer diameter surface on the back side is fitted into this through hole. In some cases, the raceway is engaged with a positioning hole provided in the concave arcuate portion of the fixing member to position the track ring on the fixing member (see, for example, Patent Document 2).

特開２００２−２８６０４１号公報（第２図）JP 2002-286041 A (FIG. 2) 特開２００４−１００８０５号公報（第４図）Japanese Patent Laid-Open No. 2004-100805 (FIG. 4)

特許文献１に記載された軌道輪を金属板のプレス成形品とした揺動軸受は、大幅に製造コストを低減できるが、エンボス加工で突出部を成形するときに軌道面に形成される陥没穴の周縁で、転動するころとの間にエッジロードが発生しやすく、軌道面の陥没穴の周縁やころの転動面に、過大な局部面圧による剥離損傷が生じる恐れがある。   The rocking bearing in which the bearing ring described in Patent Document 1 is a metal plate press-molded product can greatly reduce the manufacturing cost, but the recessed hole formed in the raceway surface when the protrusion is formed by embossing An edge load is likely to occur between the peripheral edge of the roller and the rolling roller, and there is a risk that peeling damage due to excessive local surface pressure may occur on the peripheral edge of the recessed hole on the raceway surface and the rolling surface of the roller.

また、特許文献２に記載された揺動軸受においても、位置決め用のピンを嵌め込む軌道面の貫通孔の周縁で、転動するころとの間にエッジロードが発生しやすい。   Also in the rocking bearing described in Patent Document 2, an edge load is likely to occur between the rolling roller at the periphery of the through hole of the raceway surface into which the positioning pin is fitted.

そこで、本発明の課題は、位置決め用の突出部やピンを設けるときに形成される軌道面の陥没穴や貫通孔の周縁で、転動するころとの間にエッジロードが発生しないようにすることである。   Accordingly, an object of the present invention is to prevent an edge load from being generated between the rolling roller at the recessed hole of the raceway surface and the periphery of the through hole formed when the positioning protrusion and the pin are provided. That is.

上記の課題を解決するために、本発明は、内径面に凹円弧状の軌道面が設けられた軌道輪と、この軌道輪の軌道面に配列された複数のころと、これらのころを転動自在に保持する保持器とからなり、前記軌道輪を固定部材の凹円弧状部に固定して、前記複数のころで可動部材の凸円弧状部を揺動自在に支持するようにし、前記軌道輪を金属板のプレス成形品として、前記軌道面にエンボス加工を施して、その裏面側の外径面に突出する突出部を成形し、この突出部を前記固定部材の凹円弧状部に設けた位置決め穴に係合させて、前記軌道輪を前記固定部材に位置決めした揺動軸受において、前記エンボス加工で突出部を成形するときに、エンボス加工のダイスに肩Ｒ部を設けて、前記軌道面に形成される陥没穴の周縁に肩Ｒ部を設けた構成を採用した。 In order to solve the above problems, the present invention provides a bearing ring having a concave arc-shaped raceway surface on an inner diameter surface, a plurality of rollers arranged on the raceway surface of the raceway ring, and rolling these rollers. A retainer that is movably held, the race is fixed to a concave arc-shaped portion of a fixed member, and the convex arc-shaped portion of the movable member is swingably supported by the plurality of rollers, The raceway is a metal plate press-molded product, and the raceway surface is embossed to form a projecting portion that projects to the outer diameter surface on the back side, and this projecting portion is formed into a concave arc-shaped portion of the fixing member. In the rocking bearing in which the bearing ring is positioned on the fixed member by engaging with the positioning hole provided, when the protrusion is formed by the embossing, a shoulder R portion is provided on the embossing die, A configuration in which a shoulder R part is provided at the periphery of the depression hole formed on the raceway surface. And use.

また、本発明は、内径面に凹円弧状の軌道面が設けられた軌道輪と、この軌道輪の軌道面に配列された複数のころと、これらのころを転動自在に保持する保持器とからなり、前記軌道輪を固定部材の凹円弧状部に固定して、前記複数のころで可動部材の凸円弧状部を揺動自在に支持するようにし、前記軌道輪の軌道面に貫通孔を形成して、この貫通孔に裏面側の外径面に突出するピンを嵌め込み、このピンを前記固定部材の凹円弧状部に設けた位置決め穴に係合させて、前記軌道輪を前記固定部材に位置決めした揺動軸受において、前記貫通孔を打ち抜き加工で形成し、打ち抜き加工のポンチとダイスのクリアランスを大きくして、前記軌道面に形成される貫通孔の周縁に肩Ｒ部を設けた構成も採用した。 In addition, the present invention provides a bearing ring having a concave arc-shaped raceway surface on an inner diameter surface, a plurality of rollers arranged on the raceway surface of the raceway, and a cage that holds these rollers in a freely rolling manner. The bearing ring is fixed to the concave arc-shaped portion of the fixed member, and the convex arc-shaped portion of the movable member is swingably supported by the plurality of rollers, and penetrates the raceway surface of the bearing ring. A hole is formed, and a pin protruding from the outer diameter surface on the back surface side is fitted into the through hole, and this pin is engaged with a positioning hole provided in the concave arcuate portion of the fixing member, so that the track ring is In the rocking bearing positioned on the fixed member, the through hole is formed by punching, the clearance between the punching punch and the die is increased, and a shoulder R portion is provided at the periphery of the through hole formed in the raceway surface. The configuration was also adopted.

すなわち、位置決め用の突出部やピンを設けるときに形成される軌道面の陥没穴や貫通孔の周縁に肩Ｒ部を設けることにより、軌道面の陥没穴や貫通孔の周縁で、転動するころとの間にエッジロードが発生しないようにした。なお、陥没穴の周縁の肩Ｒ部は、エンボス加工のダイスに肩Ｒ部を設けることにより形成することができる。また、貫通孔の周縁の肩Ｒ部は、貫通孔を打ち抜き加工で形成する場合は、打ち抜きポンチとダイスのクリアランスを大きくすることにより形成することができる。   That is, by providing a shoulder R portion at the periphery of the recessed hole or through hole of the raceway surface formed when providing the positioning protrusion or pin, the rolling is performed at the recessed hole of the track surface or the peripheral edge of the through hole. Edge load was prevented from occurring between the rollers. The shoulder R portion at the periphery of the depression hole can be formed by providing the shoulder R portion on an embossing die. Further, when the through hole is formed by punching, the shoulder R portion at the periphery of the through hole can be formed by increasing the clearance between the punch and the die.

前記軌道面に形成される陥没穴または貫通孔の周縁の肩Ｒ部の外周に環状のだらし面を設けることにより、より確実にエッジロードの発生を防止することができる。   By providing an annular sloping surface on the outer periphery of the shoulder R portion at the periphery of the recessed hole or the through hole formed in the raceway surface, it is possible to more reliably prevent the occurrence of edge loading.

前記環状のだらし面の外径Ｄ（ｍｍ）を前記凹部の直径の２倍以下とし、だらし面のだらし量Ｈ（ｍｍ）を、（１）式の範囲とすることにより、軌道面ところとの有効接触長さを十分に確保することができる。
Ｈ ≦δ＝０．００００３Ｑmax０．９／（Ｌ−Ｄ）０．８ （１）
ここに、Ｑmax（Ｎ）：軸受の静定格荷重における最大転動体荷重、Ｌ（ｍｍ）：ころの有効長さであり、δ（ｍｍ）はＱmaxが負荷されたときの弾性変位量（Palmgrenの式）である。 By setting the outer diameter D (mm) of the annular flaking surface to not more than twice the diameter of the concave portion and the flaking amount H (mm) of the flaking surface within the range of the formula (1), A sufficient effective contact length can be ensured.
H ≦ δ = 0.00003Qmax 0.9 / (LD) 0.8 (1)
Where Qmax (N) is the maximum rolling element load at the static load rating of the bearing, L (mm) is the effective length of the roller, and δ (mm) is the amount of elastic displacement when Qmax is applied (Palmgren's Formula).

本発明の揺動軸受は、位置決め用の突出部やピンを設けるときに形成される軌道面の陥没穴や貫通孔の周縁に肩Ｒ部を設けたので、軌道面の陥没穴や貫通孔の周縁で、転動するころとの間にエッジロードが発生しないようにすることができる。   In the rocking bearing of the present invention, since the shoulder R portion is provided at the periphery of the recessed hole or the through hole of the raceway surface formed when the protruding portion or pin for positioning is provided, the recessed hole or the through hole of the raceway surface is provided. It is possible to prevent an edge load from occurring between the rolling roller and the roller.

前記軌道面に形成される陥没穴または貫通孔の周縁の肩Ｒ部の外周に環状のだらし面を設けることにより、より確実にエッジロードの発生を防止することができる。   By providing an annular sloping surface on the outer periphery of the shoulder R portion at the periphery of the recessed hole or the through hole formed in the raceway surface, it is possible to more reliably prevent the occurrence of edge loading.

以下、図面に基づき、本発明の実施形態を説明する。図１および図２は、第１の実施形態を示す。この揺動軸受は、図１（ａ）、（ｂ）に示すように、内径面に凹円弧状の軌道面１ａが設けられた軌道輪１と、軌道輪１の軌道面１ａに配列された複数のころ２と、これらのころ２を転動自在に保持する保持器３とからなり、軌道輪１が固定部材１１の凹円弧状部１１ａに固定され、複数のころ２で可動部材１２の凸円弧状部１２ａが揺動自在に支持されるようになっている。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 and 2 show a first embodiment. As shown in FIGS. 1 (a) and 1 (b), the oscillating bearing is arranged on a raceway ring 1 having a concave arc-shaped raceway surface 1a on the inner diameter surface and a raceway surface 1a of the raceway ring 1. It comprises a plurality of rollers 2 and a cage 3 that holds these rollers 2 in a rollable manner. The race 1 is fixed to the concave arcuate portion 11 a of the fixed member 11. The convex arcuate portion 12a is supported in a swingable manner.

前記軌道輪１は鋼板のプレス成形品とされ、軌道面１ａの軸方向両端部に、ころ２の軸方向移動を規制する鍔４がフランジ曲げ加工で形成されるとともに、軌道面１ａの円周方向両端部に、ころ２を保持する保持器３の周方向移動を規制する内向きの爪５が曲げ加工によって形成されている。また、軌道面１ａにはエンボス加工が施されて、その裏面の外径面に突出する突出部６が成形され、この突出部６が固定部材１１の凹円弧状部１１ａに設けられた円形の位置決め穴１３に係合されて、軌道輪１が固定部材１１に位置決めされている。突出部６の根元周りには、位置決め穴１３の周縁との干渉を防止するために、円環状の周溝７が形成されている。   The race 1 is a press-formed product of a steel plate, and flanges 4 for restricting the axial movement of the roller 2 are formed by flange bending at both axial ends of the race 1a, and the circumference of the race 1a. Inwardly directed claws 5 for restricting circumferential movement of the cage 3 holding the rollers 2 are formed at both ends in the direction by bending. Further, the raceway surface 1 a is embossed to form a protruding portion 6 that protrudes to the outer diameter surface of the back surface, and the protruding portion 6 is a circular shape provided on the concave arc-shaped portion 11 a of the fixing member 11. The race 1 is positioned on the fixed member 11 by being engaged with the positioning hole 13. An annular circumferential groove 7 is formed around the base of the protruding portion 6 in order to prevent interference with the peripheral edge of the positioning hole 13.

図２に拡大して示すように、前記軌道面１ａには、エンボス加工で突出部６を成形するときに陥没穴８が形成され、その周縁に肩Ｒ部８ａが形成されるとともに、その外周に円環状のだらし面８ｂが形成されている。この円環状のだらし面８ｂの外径Ｄ（ｍｍ）は陥没穴８の直径ｄの２倍以下とされ、だらし面８ｂのだらし量Ｈ（ｍｍ）は、（１）式の範囲とされている。
Ｈ ≦δ＝０．００００３Ｑmax０．９／（Ｌ−Ｄ）０．８ （１）
ここに、Ｑmax（Ｎ）：軸受の静定格荷重における最大転動体荷重、Ｌ（ｍｍ）：ころの有効長さであり、δはＱmaxが負荷されたときの弾性変位量である。 As shown in FIG. 2 in an enlarged manner, the raceway surface 1a is formed with a depression hole 8 when the projecting portion 6 is formed by embossing, a shoulder R portion 8a is formed at the periphery thereof, and the outer periphery thereof. An annular gentle surface 8b is formed on the upper surface. The outer diameter D (mm) of the circular sloppy surface 8b is set to be equal to or less than twice the diameter d of the recessed hole 8, and the sloppy amount H (mm) of the sloppy surface 8b is in the range of the expression (1). .
H ≦ δ = 0.00003Qmax 0.9 / (LD) 0.8 (1)
Where Qmax (N) is the maximum rolling element load at the static load rating of the bearing, L (mm) is the effective length of the roller, and δ is the amount of elastic displacement when Qmax is applied.

実施例として、外径１０９ｍｍ、内径９０ｍｍ、幅１８ｍｍ（ころの有効長さＬ＝１３ｍｍ）、静定格荷重１３０ｋＮ（最大転動体荷重Ｑmax＝１３ｋＮ）、陥没穴８の直径ｄが３．５ｍｍで、肩Ｒ部８ａのＲ＝０．２ｍｍ、だらし面８ｂの外径Ｄ＝５．８ｍｍ（＝１．６５ｄ）、だらし量Ｈ＝０．０１５ｍｍ（≦δ＝０．０４０ｍｍ）とした揺動軸受を用意した。比較例として、基本寸法が実施例のものと同じで、肩Ｒ部８ａとだらし面８ｂのない揺動軸受も用意した。   As an example, the outer diameter is 109 mm, the inner diameter is 90 mm, the width is 18 mm (the effective length of the roller L = 13 mm), the static load rating is 130 kN (maximum rolling element load Qmax = 13 kN), and the diameter d of the recessed hole 8 is 3.5 mm. A rocking bearing in which the shoulder R portion 8a has R = 0.2 mm, the outer diameter D of the slack surface 8b = 5.8 mm (= 1.65d), and the slack amount H = 0.015 mm (≦ δ = 0.040 mm). Prepared. As a comparative example, a rocking bearing having the same basic dimensions as that of the example and having no shoulder R portion 8a and no sloping surface 8b was also prepared.

これらの実施例と比較例の揺動軸受について、高速揺動試験機を用いた軸受寿命試験を行った。試験条件は以下の通りである。試験サンプル数は、実施例と比較例とも１０個ずつとした。
・荷重 ：１９．６ｋＮ
・揺動速度：６００ｃｐｍ
・揺動角 ：±１５°
・潤滑油 ：出光ダフニー４６（商品名；油浴） A bearing life test using a high-speed rocking tester was performed on the rocking bearings of these examples and comparative examples. The test conditions are as follows. The number of test samples was 10 for each of the examples and comparative examples.
・ Load: 19.6kN
・ Oscillating speed: 600cpm
・ Oscillation angle: ± 15 °
・ Lubricant: Idemitsu Daphne 46 (trade name; oil bath)

上記軸受寿命試験の結果、実施例のものは比較例のものの約２．６倍のＬ１０寿命（サンプルの９０％が破損しないで使える時間）を有し、耐久性が著しく向上することが分かった。なお、比較例のサンプルの破損は、いずれも軌道面の陥没穴の周縁における剥離損傷によるものであった。   As a result of the above bearing life test, it was found that the example has an L10 life of about 2.6 times that of the comparative example (90% of the sample can be used without being damaged), and the durability is remarkably improved. . Note that the breakage of the samples of the comparative examples was due to peeling damage at the periphery of the recessed hole on the raceway surface.

図３および図４は、第２の実施形態を示す。この揺動軸受は基本的な構成は第１の実施形態のものと同じであり、図３（ａ）、（ｂ）に示すように、鋼板のプレス成形品とされた軌道輪１の軌道面１ａに、打ち抜き加工によって貫通孔９が形成され、この貫通孔９に裏面側の外径面に突出するピン１０が嵌め込まれて、このピン１０が固定部材１１の位置決め穴１３に係合され、軌道輪１が位置決めされている点が異なる。   3 and 4 show a second embodiment. The basic structure of this oscillating bearing is the same as that of the first embodiment. As shown in FIGS. 3 (a) and 3 (b), the raceway surface of the race 1 which is a press-formed product of a steel plate. A through hole 9 is formed in 1a by punching, and a pin 10 protruding from the outer diameter surface on the back surface side is fitted into the through hole 9, and this pin 10 is engaged with the positioning hole 13 of the fixing member 11, The difference is that the race 1 is positioned.

図４に拡大して示すように、前記軌道面１ａの貫通孔９の周縁には、第１の実施形態のものと同様に、肩Ｒ部９ａとその外周側のだらし面９ｂが形成されており、だらし面９ｂの外径Ｄは貫通孔９の直径ｄの２倍以下とされ、だらし面９ｂのだらし量Ｈは、（１）式の範囲とされている。   As shown in FIG. 4 in an enlarged manner, a shoulder R portion 9a and an outer peripheral surface 9b are formed on the periphery of the through hole 9 of the raceway surface 1a in the same manner as in the first embodiment. In addition, the outer diameter D of the sloppy surface 9b is not more than twice the diameter d of the through hole 9, and the sloppy amount H of the sloppy surface 9b is in the range of the equation (1).

ａは第１の実施形態の揺動軸受を示す縦断面図、ｂはａのIb−Ib線に沿った横断面図a is a longitudinal sectional view showing the rocking bearing of the first embodiment, and b is a transverse sectional view taken along line Ib-Ib of a. 図１（ｂ）のＡ部を拡大して示す断面図Sectional drawing which expands and shows the A section of FIG.1 (b) ａは第２の実施形態の揺動軸受を示す縦断面図、ｂはａのIIIb−IIIb線に沿った横断面図a is a longitudinal sectional view showing a rocking bearing of the second embodiment, and b is a transverse sectional view taken along line IIIb-IIIb of a. 図３（ｂ）のＢ部を拡大して示す断面図Sectional drawing which expands and shows the B section of FIG.3 (b)

符号の説明Explanation of symbols

１ 軌道輪
１ａ 軌道面
２ ころ
３ 保持器
４ 鍔
５ 爪
６ 突出部
７ 周溝
８ 陥没穴
８ａ 肩Ｒ部
８ｂ だらし面
９ 貫通孔
９ａ 肩Ｒ部
９ｂ だらし面
１０ ピン
１１ 固定部材
１１ａ 凹円弧状部
１２ 可動部材
１２ａ 凸円弧状部
１３ 位置決め穴 DESCRIPTION OF SYMBOLS 1 Raceway 1a Raceway surface 2 Roller 3 Cage 4 Cage 5 Claw 6 Protrusion part 7 Circumferential groove 8 Recessed hole 8a Shoulder R part 8b Slack surface 9 Through-hole 9a Shoulder R part 9b Deflection surface 10 Pin 11 Fixing member 11a Concave arc shape Part 12 Movable member 12a Convex arcuate part 13 Positioning hole

Claims (4)

内径面に凹円弧状の軌道面が設けられた軌道輪と、この軌道輪の軌道面に配列された複数のころと、これらのころを転動自在に保持する保持器とからなり、前記軌道輪を固定部材の凹円弧状部に固定して、前記複数のころで可動部材の凸円弧状部を揺動自在に支持するようにし、前記軌道輪を金属板のプレス成形品として、前記軌道面にエンボス加工を施して、その裏面側の外径面に突出する突出部を成形し、この突出部を前記固定部材の凹円弧状部に設けた位置決め穴に係合させて、前記軌道輪を前記固定部材に位置決めした揺動軸受において、前記エンボス加工で突出部を成形するときに、エンボス加工のダイスに肩Ｒ部を設けて、前記軌道面に形成される陥没穴の周縁に肩Ｒ部を設けたことを特徴とする揺動軸受。 The raceway is provided with a raceway having a concave arc-shaped raceway surface on its inner surface, a plurality of rollers arranged on the raceway surface of the raceway, and a cage that holds these rollers in a rollable manner. A ring is fixed to the concave arc-shaped portion of the fixed member, and the convex arc-shaped portion of the movable member is supported by the plurality of rollers so as to be swingable. The surface is embossed to form a protruding portion that protrudes to the outer diameter surface on the back surface side, and the protruding portion is engaged with a positioning hole provided in the concave arc-shaped portion of the fixing member, thereby In the rocking bearing in which the fixed member is positioned, when the protruding portion is formed by the embossing, a shoulder R portion is provided on the embossing die, and the shoulder R is formed on the periphery of the recessed hole formed in the raceway surface. A rocking bearing characterized in that a portion is provided. 内径面に凹円弧状の軌道面が設けられた軌道輪と、この軌道輪の軌道面に配列された複数のころと、これらのころを転動自在に保持する保持器とからなり、前記軌道輪を固定部材の凹円弧状部に固定して、前記複数のころで可動部材の凸円弧状部を揺動自在に支持するようにし、前記軌道輪の軌道面に貫通孔を形成して、この貫通孔に裏面側の外径面に突出するピンを嵌め込み、このピンを前記固定部材の凹円弧状部に設けた位置決め穴に係合させて、前記軌道輪を前記固定部材に位置決めした揺動軸受において、前記貫通孔を打ち抜き加工で形成し、打ち抜き加工のポンチとダイスのクリアランスを大きくして、前記軌道面に形成される貫通孔の周縁に肩Ｒ部を設けたことを特徴とする揺動軸受。 The raceway is provided with a raceway having a concave arc-shaped raceway surface on its inner surface, a plurality of rollers arranged on the raceway surface of the raceway, and a cage that holds these rollers in a rollable manner. The ring is fixed to the concave arcuate portion of the fixed member, the convex arcuate portion of the movable member is supported by the plurality of rollers so as to be swingable, and a through hole is formed in the raceway surface of the raceway ring, A pin projecting to the outer diameter surface on the back surface side is fitted into the through hole, and this pin is engaged with a positioning hole provided in the concave arcuate portion of the fixing member to position the track ring on the fixing member. In the dynamic bearing, the through hole is formed by punching, the clearance between the punching punch and the die is increased, and a shoulder R portion is provided on the periphery of the through hole formed in the raceway surface. Swing bearing. 前記軌道面に形成される陥没穴または貫通孔の周縁の肩Ｒ部の外周に、環状のだらし面を設けた請求項１または２に記載の揺動軸受。   3. The rocking bearing according to claim 1, wherein an annular sloping surface is provided on an outer periphery of a shoulder R portion at a peripheral edge of a recessed hole or a through-hole formed in the raceway surface. 前記環状のだらし面の外径Ｄ（ｍｍ）を前記凹部の直径の２倍以下とし、だらし面のだらし量Ｈ（ｍｍ）を、（１）式の範囲とした請求項３に記載の揺動軸受。
Ｈ ≦δ＝０．００００３Ｑmax０．９／（Ｌ−Ｄ）０．８ （１）
ここに、Ｑmax（Ｎ）：軸受の静定格荷重における最大転動体荷重、Ｌ（ｍｍ）：ころの有効長さであり、δ（ｍｍ）はＱmaxが負荷されたときの弾性変位量である。 The rocking | fluctuation of Claim 3 which made the outer diameter D (mm) of the said annular | circular gentle surface into 2 times or less of the diameter of the said recessed part, and made the gentle amount H (mm) of the gentle surface into the range of (1) Formula. bearing.
H ≦ δ = 0.00003Qmax 0.9 / (LD) 0.8 (1)
Here, Qmax (N) is the maximum rolling element load at the static load rating of the bearing, L (mm) is the effective length of the roller, and δ (mm) is the elastic displacement when Qmax is loaded.
JP2006087157A 2006-03-28 2006-03-28 Swing bearing Expired - Fee Related JP4536675B2 (en)

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Publication number Priority date Publication date Assignee Title
JP5010538B2 (en) * 2008-06-05 2012-08-29 Ｎｔｎ株式会社 Swing bearing
JP2010127450A (en) * 2008-12-01 2010-06-10 Ntn Corp Swinging bearing device
JP2018087604A (en) * 2016-11-29 2018-06-07 Ntn株式会社 Rolling bearing

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JPS62166962A (en) * 1986-01-17 1987-07-23 Ntn Toyo Bearing Co Ltd Machining method of shell type needle-shaped roller bearing for lever shaft
JPH0586034U (en) * 1992-04-23 1993-11-19 エヌティエヌ株式会社 Shell type bearing with flange
JPH071067A (en) * 1993-01-28 1995-01-06 Toyota Auto Body Co Ltd Forming of embossment
JP2002286041A (en) * 2001-03-26 2002-10-03 Ntn Corp Oscillating bearing
JP2003049848A (en) * 2001-08-06 2003-02-21 Nsk Ltd Ball bearing for supporting pulley
JP2004100805A (en) * 2002-09-09 2004-04-02 Ntn Corp Swinging bearing
JP2005147185A (en) * 2003-11-12 2005-06-09 Nachi Fujikoshi Corp Double row rolling bearing
JP2005299702A (en) * 2004-04-06 2005-10-27 Nsk Ltd Automatic aligning roller bearing

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62166962A (en) * 1986-01-17 1987-07-23 Ntn Toyo Bearing Co Ltd Machining method of shell type needle-shaped roller bearing for lever shaft
JPH0586034U (en) * 1992-04-23 1993-11-19 エヌティエヌ株式会社 Shell type bearing with flange
JPH071067A (en) * 1993-01-28 1995-01-06 Toyota Auto Body Co Ltd Forming of embossment
JP2002286041A (en) * 2001-03-26 2002-10-03 Ntn Corp Oscillating bearing
JP2003049848A (en) * 2001-08-06 2003-02-21 Nsk Ltd Ball bearing for supporting pulley
JP2004100805A (en) * 2002-09-09 2004-04-02 Ntn Corp Swinging bearing
JP2005147185A (en) * 2003-11-12 2005-06-09 Nachi Fujikoshi Corp Double row rolling bearing
JP2005299702A (en) * 2004-04-06 2005-10-27 Nsk Ltd Automatic aligning roller bearing

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