JP2024045260A - Needle roller bearing cages and needle roller bearings - Google Patents
Needle roller bearing cages and needle roller bearings Download PDFInfo
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- JP2024045260A JP2024045260A JP2024006110A JP2024006110A JP2024045260A JP 2024045260 A JP2024045260 A JP 2024045260A JP 2024006110 A JP2024006110 A JP 2024006110A JP 2024006110 A JP2024006110 A JP 2024006110A JP 2024045260 A JP2024045260 A JP 2024045260A
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- 238000005452 bending Methods 0.000 claims description 11
- 239000002184 metal Substances 0.000 abstract description 5
- 238000010586 diagram Methods 0.000 abstract 1
- 239000003638 chemical reducing agent Substances 0.000 description 9
- 230000002093 peripheral effect Effects 0.000 description 9
- 238000000034 method Methods 0.000 description 7
- 238000004519 manufacturing process Methods 0.000 description 6
- 238000012360 testing method Methods 0.000 description 4
- 238000012856 packing Methods 0.000 description 3
- 238000004080 punching Methods 0.000 description 3
- 238000005520 cutting process Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000008719 thickening Effects 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D28/00—Shaping by press-cutting; Perforating
- B21D28/02—Punching blanks or articles with or without obtaining scrap; Notching
- B21D28/14—Dies
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D53/00—Making other particular articles
- B21D53/10—Making other particular articles parts of bearings; sleeves; valve seats or the like
- B21D53/12—Making other particular articles parts of bearings; sleeves; valve seats or the like cages for bearings
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
- B21D22/20—Deep-drawing
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D37/00—Tools as parts of machines covered by this subclass
- B21D37/10—Die sets; Pillar guides
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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
- F16C19/24—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
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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
- F16C19/44—Needle bearings
- F16C19/46—Needle bearings with one row or needles
- F16C19/463—Needle bearings with one row or needles consisting of needle rollers held in a cage, i.e. subunit without race rings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
- F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
- F16C33/4629—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from metal, e.g. cast or machined window cages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
- F16C33/4676—Details of individual pockets, e.g. shape or roller retaining means of the stays separating adjacent cage pockets, e.g. guide means for the bearing-surface of the rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
- F16C33/541—Details of individual pockets, e.g. shape or roller retaining means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
- F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
- F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
- F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D28/00—Shaping by press-cutting; Perforating
- B21D28/02—Punching blanks or articles with or without obtaining scrap; Notching
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D28/00—Shaping by press-cutting; Perforating
- B21D28/24—Perforating, i.e. punching holes
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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
- F16C2220/00—Shaping
- F16C2220/40—Shaping by deformation without removing material
- F16C2220/42—Shaping by deformation without removing material by working of thin walled material such as sheet or tube
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/60—Thickness, e.g. thickness of coatings
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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
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators
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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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
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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
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/06—Crankshafts
- F16C3/08—Crankshafts made in one piece
Abstract
【課題】プレス成形品からなる針状ころ軸受用保持器のスラスト荷重に対する耐久性を高める。
【解決手段】針状ころ軸受用保持器２０は、複数の柱部２１ａおよび複数のポケット２１ｂを有する円筒部２１と、円筒部２１の軸方向一方の端部から屈曲部２２を介して内径側に延びる一方のフランジ部２３と、円筒部２１の軸方向他方の端部から屈曲部２４を介して内径側に延びる他方のフランジ部２５とを一体に有する金属板のプレス成形品からなる。円筒部２１と一方のフランジ部２３との間に設けられた屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１と、円筒部２１の軸方向一方の端部の肉厚Ｔ１とが、Ｌ１／Ｔ１≦１．４を満たす。
【選択図】図３
[Problem] To improve the durability against thrust loads of a needle roller bearing cage made of a press-formed product.
A cage 20 for a needle roller bearing includes a cylindrical part 21 having a plurality of column parts 21a and a plurality of pockets 21b, and an inner diameter side from one axial end of the cylindrical part 21 via a bent part 22. It is a press-formed metal plate integrally having one flange portion 23 extending from the cylindrical portion 21 and the other flange portion 25 extending radially inward from the other axial end of the cylindrical portion 21 via the bent portion 24. The radial dimension L1 of the outer curved surface 22a of the bent portion 22 provided between the cylindrical portion 21 and one flange portion 23 and the wall thickness T1 of one axial end of the cylindrical portion 21 are L1/T1. ≦1.4 is satisfied.
[Selection diagram] Figure 3
Description
本発明は、針状ころ軸受用保持器に関し、特に、プレス加工で形成された針状ころ軸受用保持器に関する。 The present invention relates to a retainer for a needle roller bearing, and in particular to a retainer for a needle roller bearing formed by press working.
例えば特許文献１には、産業用ロボットや工作機械等に組み込まれる偏心揺動型歯車減速機が示されている。この減速機は、筒状のケーシングと、ケーシングに設けられた内歯車と、内歯車と噛み合う遊星ギアと、遊星ギアを遊星運動させるクランク軸とを備え、入力軸の回転が入力されてクランク軸が回転すると、クランク軸の偏心部に取り付けられた遊星ギアが内歯車と噛み合いながら遊星運動し、この遊星運動の公転成分が出力軸の回転として出力される。この減速機では、クランク軸のジャーナル部と出力軸との間、および、クランク軸の偏心部と遊星ギアとの間に、それぞれ針状ころ軸受が組み込まれている。 For example, Patent Document 1 shows an eccentric oscillating gear reducer that is incorporated into industrial robots, machine tools, and the like. This reducer has a cylindrical casing, an internal gear provided in the casing, a planetary gear that meshes with the internal gear, and a crankshaft that causes the planetary gear to perform planetary motion; when rotation of the input shaft is input and the crankshaft rotates, the planetary gear attached to the eccentric portion of the crankshaft performs planetary motion while meshing with the internal gear, and the orbital component of this planetary motion is output as rotation of the output shaft. In this reducer, needle roller bearings are incorporated between the journal portion of the crankshaft and the output shaft, and between the eccentric portion of the crankshaft and the planetary gear.
針状ころ軸受の保持器は、切削加工で形成されることが多いが、製造コストを低減するために、プレス加工で形成されることもある（例えば、下記の特許文献２参照）。 The cages of needle roller bearings are often formed by cutting, but may also be formed by pressing to reduce manufacturing costs (see, for example, Patent Document 2 below).
ところで、産業用ロボットでは、ロボット自体の大型化や可搬重量の増大に伴い、ロボットに組み込まれる減速機の軸受に加わるラジアル荷重が増大し、ラジアル荷重の増大に伴ってスラスト荷重（誘起スラスト荷重）も増大している。特に、上記特許文献１のように、減速機のクランク軸を針状ころ軸受のみで支持する場合は、これらの針状ころ軸受にスラスト荷重が加わりやすい。針状ころ軸受が軸方向に移動して保持器が他部材（他の針状ころ軸受の保持器や、針状ころ軸受の軸方向移動を規制する止め輪等）に当接すると、保持器に応力が加わるため、保持器に強度対策を行うことで信頼性を高めることができる。 By the way, in industrial robots, as the robot itself becomes larger and its payload increases, the radial load applied to the bearings of the reducer built into the robot increases, and as the radial load increases, thrust load (induced thrust load) increases. ) is also increasing. In particular, when the crankshaft of the speed reducer is supported only by needle roller bearings as in Patent Document 1, thrust loads are likely to be applied to these needle roller bearings. When the needle roller bearing moves in the axial direction and the cage comes into contact with another member (such as the cage of another needle roller bearing or a retaining ring that restricts the axial movement of the needle roller bearing), the cage Since stress is applied to the cage, reliability can be increased by taking measures to strengthen the cage.
例えば、保持器を切削加工で形成する場合は、形状の変更が比較的容易であるため、強度を必要とする部位を局部的に厚肉化する等の対策が可能である。しかし、保持器をプレス加工で形成する場合は、部分的に厚肉化することは容易ではないため、他の対策が必要となる。 For example, when the cage is formed by cutting, it is relatively easy to change the shape, so measures such as locally thickening the areas that require strength can be taken. However, when the cage is formed by pressing, it is not easy to locally thicken the areas, so other measures are required.
例えば、上記の特許文献３には、保持器とこれに軸方向で当接する座金との接触面積を増大させることで、保持器の変形や破損を防止している。しかし、このような対策は、座金を設けない場合や、座金の形状を変更することができない場合には適用することができない。 For example, in the above-mentioned Patent Document 3, deformation and damage to the cage are prevented by increasing the contact area between the cage and the washer that abuts against it in the axial direction. However, such measures cannot be applied when a washer is not provided or when the shape of the washer cannot be changed.
そこで、本発明は、プレス成形品からなる針状ころ軸受用保持器のスラスト荷重に対する耐久性を高めることを目的とする。 Therefore, an object of the present invention is to improve the durability against thrust loads of a needle roller bearing retainer made of a press-formed product.
例えば、図８に示す針状ころ軸受用保持器１２０は、針状ころ１１０を保持するポケット１２１ｂが形成された円筒部１２１と、円筒部１２１の軸方向両端から屈曲部１２２、１２４を介して内径側に延びる一対のフランジ部１２３、１２５とを一体に有するプレス成形品からなる。図９に拡大して示すように、保持器１２０に軸方向一方側（図中右側）から他部材Ｍが当接すると、一方のフランジ部１２３の内径端は軸方向内側に変位するが、外径端は円筒部１２１で支持されているためほとんど変位しない。その結果、フランジ部１２３の外側端面１２３ａの外径端Ｐ（すなわち、屈曲部１２２の外側曲面１２２ａの内径端）が、スラスト荷重Ｆを支持する点となる。 For example, the needle roller bearing retainer 120 shown in FIG. 8 is a press-molded product having a cylindrical portion 121 in which a pocket 121b for retaining the needle rollers 110 is formed, and a pair of flange portions 123, 125 extending from both axial ends of the cylindrical portion 121 to the inner diameter side via bent portions 122, 124. As shown in an enlarged view in FIG. 9, when another member M abuts against the retainer 120 from one axial side (the right side in the figure), the inner diameter end of one flange portion 123 is displaced axially inward, but the outer diameter end is hardly displaced because it is supported by the cylindrical portion 121. As a result, the outer diameter end P of the outer end surface 123a of the flange portion 123 (i.e., the inner diameter end of the outer curved surface 122a of the bent portion 122) becomes the point that supports the thrust load F.
ところで、フランジ部１２３と円筒部１２１との間の屈曲部１２２を曲げ加工により形成する場合、屈曲部１２２が略均一な肉厚で曲げられる。このため、屈曲部１２２の外側曲面１２２ａの半径方向寸法Ｌ１が、円筒部１２１の肉厚Ｔ１と屈曲部１２２の内側曲面１２２ｂの半径方向寸法Ｌ２との合計と略等しくなる（Ｌ１≒Ｔ１＋Ｌ２）。この場合、屈曲部１２２の内側曲面１２２ｂの半径方向寸法Ｌ２を小さくすれば、屈曲部１２２の外側曲面１２２ａの半径方向寸法Ｌ１を小さくすることができるが、屈曲部１２２の内側曲面１２２ｂの半径方向寸法Ｌ２は、製造上の都合からむやみに小さくすることはできない。このため、従来のプレス成形品からなる保持器では、屈曲部１２２の外側曲面１２２ａの半径方向寸法Ｌ１は、円筒部１２１の肉厚Ｔ１の１．５倍程度とされていた。 When the bent portion 122 between the flange portion 123 and the cylindrical portion 121 is formed by bending, the bent portion 122 is bent with a substantially uniform thickness. Therefore, the radial dimension L1 of the outer curved surface 122a of the bent portion 122 is substantially equal to the sum of the thickness T1 of the cylindrical portion 121 and the radial dimension L2 of the inner curved surface 122b of the bent portion 122 (L1 ≒ T1 + L2). In this case, if the radial dimension L2 of the inner curved surface 122b of the bent portion 122 is reduced, the radial dimension L1 of the outer curved surface 122a of the bent portion 122 can be reduced, but the radial dimension L2 of the inner curved surface 122b of the bent portion 122 cannot be reduced unnecessarily for manufacturing reasons. For this reason, in a conventional retainer made of a press-molded product, the radial dimension L1 of the outer curved surface 122a of the bent portion 122 was set to about 1.5 times the thickness T1 of the cylindrical portion 121.
本発明は、上記のように屈曲部の外側曲面の内径端がスラスト荷重Ｆを支持する点となる点に着目してなされたものであり、屈曲部の外側曲面の半径方向寸法を従来よりも小さくすることにより、スラスト荷重を支持する点を従来よりも外径側に配したことを特徴とするものである。具体的には、屈曲部の外側曲面の半径方向寸法Ｌ１を、円筒部の端部の肉厚Ｔ１の１．４倍以下とした。これにより、フランジ部に加わるモーメント荷重が小さくなり、屈曲部に加わる応力が軽減されるため、保持器の耐久性を向上させることができる。 The present invention has been made by focusing on the fact that the inner diameter end of the outer curved surface of the bent portion is the point that supports the thrust load F, as described above, and the radial dimension of the outer curved surface of the bent portion is made larger than before. By making it smaller, the point that supports the thrust load is placed closer to the outer diameter than in the past. Specifically, the radial dimension L1 of the outer curved surface of the bent portion was set to be 1.4 times or less the wall thickness T1 of the end portion of the cylindrical portion. As a result, the moment load applied to the flange portion is reduced, and the stress applied to the bent portion is reduced, so that the durability of the cage can be improved.
以上より、本発明は、複数の柱部および隣接する柱部の周方向間に設けられた複数のポケットを有する円筒部と、前記円筒部の軸方向一方の端部から屈曲部を介して内径側に延びる一方のフランジ部と、前記円筒部の軸方向他方の端部から屈曲部を介して内径側に延びる他方のフランジ部とを一体に有する金属板のプレス成形品からなる針状ころ軸受用保持器であって、前記円筒部と前記一方のフランジ部との間に設けられた屈曲部の外側曲面の半径方向寸法Ｌ１と、前記円筒部の軸方向一方の端部の肉厚Ｔ１とが、Ｌ１／Ｔ１≦１．４を満たす針状ころ軸受用保持器を提供する。 As described above, the present invention provides a cylindrical portion having a plurality of columnar portions and a plurality of pockets provided between adjacent columnar portions in the circumferential direction; A needle roller bearing made of a press-molded metal plate integrally having one flange portion extending in the axial direction and the other flange portion extending radially inward from the other axial end of the cylindrical portion via a bent portion. A radial dimension L1 of an outer curved surface of a bent part provided between the cylindrical part and the one flange part, and a wall thickness T1 of one axial end of the cylindrical part. provides a cage for a needle roller bearing that satisfies L1/T1≦1.4.
上記の発明は、ころ充填率が７０％以上の針状ころ軸受の保持器、具体的には、円筒部における前記ポケットの周方向の割合が７０％以上である保持器に主に適用できる。 The above invention is primarily applicable to needle roller bearing retainers with a roller filling rate of 70% or more, specifically, retainers in which the circumferential proportion of the pockets in the cylindrical portion is 70% or more.
上記の保持器は、例えば、屈曲部の外側曲面の半径方向寸法Ｌ１と、屈曲部の内側曲面の半径方向寸法Ｌ２と、円筒部の軸方向一方の端部の肉厚Ｔ１とが、Ｌ１＜Ｔ１＋Ｌ２を満たすように設計される。 In the cage described above, for example, the radial dimension L1 of the outer curved surface of the bent portion, the radial dimension L2 of the inner curved surface of the bent portion, and the wall thickness T1 of one end in the axial direction of the cylindrical portion are L1< It is designed to satisfy T1+L2.
上記の保持器では、例えば、一方のフランジ部の軸方向外側の端面のうち、少なくとも外径端（屈曲部の外側曲面との境界）を含む領域に研削加工を施すことにより、Ｌ１／Ｔ１≦１．４を満たすことができる。あるいは、円筒部と一方のフランジ部との間の角度が８９．９°以下となるように屈曲させることにより、Ｌ１／Ｔ１≦１．４を満たすことができる。 In the above cage, for example, by performing a grinding process on the region of the axially outer end face of one of the flange portions, including at least the outer diameter end (the boundary with the outer curved surface of the bent portion), it is possible to satisfy L1/T1≦1.4. Alternatively, it is possible to satisfy L1/T1≦1.4 by bending the flange portion so that the angle between the cylindrical portion and one of the flange portions is 89.9° or less.
上記の保持器では、屈曲部の外側曲面の半径方向寸法Ｌ１と、円筒部の軸方向一方の端部の肉厚Ｔ１とが、０．５≦Ｌ１／Ｔ１≦１．３を満たすことがより好ましい。 In the above retainer, it is more preferable that the radial dimension L1 of the outer curved surface of the bent portion and the wall thickness T1 of one axial end of the cylindrical portion satisfy 0.5≦L1/T1≦1.3.
上記の保持器は、金属板に絞り加工を施して円筒成形部およびその軸方向他方の端部を閉塞する底部を一体に有する成形品を形成する工程と、前記底部の軸心を打ち抜いて前記他方のフランジ部を形成する工程と、前記円筒成形部に曲げ加工を施して前記一方のフランジ部を形成する工程と、前記円筒成形部の周方向複数箇所を打ち抜いて前記複数のポケットを形成する工程とを経て製造することができる。 The above-mentioned retainer includes a process of drawing a metal plate to form a molded product that integrally has a cylindrical molded part and a bottom part that closes the other axial end of the cylindrical molded part, and punching out the axis of the bottom part to form a molded product. a step of forming the other flange portion, a step of bending the cylindrical molded portion to form the one flange portion, and punching out multiple locations in the circumferential direction of the cylindrical molded portion to form the plurality of pockets. It can be manufactured through the following steps.
上記の製造方法において、円筒成形部の軸方向一方の端部を含む領域に、他の領域よりも肉厚が薄い薄肉領域を設け、この薄肉領域に曲げ加工を施せば、曲げ加工が容易になる。こうして形成された保持器は、円筒部の軸方向一方の端部の肉厚が、円筒部の軸方向中央部の肉厚よりも薄くなっているため、本発明を適用して耐久性を高めることが特に好ましい。 In the above manufacturing method, if a thin region that is thinner than other regions is provided in the region including one end in the axial direction of the cylindrical molded part, and bending is performed on this thin region, the bending process can be easily performed. Become. Since the cage thus formed has a wall thickness at one axial end of the cylindrical portion that is thinner than a wall thickness at the axial center of the cylindrical portion, durability can be increased by applying the present invention. This is particularly preferred.
以上のように、本発明によれば、プレス成形品からなる針状ころ軸受用保持器のスラスト荷重に対する耐久性を高めることができる。 As described above, according to the present invention, the durability against thrust loads of a needle roller bearing retainer made of a press-formed product can be improved.
以下、本発明の実施の形態を図面に基づいて説明する。 The following describes an embodiment of the present invention with reference to the drawings.
図１は、産業用ロボットの関節部に設けられた偏心揺動型歯車減速機のクランク軸１を示す。クランク軸１は、軸方向に離間した２箇所に設けられた一対のジャーナル部１ａと、一対のジャーナル部１ａの間に設けられた一対の偏心部１ｂと、軸方向一端に設けられたスパーギア取付部１ｃとを有する。一対のジャーナル部１ａの外周面は、回転中心Ｏを中心とした円筒面状に形成される。一対の偏心部１ｂの外周面は、回転中心Ｏからオフセットした軸心を中心とした円筒面状に形成される。各偏心部１ｂの外周面の軸心は、回転中心Ｏに対して異なる位相に配され、例えば１８０°異なる位相に配される。 FIG. 1 shows a crankshaft 1 of an eccentric rocking type gear reducer provided at a joint of an industrial robot. The crankshaft 1 includes a pair of journal parts 1a provided at two locations spaced apart in the axial direction, a pair of eccentric parts 1b provided between the pair of journal parts 1a, and a spur gear attachment provided at one end in the axial direction. It has a part 1c. The outer peripheral surfaces of the pair of journal parts 1a are formed into a cylindrical shape centered on the rotation center O. The outer circumferential surfaces of the pair of eccentric parts 1b are formed into a cylindrical shape centered on an axis offset from the rotation center O. The axes of the outer circumferential surfaces of the respective eccentric portions 1b are arranged at different phases with respect to the rotation center O, for example, 180° different from each other.
クランク軸１の各ジャーナル部１ａの外周面は、針状ころ軸受２を介して、キャリア３に取り付けられる。また、クランク軸１の各偏心部１ｂの外周面は、針状ころ軸受２を介して、遊星ギア４の内周面に取り付けられる。クランク軸１は、これらの４つの針状ころ軸受２のみで回転自在に支持されている。クランク軸１のスパーギア取付部１ｃの外周面には、スパーギア５が固定される。尚、偏心揺動型歯車減速機の全体構成は、公知のもの（例えば特許文献１に示されたもの）と同様であるため、詳細な説明は省略する。 The outer peripheral surface of each journal portion 1a of the crankshaft 1 is attached to a carrier 3 via a needle roller bearing 2. The outer peripheral surface of each eccentric portion 1b of the crankshaft 1 is attached to the inner peripheral surface of a planetary gear 4 via a needle roller bearing 2. The crankshaft 1 is rotatably supported only by these four needle roller bearings 2. A spur gear 5 is fixed to the outer peripheral surface of the spur gear mounting portion 1c of the crankshaft 1. The overall configuration of the eccentric oscillating gear reducer is similar to that of a known device (for example, that shown in Patent Document 1), so a detailed description will be omitted.
針状ころ軸受２は、複数の針状ころ１０と、これらを保持する保持器２０とを有する。本実施形態では、針状ころ軸受２の内側軌道面がクランク軸１の外周面に直接形成され、針状ころ軸受２の外側軌道面がキャリア３および遊星ギア４の内周面に直接形成されている。針状ころ軸受２のころ充填率は、例えば７０％以上、好ましくは８０％以上とされる。また、針状ころ軸受２のころ充填率は、保持器２０の強度等に応じて上限が設定され、例えば９０％以下とされる。尚、ころ充填率γは次式で表される。
ころ充填率γ＝（Ｚ・ＤＡ）／（π・ＰＣＤ）
ただし、Ｚ：ころ本数、ＤＡ：ころ直径、ＰＣＤ：ころピッチ円直径
Needle roller bearing 2 has a plurality of needle rollers 10 and a cage 20 that holds them. In this embodiment, the inner raceway surface of needle roller bearing 2 is formed directly on the outer peripheral surface of crankshaft 1, and the outer raceway surface of needle roller bearing 2 is formed directly on the inner peripheral surfaces of carrier 3 and planetary gear 4. The roller packing rate of needle roller bearing 2 is, for example, 70% or more, and preferably 80% or more. The upper limit of the roller packing rate of needle roller bearing 2 is set depending on the strength of cage 20, etc., and is, for example, 90% or less. The roller packing rate γ is expressed by the following equation:
Roller filling rate γ = (Z DA) / (π PCD)
Where Z is the number of rollers, DA is the roller diameter, PCD is the roller pitch circle diameter
保持器２０は、金属板のプレス成形品からなり、図２に示すように、円筒部２１と、円筒部２１の軸方向一方の端部（図中右端）から屈曲部２２を介して内径側に延びる一方のフランジ部２３と、円筒部２１の軸方向他方の端部（図中左端）から屈曲部２４を介して内径側に延びる他方のフランジ部２５とを一体に有する。保持器２０は、円筒部２１の外周面が軌道面（キャリア３の内周面又は遊星ギア４の内周面）と接触することで案内される、いわゆる外輪案内タイプである。 The cage 20 is made of a press-molded metal plate, and as shown in FIG. It integrally includes one flange portion 23 extending in the cylindrical portion 21 and the other flange portion 25 extending radially inward from the other axial end (left end in the figure) of the cylindrical portion 21 via the bent portion 24 . The cage 20 is a so-called outer ring guide type in which the cage 20 is guided by the outer circumferential surface of the cylindrical portion 21 coming into contact with a raceway surface (the inner circumferential surface of the carrier 3 or the inner circumferential surface of the planetary gear 4).
円筒部２１は、周方向等間隔に配された多数の柱部２１ａと、隣接する柱部２１ａの間に設けられた多数のポケット２１ｂとを有する。本実施形態では、円筒部２１におけるポケット２１ｂの周方向の割合が７０％以上とされる。円筒部２１の軸方向一方の端部の肉厚Ｔ１は、円筒部２１の軸方向中央部の肉厚Ｔ２よりも薄い。図示例では、図３に拡大して示すように、柱部２１ａが、肉厚Ｔ２で形成された本体部２１ａ１と、本体部２１ａ１の軸方向一方側に隣接して設けられ、肉厚がＴ２からＴ１まで徐々に小さくなる徐変部２１ａ２とを有する。徐変部２１ａ２の外周面は、本体部２１ａ１の外周面と同一円筒面上に設けられ、徐変部２１ａ２の内周面は、軸方向一方側へ向けて徐々に拡径したテーパ状を成している。円筒部２１の軸方向他方の端部は、軸方向中央部と同じ肉厚Ｔ２を有する。尚、図示例では、柱部２１ａが軸方向に沿った直線状を成しているが、これに限らず、例えば柱部２１ａの軸方向中央部を内径側に配した断面略Ｍ字形状としてもよい。 The cylindrical portion 21 has a large number of columnar portions 21a arranged at equal intervals in the circumferential direction, and a large number of pockets 21b provided between adjacent columnar portions 21a. In this embodiment, the ratio of pockets 21b in the cylindrical portion 21 in the circumferential direction is 70% or more. The wall thickness T1 at one axial end of the cylindrical portion 21 is thinner than the wall thickness T2 at the axial center of the cylindrical portion 21. In the illustrated example, as shown in an enlarged view in FIG. 3, the column portion 21a is provided adjacent to a main body portion 21a1 having a wall thickness of T2, and on one side in the axial direction of the main body portion 21a1, and has a wall thickness of T2. It has a gradually changing portion 21a2 that gradually decreases in size from T1 to T1. The outer circumferential surface of the gradually variable portion 21a2 is provided on the same cylindrical surface as the outer circumferential surface of the main body portion 21a1, and the inner circumferential surface of the gradually variable portion 21a2 has a tapered shape whose diameter gradually increases toward one side in the axial direction. are doing. The other axial end of the cylindrical portion 21 has the same wall thickness T2 as the axial center. In the illustrated example, the columnar portion 21a has a linear shape along the axial direction, but the present invention is not limited to this. For example, the columnar portion 21a may have a substantially M-shaped cross section with the axial center portion on the inner diameter side. Good too.
円筒部２１と一方のフランジ部２３との間に設けられた屈曲部２２は、円筒部２１の軸方向一方の端部の外周面と一方のフランジ部２３の外側端面２３ａとを連続する外側曲面２２ａと、円筒部２１の軸方向一方の端部の内周面と一方のフランジ部２３の内側端面２３ｂとを連続する内側曲面２２ｂとを有する。屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１は、円筒部２１の軸方向一方の端部の肉厚Ｔ１の１．４倍以下（Ｌ１／Ｔ１≦１．４）、好ましくは１．３倍以下（Ｌ１／Ｔ１≦１．３）、より好ましくは１．２倍以下（Ｌ１／Ｔ１≦１．２）、さらに好ましくは１倍以下（Ｌ１／Ｔ１≦１）とされる。図示例では、屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１が、円筒部２１の軸方向一方の端部の肉厚Ｔ１と内側曲面２４ｂの半径方向寸法Ｌ２との和よりも小さい（Ｌ１＜Ｔ１＋Ｌ２）。また、図示例では、屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１が、柱部２１ａの本体部２１ａ１の肉厚Ｔ２よりも小さい（Ｌ１＜Ｔ２）。屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１の下限値は、強度や製造上の都合の観点から設定され、例えば上記肉厚Ｔ１の０．５倍以上（Ｌ１／Ｔ１≧０．５）とされる。 The bent portion 22 provided between the cylindrical portion 21 and one of the flange portions 23 has an outer curved surface 22a that connects the outer peripheral surface of one axial end of the cylindrical portion 21 and the outer end surface 23a of one of the flange portions 23, and an inner curved surface 22b that connects the inner peripheral surface of one axial end of the cylindrical portion 21 and the inner end surface 23b of one of the flange portions 23. The radial dimension L1 of the outer curved surface 22a of the bent portion 22 is 1.4 times or less (L1/T1≦1.4), preferably 1.3 times or less (L1/T1≦1.3), more preferably 1.2 times or less (L1/T1≦1.2), and even more preferably 1 time or less (L1/T1≦1). In the illustrated example, the radial dimension L1 of the outer curved surface 22a of the bent portion 22 is smaller than the sum of the thickness T1 of one axial end of the cylindrical portion 21 and the radial dimension L2 of the inner curved surface 24b (L1<T1+L2). Also, in the illustrated example, the radial dimension L1 of the outer curved surface 22a of the bent portion 22 is smaller than the thickness T2 of the main body 21a1 of the column portion 21a (L1<T2). The lower limit of the radial dimension L1 of the outer curved surface 22a of the bent portion 22 is set from the viewpoint of strength and manufacturing convenience, and is, for example, 0.5 times or more the thickness T1 (L1/T1≧0.5).
一方のフランジ部２３の外側端面２３ａのうち、少なくとも外径端を含む領域には研削面が設けられ、本実施形態では、一方のフランジ部２３の外側端面２３ａの全域に研削面が設けられる。こうして研削を施した分だけ、一方のフランジ部２３の肉厚Ｔ３は、円筒部２１の軸方向一方の端部の肉厚Ｔ１よりも小さくなっている。 A grinding surface is provided on at least the area of the outer end surface 23a of one flange portion 23, including the outer diameter end, and in this embodiment, a grinding surface is provided on the entire outer end surface 23a of one flange portion 23. By the amount of grinding, the thickness T3 of one flange portion 23 is smaller than the thickness T1 of one axial end of the cylindrical portion 21.
円筒部２１と他方のフランジ部２５との間に設けられた屈曲部２４は、図４に拡大して示すように、円筒部２１の外周面と他方のフランジ部２５の外側端面２５ａとを連続する外側曲面２４ａと、円筒部２１の内周面と他方のフランジ部２５の内側端面２５ｂとを連続する内側曲面２４ｂとを有する。屈曲部２４の外側曲面２４ａの半径方向寸法Ｌ３は、円筒部２１の軸方向他方の端部の肉厚Ｔ２と内側曲面２４ｂの半径方向寸法Ｌ４との和とほぼ等しい（Ｌ３≒Ｔ２＋Ｌ４）。他方のフランジ部２５の外側端面２５ａには、研削面は設けられておらず、全域がプレス成形面となっている。他方のフランジ部２５の肉厚Ｔ４は、円筒部２１の軸方向他方の端部の肉厚Ｔ２よりも厚い。 The bent portion 24 provided between the cylindrical portion 21 and the other flange portion 25 connects the outer circumferential surface of the cylindrical portion 21 and the outer end surface 25a of the other flange portion 25, as shown in an enlarged view in FIG. and an inner curved surface 24b that connects the inner circumferential surface of the cylindrical portion 21 and the inner end surface 25b of the other flange portion 25. The radial dimension L3 of the outer curved surface 24a of the bent portion 24 is approximately equal to the sum of the wall thickness T2 of the other axial end of the cylindrical portion 21 and the radial dimension L4 of the inner curved surface 24b (L3≈T2+L4). The outer end surface 25a of the other flange portion 25 is not provided with a ground surface, and the entire area is a press-formed surface. The wall thickness T4 of the other flange portion 25 is thicker than the wall thickness T2 of the other end of the cylindrical portion 21 in the axial direction.
一方のフランジ部２３と円筒部２１との間の屈曲部２２は曲げ加工で形成され、他方のフランジ部２５と円筒部２１との間の屈曲部２４は、絞り加工で形成される（詳細は後述する）。尚、図示例では、フランジ部２３、２５と円筒部２１との間の角度が略９０°に設定されているが、これらの一方又は双方の角度を９０°よりもわずかに小さい値に設定してもよい。 The bent portion 22 between the flange portion 23 and the cylindrical portion 21 on one side is formed by bending, and the bent portion 24 between the flange portion 25 and the cylindrical portion 21 on the other side is formed by drawing (details will be described later). In the illustrated example, the angle between the flange portions 23, 25 and the cylindrical portion 21 is set to approximately 90°, but one or both of these angles may be set to a value slightly smaller than 90°.
上記の保持器２０に軸方向一方側から他部材が当接すると、図３に示すように、一方のフランジ部２３の外側端面２３ａの外径端Ｐ１（すなわち、フランジ部２３の外側端面２３ａと屈曲部２２の外側曲面２２ａの内径端）にスラスト荷重Ｆ１が加わる。本実施形態では、屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１が小さくなっている（具体的には、Ｌ１／Ｔ１≦１．４を満たす）ため、スラスト荷重Ｆ１が加わる点Ｐ１が外径側に設けられる。これにより、フランジ部２３に加わるモーメント荷重が軽減されるため、フランジ部２３が傾斜することにより屈曲部２２や円筒部２１の軸方向一方の端部に加わる応力が軽減される。特に、本実施形態では、円筒部２１の軸方向一方の端部の肉厚Ｔ１が薄くなっているため、この部分に加わる荷重が軽減されることで、保持器２０のスラスト荷重に対する耐久性が高められる。 When another member abuts against the above-mentioned retainer 20 from one axial side, as shown in FIG. 3, a thrust load F1 is applied to the outer diameter end P1 of the outer end surface 23a of one flange portion 23 (i.e., the outer end surface 23a of the flange portion 23 and the inner diameter end of the outer curved surface 22a of the bent portion 22). In this embodiment, the radial dimension L1 of the outer curved surface 22a of the bent portion 22 is small (specifically, L1/T1≦1.4 is satisfied), so that the point P1 to which the thrust load F1 is applied is provided on the outer diameter side. As a result, the moment load applied to the flange portion 23 is reduced, and the stress applied to the bent portion 22 and one axial end of the cylindrical portion 21 is reduced by the inclination of the flange portion 23. In particular, in this embodiment, the wall thickness T1 of one axial end of the cylindrical portion 21 is thin, so that the load applied to this portion is reduced, thereby improving the durability of the retainer 20 against thrust loads.
一方、上記の保持器２０に軸方向他方側から他部材が当接すると、図４に示すように、他方のフランジ部２５のフランジ部２５の外側端面２５ａの外径端Ｐ２（すなわち、フランジ部２５の外側端面２５ａと屈曲部２４の外側曲面２４ａの内径端）にスラスト荷重Ｆ２が加わる。屈曲部２４の外側曲面２４ａの半径方向寸法Ｌ３は、屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１よりも大きいため、スラスト荷重Ｆ２が加わる点Ｐ２は、図３に示す点Ｐ１よりも内径側に設けられる。このため、フランジ部２５に加わるモーメント荷重は比較的大きくなるが、円筒部２１の軸方向他方の端部の肉厚Ｔ２やこれに連続する屈曲部２４の肉厚が厚くなっているため、耐久性に問題はない。もちろん、屈曲部２４の外側曲面２４ａの半径方向寸法Ｌ３を、屈曲部２２と同様に小さくしてもよく、この場合、保持器２０の耐久性がさらに高められる。 On the other hand, when another member comes into contact with the retainer 20 from the other side in the axial direction, as shown in FIG. A thrust load F2 is applied to the outer end surface 25a of the curved portion 25 and the inner diameter end of the outer curved surface 24a of the bent portion 24. Since the radial dimension L3 of the outer curved surface 24a of the bent portion 24 is larger than the radial dimension L1 of the outer curved surface 22a of the bent portion 22, the point P2 where the thrust load F2 is applied is on the inner radial side of the point P1 shown in FIG. established in Therefore, the moment load applied to the flange portion 25 becomes relatively large, but since the wall thickness T2 of the other axial end of the cylindrical portion 21 and the wall thickness of the bent portion 24 continuous thereto are thick, the durability There is no problem with sex. Of course, the radial dimension L3 of the outer curved surface 24a of the bent portion 24 may be made smaller similarly to the bent portion 22, and in this case, the durability of the retainer 20 is further improved.
次に、上記の保持器２０のプレス加工による製造方法を、図５を用いて説明する。 Next, the method of manufacturing the above-mentioned retainer 20 by press working will be explained using Figure 5.
まず、平板状の金属板（例えば鋼板）を所定形状に打ち抜いてブランク材Ｗ０を形成する（図５（Ａ）参照）。そして、このブランク材Ｗ０に絞り加工を施して、円筒成形部Ｗ１およびその軸方向一方の端部（図中上端）を閉塞する底部Ｗ２を一体に有するコップ状の成形品Ｗを形成する（図５（Ｂ）参照）。この絞り加工は、複数回に分けて行ってもよい。上記の絞り加工により円筒成形部Ｗ１が引き延ばされるため、円筒成形部Ｗ１の肉厚は底部Ｗ２の肉厚よりも薄くなる。また、上記の絞り加工により、円筒成形部Ｗ１の開口側端部を含む領域には、他の領域よりも肉厚が薄い薄肉部Ｗ１１が形成される。薄肉部Ｗ１１は、例えば金型（ポンチ）の形状を転写して成形される。 First, a blank material W0 is formed by punching out a flat metal plate (e.g., steel plate) into a predetermined shape (see FIG. 5(A)). Then, the blank material W0 is subjected to drawing to form a cup-shaped molded product W having a cylindrical molded portion W1 and a bottom portion W2 that closes one axial end (the upper end in the figure) (see FIG. 5(B)). This drawing may be performed multiple times. The cylindrical molded portion W1 is stretched by the drawing, so that the thickness of the cylindrical molded portion W1 becomes thinner than the thickness of the bottom portion W2. In addition, the drawing forms a thin-walled portion W11 that is thinner than other regions in the region including the open end of the cylindrical molded portion W1. The thin-walled portion W11 is formed by, for example, transferring the shape of a die (punch).
次に、成形品Ｗの底部Ｗ２の軸心を打ち抜いて、開口部Ｗ２０を形成する（図５（Ｃ）参照）。こうして開口部Ｗ２０が形成された底部Ｗ２が、保持器２０の他方のフランジ部２５となる。 Next, the axial center of the bottom W2 of the molded product W is punched out to form an opening W20 (see FIG. 5(C)). The bottom W2 in which the opening W20 is formed becomes the other flange 25 of the retainer 20.
次に、成形品Ｗの円筒成形部Ｗ１の軸方向他方の端部を、曲げ型で複数回に分けてプレスして内径側に屈曲させる（図５（Ｄ）参照）。このとき、円筒成形部Ｗ１の薄肉部Ｗ１１を屈曲させることで、曲げ加工が容易化される。この曲げ加工により、円筒成形部Ｗ１から内径側に延びるフランジ部Ｗ３が形成される。 Next, the other axial end of the cylindrical molded portion W1 of the molded product W is pressed in a bending die in multiple steps to bend it toward the inner diameter (see FIG. 5(D)). At this time, bending the thin-walled portion W11 of the cylindrical molded portion W1 makes the bending process easier. This bending process forms a flange portion W3 that extends from the cylindrical molded portion W1 toward the inner diameter.
次に、フランジ部Ｗ３の軸心を打ち抜いて、所定径の開口部Ｗ３０を形成する（図５（Ｅ）参照）。こうして開口部Ｗ３０が形成されたフランジ部Ｗ３が、保持器２０の一方のフランジ部２３となる。その後、円筒成形部Ｗ１の周方向複数箇所を半径方向に打ち抜いて、複数の開口部Ｗ１０を形成する（図５（Ｆ）参照）。こうして形成された開口部Ｗ１０が保持器２０のポケット２１ｂとなり、この開口部Ｗ１０を有する円筒成形部Ｗ１が保持器２０の円筒部２１となる。 Next, the flange portion W3 is punched out along its axis to form an opening W30 of a predetermined diameter (see FIG. 5(E)). The flange portion W3 with the opening W30 thus formed becomes one of the flange portions 23 of the retainer 20. After that, the cylindrical molded portion W1 is punched out in the radial direction at multiple locations around the circumference to form multiple openings W10 (see FIG. 5(F)). The openings W10 thus formed become the pockets 21b of the retainer 20, and the cylindrical molded portion W1 with these openings W10 becomes the cylindrical portion 21 of the retainer 20.
こうしてプレス成形された保持器２０の一方のフランジ部２３の外側端面２３ａに研削加工を施す。具体的に、研削加工を施す前の一方のフランジ部２３の外側端面２３ａ’は、図３に点線で示す位置に設けられ、この外側端面２３ａ’と屈曲部２２の外側曲面２２ａとの境界はＰ１’で示す位置に設けられる。この外側端面２３ａ’のうち、少なくとも外径端を含む領域（本実施形態では全域）に研削加工を施すことにより、実線で示す外側端面２３ａが形成されると共に、外側端面２３ａと屈曲部２２の外側曲面２２ａとの境界Ｐ１が、研削前の境界Ｐ１’よりも外径側に移動する。これにより、屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１が小さくなって、Ｌ１／Ｔ１≦１．４が満たされる。 The outer end surface 23a of one flange portion 23 of the retainer 20 thus press-molded is subjected to a grinding process. Specifically, the outer end surface 23a' of one flange portion 23 before being subjected to the grinding process is provided at the position shown by the dotted line in FIG. It is provided at a position indicated by P1'. By grinding a region of this outer end surface 23a' that includes at least the outer diameter end (in this embodiment, the entire area), the outer end surface 23a shown by the solid line is formed, and the outer end surface 23a and the bent portion 22 are The boundary P1 with the outer curved surface 22a moves toward the outer diameter side from the boundary P1' before grinding. As a result, the radial dimension L1 of the outer curved surface 22a of the bent portion 22 becomes smaller, and L1/T1≦1.4 is satisfied.
本発明は、上記の実施形態に限られない。以下、本発明の他の実施形態を説明するが、上記の実施形態と同様の点については重複説明を省略する。 The present invention is not limited to the embodiments described above. Other embodiments of the present invention will be described below, but redundant explanation of points similar to the above embodiments will be omitted.
図６に示す実施形態では、屈曲部２２の曲率半径を小さくすることにより、屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１を小さくしている。図示例では、一方のフランジ部２３と円筒部２１との間の角度を積極的に小さくする（例えば、８９．９°以下とする）ことにより、屈曲部２２の曲率半径を小さくして外側曲面２２ａの半径方向寸法Ｌ１を小さくし、Ｌ１／Ｔ１≦１．４を満たすようにしている。尚、本実施形態では、外側曲面２２ａが、厳密には、軸方向外側の端部Ｐ１（頂点）よりも内径側の点Ｑまで延びているが、本発明では、外側曲面２２ａの半径方向寸法Ｌ１は、外側曲面２２ａの外径端と軸方向外側の端部Ｐ１との間の半径方向寸法のことを意味するものとする。 6, the radius of curvature of the bent portion 22 is reduced, thereby reducing the radial dimension L1 of the outer curved surface 22a of the bent portion 22. In the illustrated example, the angle between one flange portion 23 and the cylindrical portion 21 is actively reduced (for example, to 89.9° or less), thereby reducing the radius of curvature of the bent portion 22 and reducing the radial dimension L1 of the outer curved surface 22a, so as to satisfy L1/T1≦1.4. In this embodiment, strictly speaking, the outer curved surface 22a extends to a point Q on the inner diameter side of the axially outer end P1 (apex), but in the present invention, the radial dimension L1 of the outer curved surface 22a means the radial dimension between the outer diameter end of the outer curved surface 22a and the axially outer end P1.
本発明に係る保持器及びこれを備えた針状ころ軸受は、産業用ロボットの減速機に限らず、工作機械等の他の機械の回転軸を支持する軸受として組み込むことができる。 The cage according to the present invention and the needle roller bearing equipped with the same can be incorporated not only into reducers of industrial robots but also as bearings that support rotating shafts of other machines such as machine tools.
ＦＥＭ解析により、図２に示す保持器２０の屈曲部２２の外側曲面２２ａの半径方向寸法Ｌ１と、円筒部２１の軸方向一方の端部の肉厚Ｔ１とを異ならせた複数の試験片に対し、軸方向一方側から他部材を当接させたときに、破損領域の応力が発生するか否かを確認した。その結果を下記の表１に示す。 FEM analysis was used to confirm whether or not stress occurs in the fracture area when another member is brought into contact with multiple test pieces that have different radial dimensions L1 of the outer curved surface 22a of the bent portion 22 of the retainer 20 shown in Figure 2 and different wall thicknesses T1 of one axial end of the cylindrical portion 21 from one axial side. The results are shown in Table 1 below.
表１に示されるように、Ｌ１／Ｔ１が１．４を超えている比較例１及び２には破損領域の応力が発生したのに対し、Ｌ１／Ｔ１が１．４以下である実施例１～３には破損領域の応力は発生しなかった。 As shown in Table 1, stress occurred in the damage area in Comparative Examples 1 and 2, where L1/T1 exceeded 1.4, whereas no stress occurred in the damage area in Examples 1 to 3, where L1/T1 was 1.4 or less.
次に、Ｌ１／Ｔ１が２．０である複数の従来品と、Ｌ１／Ｔ１が１．３３である複数の本発明品に対し、スラスト荷重を負荷しながら回転試験を行った。その結果、図７に示すように、従来品は何れも短時間で破断した（柱部の軸方向一方の端部が破断した）。これに対し、本発明品は、基準の８．１倍の時間を超えても保持器は破断しなかった（本明細書作成時点で試験継続中）。以上の結果から、Ｌ１／Ｔ１を１．４以下とする本発明により保持器の耐久性が向上することが確認された。 Next, a rotation test was conducted while applying a thrust load to several conventional products with an L1/T1 ratio of 2.0 and several products of the present invention with an L1/T1 ratio of 1.33. As a result, as shown in Figure 7, all of the conventional products broke in a short time (one axial end of the column broke). In contrast, the cage of the product of the present invention did not break even after 8.1 times the standard time (testing was ongoing at the time of writing this specification). From these results, it was confirmed that the durability of the cage is improved by the present invention, which sets L1/T1 at 1.4 or less.
１ クランク軸
２ 針状ころ軸受
２０ 保持器
２１ 円筒部
２２ 屈曲部
２３ 一方のフランジ部
２４ 屈曲部
２５ 他方のフランジ部
Ｗ 成形品
Ｗ１ 円筒成形部
Ｗ１１ 薄肉部
Ｗ２ 底部
Ｗ３ フランジ部
1 Crankshaft 2 Needle roller bearing 20 Cage 21 Cylindrical part 22 Bent part 23 One flange part 24 Bent part 25 Other flange part W Molded product W1 Cylindrical molded part W11 Thin part W2 Bottom part W3 Flange part
Claims (9)
前記第１の屈曲部が曲げ加工で形成され、
前記第１の屈曲部の外側曲面の前記円筒部側の端部が、前記一方のフランジ部の軸方向内側の端面の外径端よりも軸方向内側に配され、
前記第１の屈曲部の外側曲面の半径方向寸法Ｌ１と、前記円筒部の軸方向一方の端部の肉厚Ｔ１とが、Ｌ１／Ｔ１≦１．４を満たす針状ころ軸受用保持器。 a cylindrical part having a plurality of pillar parts and a plurality of pockets provided between adjacent pillar parts in the circumferential direction; and a second flange extending radially inward from the other axial end of the cylindrical part via a second bent part. A retainer,
the first bent portion is formed by bending;
an end portion of the outer curved surface of the first bent portion on the cylindrical portion side is arranged axially inwardly than an outer diameter end of an axially inner end surface of the one flange portion;
A cage for a needle roller bearing, wherein a radial dimension L1 of an outer curved surface of the first bent portion and a wall thickness T1 of one axial end of the cylindrical portion satisfy L1/T1≦1.4.
The needle roller bearing according to claim 8, wherein the roller filling rate is 70% or more.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2024006110A JP2024045260A (en) | 2019-07-10 | 2024-01-18 | Needle roller bearing cages and needle roller bearings |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2019128555A JP2021014863A (en) | 2019-07-10 | 2019-07-10 | Cage for needle roller bearing and needle roller bearing |
| JP2024006110A JP2024045260A (en) | 2019-07-10 | 2024-01-18 | Needle roller bearing cages and needle roller bearings |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2019128555A Division JP2021014863A (en) | 2019-07-10 | 2019-07-10 | Cage for needle roller bearing and needle roller bearing |
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| Publication Number | Publication Date |
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| JP2024045260A true JP2024045260A (en) | 2024-04-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2019128555A Pending JP2021014863A (en) | 2019-07-10 | 2019-07-10 | Cage for needle roller bearing and needle roller bearing |
| JP2024006110A Pending JP2024045260A (en) | 2019-07-10 | 2024-01-18 | Needle roller bearing cages and needle roller bearings |
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| Application Number | Title | Priority Date | Filing Date |
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| JP2019128555A Pending JP2021014863A (en) | 2019-07-10 | 2019-07-10 | Cage for needle roller bearing and needle roller bearing |
Country Status (4)
| Country | Link |
|---|---|
| JP (2) | JP2021014863A (en) |
| CN (1) | CN113993639A (en) |
| DE (1) | DE112020003265T5 (en) |
| WO (1) | WO2021005994A1 (en) |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005076810A (en) * | 2003-09-02 | 2005-03-24 | Nsk Ltd | Retainer for needle bearing and needle bearing |
| JP3984972B2 (en) * | 2004-05-13 | 2007-10-03 | 日本トムソン株式会社 | Roller bearing and method for manufacturing the same |
| JP5246742B2 (en) * | 2007-12-27 | 2013-07-24 | Ｎｔｎ株式会社 | Roller bearing cage and needle roller bearing |
| JP2011012699A (en) * | 2009-06-30 | 2011-01-20 | Nsk Ltd | Guide structure of retainer end face |
| JP2012057751A (en) | 2010-09-10 | 2012-03-22 | Ntn Corp | Retainer and needle roller bearing |
| DE102011085716A1 (en) * | 2011-11-03 | 2013-05-08 | Schaeffler Technologies AG & Co. KG | Radial cage e.g. needle bearing cage for cylindrical rolling elements, has profile rollers and side rings that are arranged, such that material thicknesses of rollers are smaller than thickness of side portions of axial webs |
| JP2014159846A (en) * | 2013-02-20 | 2014-09-04 | Nsk Ltd | Roller bearing and fixation device |
| JP2016161117A (en) * | 2015-03-05 | 2016-09-05 | Ntn株式会社 | Cycloid speed reducer and motor drive device with cycloid speed reducer |
| JP6585271B2 (en) | 2018-11-29 | 2019-10-02 | ナブテスコ株式会社 | Reduction gear group, reduction gear and reduction gear design method |
-
2019
- 2019-07-10 JP JP2019128555A patent/JP2021014863A/en active Pending
-
2020
- 2020-06-18 CN CN202080044342.7A patent/CN113993639A/en active Pending
- 2020-06-18 DE DE112020003265.5T patent/DE112020003265T5/en active Pending
- 2020-06-18 WO PCT/JP2020/023910 patent/WO2021005994A1/en active Application Filing
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2024
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Also Published As
| Publication number | Publication date |
|---|---|
| JP2021014863A (en) | 2021-02-12 |
| CN113993639A (en) | 2022-01-28 |
| DE112020003265T5 (en) | 2022-03-24 |
| WO2021005994A1 (en) | 2021-01-14 |
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