JP7505941B2 - Needle roller bearings - Google Patents
Needle roller bearings Download PDFInfo
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- JP7505941B2 JP7505941B2 JP2020144350A JP2020144350A JP7505941B2 JP 7505941 B2 JP7505941 B2 JP 7505941B2 JP 2020144350 A JP2020144350 A JP 2020144350A JP 2020144350 A JP2020144350 A JP 2020144350A JP 7505941 B2 JP7505941 B2 JP 7505941B2
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- needle roller
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- 239000007787 solid Substances 0.000 claims description 9
- 238000005096 rolling process Methods 0.000 description 10
- 229910000831 Steel Inorganic materials 0.000 description 5
- 239000010959 steel Substances 0.000 description 5
- 239000003921 oil Substances 0.000 description 4
- 238000003825 pressing Methods 0.000 description 4
- 230000000052 comparative effect Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 238000005520 cutting process Methods 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 230000035699 permeability Effects 0.000 description 2
- 230000035939 shock Effects 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000012447 hatching Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005498 polishing Methods 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 238000007665 sagging Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Classifications
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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
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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
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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
- F16C33/58—Raceways; Race rings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Description
本発明は、転がり軸受に関し、特にころを保持する保持器に関する。 The present invention relates to rolling bearings, and in particular to a cage that holds rollers.
針状ころおよび保持器を備える転がり軸受として例えば特許文献１および特許文献２に記載されるシェル形針状ころ軸受が知られている。特許文献１の保持器は、柱部の軸方向一端から他端まで真っ直ぐに延び、柱部全体の径方向寸法が１対のリング部の径方向厚みと等しくされることから、ストレート形状保持器ともいう。特許文献２の保持器は、柱部の軸方向中央部分が軸方向両端部分よりも内径側に配置されることから、Ｖ形保持器ともいう。 As a rolling bearing equipped with needle rollers and a cage, for example, the shell-shaped needle roller bearing described in Patent Document 1 and Patent Document 2 is known. The cage in Patent Document 1 extends straight from one axial end of the column to the other, and the radial dimension of the entire column is made equal to the radial thickness of the pair of ring portions, so it is also called a straight-shaped cage. The cage in Patent Document 2 is also called a V-shaped cage, because the axial center portion of the column is positioned closer to the inner diameter than both axial end portions.
ストレート形状保持器は、板厚が大きいとばりやだれが大きく出てしまうため、板厚に制限がある。また、針状ころが保持器から脱落しない設計とするため、保持器外径が針状ころのピッチ円ＰＣＤよりも小さくされる。このため針状ころは、保持器の柱部の外径側で案内され、柱部の外径側角部と接触する。角部には油膜が形成されないばかりでなく、角部はころ転動面の油膜形成を阻害する。また針状ころが保持器を押すことにより発生する応力が大きくなるため、保持器強度に劣る。 Straight-shaped cages have limitations on plate thickness because larger plate thicknesses result in greater burrs and sagging. Also, to prevent the needle rollers from falling off the cage, the cage outer diameter is made smaller than the pitch circle PCD of the needle rollers. As a result, the needle rollers are guided by the outer diameter side of the cage column and come into contact with the corners on the outer diameter side of the column. Not only does an oil film not form at the corners, but the corners also inhibit the formation of an oil film on the roller rolling surfaces. Also, the stress generated by the needle rollers pressing against the cage is large, resulting in inferior cage strength.
次に、従来のＶ形保持器を図７の縦断面図および正面図で示す。Ｖ形保持器１１２は、保持器を薄板で構成しつつも保持器全体の径方向厚み寸法を大きくできる点で、ストレート形状保持器よりも有利である。Ｖ形保持器１１２は、軸方向に離隔する１対のリング部１１３，１１３と、これらリング部１１３同士を連結する複数の柱部１１４を有する。柱部１１４の軸方向両端部分１１６および軸方向中央部分１１７の間の段付きはロール成形によって形成される。針状ころ１１１のピッチ円ＰＣＤは、径方向外側の段に相当する軸方向両端部分１１６と交差する。径方向内側の段に相当する軸方向中央部分１１７は、ピッチ円ＰＣＤよりも内径側に配置され、針状ころ１１１がポケット１１５から径方向内側へ脱落することを防止する。Ｖ形保持器によれば、針状ころが保持器の面で案内される。角ではなく面で案内される利点として、通油性は上述したストレート形状保持器よりも優れ、ころが保持器を押すことにより当該保持器に発生する応力はストレート形状保持器よりも小さい。 Next, a conventional V-shaped retainer is shown in a longitudinal section and a front view in FIG. 7. The V-shaped retainer 112 is advantageous over a straight-shaped retainer in that the retainer can be made of thin plates while the radial thickness dimension of the entire retainer can be increased. The V-shaped retainer 112 has a pair of ring portions 113, 113 spaced apart in the axial direction, and a number of column portions 114 connecting these ring portions 113. The steps between the axial end portions 116 and the axial center portion 117 of the column portion 114 are formed by roll forming. The pitch circle PCD of the needle roller 111 intersects with the axial end portions 116 corresponding to the radially outer step. The axial center portion 117 corresponding to the radially inner step is arranged on the inner diameter side of the pitch circle PCD, preventing the needle roller 111 from falling out of the pocket 115 radially inward. With the V-shaped retainer, the needle roller is guided by the surface of the retainer. The advantage of being guided by a surface rather than a corner is that it has better oil permeability than the straight-shaped cage mentioned above, and the stress generated in the cage by the rollers pressing against it is smaller than that of a straight-shaped cage.
特許文献１および特許文献２のシェル形針状ころ軸受は主に、エンジン車両の駆動系の回転要素の転がり支持に使用される。 The drawn cup needle roller bearings in Patent Documents 1 and 2 are primarily used to support the rolling elements of the drive train of engine vehicles.
昨今の省燃費化の要請を受けて、ガソリンを燃料とするエンジン車両から電気自動車やハイブリッドカーへ移行するに従い、車両はエンジン駆動から電気モータ駆動へと代替される。これにより駆動系回転要素の軸受が、今までよりも速い回転数で使用される場合が増える。 In response to the recent demand for fuel economy, vehicles are shifting from gasoline-fueled engine vehicles to electric vehicles and hybrid cars, and as a result, vehicles are being switched from being engine-driven to being electric motor-driven. This means that there are more cases where bearings in the rotating elements of the drive system are used at higher rotation speeds than before.
具体的には、針状ころ１１１がＶ形保持器１１２に及ぼす力が今までよりも大きくなる。一方で針状ころ１１１は内径段になる軸方向中央部分１１７には当接せず、外径段になる軸方向両端部分１１６のみで案内されるため、針状ころ１１１とＶ形保持器１１２の柱部１１４が互いに接触するころ案内面は軸方向両端部分１１６に限定される。そうすると以下の問題が懸念される。 Specifically, the force that the needle rollers 111 exert on the V-shaped retainer 112 will be greater than ever before. On the other hand, the needle rollers 111 do not come into contact with the axial center portion 117, which is the inner diameter step, and are guided only by the axial end portions 116, which are the outer diameter steps. Therefore, the roller guide surfaces where the needle rollers 111 and the column portions 114 of the V-shaped retainer 112 come into contact with each other are limited to the axial end portions 116. This gives rise to the following concerns:
第１に、保持器強度の問題が懸念される。針状ころ１１１とＶ形保持器１１２の柱部１１４の接触が軸方向両端部分１１６に限られるため、ポケット隅Ｒに発生する主応力が大きくなり、Ｖ形保持器１１２の耐久性が悪化する。図１を参照すると、ポケット隅Ｒは一般的に柱部１４とリング部１３の結合箇所で区画され、円弧状に切り欠かれている。円弧状に切り欠かれているため、従来はポケット隅Ｒに発生する主応力が緩和されていた。しかし今後は、上述した理由により、ポケット隅Ｒに発生する主応力が新たな問題となる。 First, there is concern about the strength of the cage. Because contact between the needle rollers 111 and the column sections 114 of the V-shaped cage 112 is limited to both axial end sections 116, the principal stress generated at the pocket corners R increases, and the durability of the V-shaped cage 112 deteriorates. Referring to FIG. 1, the pocket corners R are generally defined by the joints between the column sections 14 and the ring section 13, and are cut out in an arc shape. Because they are cut out in an arc shape, the principal stress generated at the pocket corners R has traditionally been alleviated. However, in the future, for the reasons mentioned above, the principal stress generated at the pocket corners R will become a new problem.
第２に、摩耗の問題が懸念される。軸受が使用される回転数が速くなると、針状ころ１１１がＶ形保持器１１２の柱部１１４を押すことにより発生する接触面圧（Pressure）と滑り速度（Velocity）の積（ＰＶ値）が大きくなる。さらに針状ころ１１１とＶ形保持器１１２の接触長さＬｃが外径段に限られるため、押し力Ｆ／接触長さＬｃで算出される接触面圧（Pressure）が大きくなる。そうすると柱部１１４の早期摩耗が懸念される。 Secondly, there is concern about wear. As the rotational speed at which the bearing is used increases, the product (PV value) of the contact surface pressure (Pressure) and the sliding speed (Velocity) generated by the needle rollers 111 pressing against the column sections 114 of the V-shaped retainer 112 increases. Furthermore, because the contact length Lc between the needle rollers 111 and the V-shaped retainer 112 is limited to the outer diameter stage, the contact surface pressure (Pressure) calculated as pressing force F/contact length Lc increases. This raises concerns about early wear of the column sections 114.
第３に、針状ころ軸受の負荷容量の低下が懸念される。上述した主応力増大に対応するためには、リング部１１３の幅Ｌｎを大きくする必要がある。リング部１１３の幅Ｌｎを大きくとると、限られた軸受の周方向寸法の残りになるポケット軸方向寸法が小さくなり、さらに針状ころ１１１のころ長が小さくなり、針状ころ軸受の負荷容量が小さくなるので不利になる。 Thirdly, there is concern about a decrease in the load capacity of the needle roller bearing. In order to deal with the increase in principal stress mentioned above, it is necessary to increase the width Ln of the ring portion 113. If the width Ln of the ring portion 113 is increased, the axial dimension of the pocket, which is the remaining limited circumferential dimension of the bearing, will become smaller, and the roller length of the needle rollers 111 will become smaller, which will result in a decrease in the load capacity of the needle roller bearing, which is disadvantageous.
本発明は、今まで使用することのなかった高速回転環境下で有利に使用できる技術を提供することを目的とする。 The present invention aims to provide technology that can be advantageously used in high-speed rotation environments that have not been used before.
この目的のため本発明による針状ころ軸受は、１対のリング部、および両端が１対のリング部にそれぞれ結合する複数の柱部とを有し、周方向で隣り合う柱部同士間にポケットを区画する保持器と、ポケットに保持される針状ころとを備える。そして柱部のうち軸方向両端部分が外径側に配置され、柱部のうち軸方向中央部分が内径側に配置され、軸方向両端部分および軸方向中央部分はポケットに面するポケット壁面を有し、軸方向両端部分に設けられるポケット壁面のうち内径側領域と、軸方向中央部分に設けられるポケット壁面のうち外径側領域が、径方向位置に関して重複する重複領域を構成する。そして重複領域は、針状ころを案内するころ案内面を含む。 For this purpose, the needle roller bearing according to the present invention comprises a cage having a pair of ring portions and a number of column portions, both ends of which are respectively connected to the pair of ring portions, which defines pockets between adjacent column portions in the circumferential direction, and needle rollers held in the pockets. The column portions have both axial end portions arranged on the outer diameter side, and the axial center portion arranged on the inner diameter side, and both axial end portions and the axial center portion have pocket wall surfaces facing the pockets, and the inner diameter side region of the pocket wall surfaces provided at both axial end portions and the outer diameter side region of the pocket wall surfaces provided at the axial center portion form an overlapping region in which they overlap in terms of radial position. The overlapping region includes a roller guide surface that guides the needle rollers.
かかる本発明によれば、ころ案内面が柱部の一端部から他端部までの長さになるため、従来よりも大きくなる。したがってポケット隅Ｒに発生する主応力を小さくして、Ｖ形保持器の耐久性が向上する。また接触面圧（Pressure）が従来よりも小さくなるため、針状ころ軸受が高速回転する場合であってもＰＶ値の増大を抑制することができ、柱部の早期摩耗が解消される。さらにポケット隅Ｒの主応力を小さくすることができるので、リング部の幅を殊更大きくする必要がない。したがって、針状ころのころ長をこれまで通りとして、針状ころ軸受の負荷容量を確保することができる。なお、ころ案内面とは、ポケット壁面のうち針状ころの転動面と接触する面をいう。 According to the present invention, the roller guide surface is the length from one end to the other end of the column portion, which is larger than the conventional one. Therefore, the principal stress generated at the pocket corner R is reduced, improving the durability of the V-shaped retainer. In addition, since the contact surface pressure is smaller than the conventional one, it is possible to suppress an increase in the PV value even when the needle roller bearing rotates at high speed, and early wear of the column portion is eliminated. Furthermore, since the principal stress at the pocket corner R can be reduced, there is no need to particularly increase the width of the ring portion. Therefore, the load capacity of the needle roller bearing can be secured while keeping the roller length of the needle roller the same as before. The roller guide surface refers to the surface of the pocket wall that comes into contact with the rolling surface of the needle roller.
針状ころは保持器の径方向に若干の相対移動可能であることから、ころ案内面は保持器の径方向に幅寸法を有する。ころ案内面は、重複領域と一致してもよいし、あるいは重複領域よりも小さくてもよい。換言すると、複数の針状ころが全て中立位置にあるときのピッチ円からみて、保持器は若干の偏心移動を許容される。本発明の一局面としてポケット壁面の重複領域は、針状ころのピッチ円と交差する。かかる局面によれば、ピッチ円の接線方向に針状ころを案内することができるので、接触面圧を小さくすることができる。他の局面として、ポケット壁面の重複領域は、針状ころのピッチ円よりも外径側にずれていてもよいし、あるいは内径側にずれていてもよい。 Since the needle rollers are capable of slight relative movement in the radial direction of the cage, the roller guide surface has a width dimension in the radial direction of the cage. The roller guide surface may coincide with the overlapping area or may be smaller than the overlapping area. In other words, the cage is allowed to move slightly eccentrically from the pitch circle when all of the needle rollers are in their neutral positions. In one aspect of the present invention, the overlapping area of the pocket wall surface intersects with the pitch circle of the needle rollers. According to this aspect, the needle rollers can be guided in the tangential direction of the pitch circle, so that the contact surface pressure can be reduced. In another aspect, the overlapping area of the pocket wall surface may be shifted toward the outer diameter side or toward the inner diameter side from the pitch circle of the needle rollers.
本発明の針状ころ軸受は、様々な外輪とともに使用可能である。本発明の好ましい局面として針状ころ軸受は、針状ころが転動する外側軌道面を構成するシェル外輪をさらに備える。シェル外輪は、溶接して円筒形状にされるのではなく、深絞り加工により円筒形状にされる。本発明の他の局面として針状ころ軸受は、針状ころが転動する外側軌道面を構成するソリッド外輪をさらに備える。ソリッド外輪は、削り出しによって形成される。本発明の他の局面として、針状ころ軸受は保持器付きころであってもよい。 The needle roller bearing of the present invention can be used with a variety of outer rings. In a preferred aspect of the present invention, the needle roller bearing further comprises a shell outer ring that constitutes the outer raceway on which the needle rollers roll. The shell outer ring is not welded into a cylindrical shape, but is formed into a cylindrical shape by deep drawing. In another aspect of the present invention, the needle roller bearing further comprises a solid outer ring that constitutes the outer raceway on which the needle rollers roll. The solid outer ring is formed by machining. In another aspect of the present invention, the needle roller bearing may be a roller with a cage.
本発明のさらに他の局面として保持器は、リング部の軸方向外側縁から内径側へ突出する鍔部を含む。かかる局面によれば、保持器強度が大きくなり、耐久性が向上する。あるいはリング部の軸方向寸法を小さくし、ポケットの軸方向寸法および針状ころのころ長を大きくして、負荷容量を増大させることができる。 In yet another aspect of the present invention, the cage includes a flange that protrudes from the axially outer edge of the ring portion toward the inner diameter side. This aspect increases the strength of the cage and improves durability. Alternatively, the load capacity can be increased by reducing the axial dimension of the ring portion and increasing the axial dimension of the pocket and the roller length of the needle rollers.
本発明の一局面として、保持器は針状ころに案内されるころ案内とされる。本発明の他の局面として、保持器は外側軌道面に案内される外輪案内とされる。 In one aspect of the invention, the cage is roller-guided and guided by needle rollers. In another aspect of the invention, the cage is outer-ring-guided and guided by an outer raceway.
柱部の軸方向両端部分および軸方向中央部分の径方向段差は、軸方向中央部分の径方向肉厚の１．０倍未満であることから、軸方向両端部分および軸方向中央部分が保持器の径方向に重複する重複領域を柱部に設けることができる。本発明の一局面として、柱部の軸方向両端部分および軸方向中央部分の径方向段差が、軸方向中央部分の径方向肉厚の０．２倍以上０．８倍以下の範囲に含まれる。これにより上述した重複領域の上限値を８０％とし、下限値を２０％に設定することができる。 The radial step between the axial end portions and the axial center portion of the column is less than 1.0 times the radial thickness of the axial center portion, so that an overlapping region in which the axial end portions and the axial center portion overlap in the radial direction of the cage can be provided in the column. As one aspect of the present invention, the radial step between the axial end portions and the axial center portion of the column is in the range of 0.2 to 0.8 times the radial thickness of the axial center portion. This allows the upper limit of the overlapping region to be set to 80% and the lower limit to 20%.
このように本発明によれば、従来の針状ころ軸受と比較して本発明を高速運転する場合であっても、保持器のポケット隅Ｒに発生する主応力を小さくして、保持器の耐久性を向上させることができる。またＰＶ値が少なくなり、摩耗が軽減される。さらに針状ころ軸受の負荷容量を大きくすることができる。 As described above, according to the present invention, the principal stress generated at the pocket corner R of the cage can be reduced and the durability of the cage can be improved, even when the present invention is operated at high speeds compared to conventional needle roller bearings. In addition, the PV value is reduced, and wear is reduced. Furthermore, the load capacity of the needle roller bearing can be increased.
以下、本発明の実施の形態を、図面に基づき詳細に説明する。図１は、本発明の一実施形態になる保持器を示す正面図であり、外径側から見た状態を表す。図２は、同実施形態になる保持器および針状ころを示す縦断面図であり、保持器の軸線を含む平面で当該保持器を切断した切断面を拡大して表す。図３は、同実施形態になる保持器および針状ころを示す横断面図であり、保持器の軸線に直角な平面で当該保持器を切断し、軸線よりも上方の切断面および下方の切断面を取り出して拡大表示する。なお図の煩雑を避けるため、図２以降では、紙面最上部または最下部のポケットおよび柱部を表し、残りを図略する。 The following describes in detail an embodiment of the present invention with reference to the drawings. FIG. 1 is a front view of a cage according to one embodiment of the present invention, as viewed from the outer diameter side. FIG. 2 is a longitudinal section of the cage and needle rollers according to the embodiment, showing an enlarged cut surface of the cage cut on a plane including the axis of the cage. FIG. 3 is a transverse section of the cage and needle rollers according to the embodiment, showing an enlarged cut surface of the cage cut on a plane perpendicular to the axis of the cage, with the cut surfaces above and below the axis taken out. In order to avoid cluttering the figures, in FIG. 2 and subsequent figures, only the pockets and columns at the top or bottom of the page are shown, and the rest are omitted.
本実施形態の針状ころ軸受は、針状ころ（以下、単にころ１１という）および保持器１２を備える。ころ１１のころ長Ｌｒは、ころ径φｒの３倍以上１０倍以下の範囲に含まれる（３φｒ≦Ｌｒ＜１０φｒ。保持器１２は、１対のリング部１３，１３、および両端が１対のリング部１３，１３にそれぞれ結合する複数の柱部１４を有する。１対のリング部１３，１３は、保持器１２の周方向に延び、軸方向に間隔を空けて配置される。柱部１４は、保持器１２の軸方向に延び、リング部１３の周方向に等間隔に配置されることから、周方向で隣り合う柱部１４，１４同士間にポケット１５を区画する。ころ１１は、各ポケット１５に保持される。 The needle roller bearing of this embodiment includes needle rollers (hereinafter simply referred to as rollers 11) and a cage 12. The roller length Lr of the rollers 11 is in the range of 3 to 10 times the roller diameter φr (3φr≦Lr<10φr. The cage 12 has a pair of ring portions 13, 13 and multiple column portions 14 whose both ends are connected to the pair of ring portions 13, 13. The pair of ring portions 13, 13 extend in the circumferential direction of the cage 12 and are spaced apart in the axial direction. The column portions 14 extend in the axial direction of the cage 12 and are arranged at equal intervals in the circumferential direction of the ring portions 13, so that pockets 15 are defined between the column portions 14, 14 adjacent to each other in the circumferential direction. The rollers 11 are held in each pocket 15.
図１に示すように、柱部１４は軸方向両端部分１６，１６および軸方向中央部分１７を含む。図２に示すように、軸方向両端部分１６，１６は保持器１２の軸線Ｏからみて遠い外径側に配置される一方、軸方向中央部分１７は軸線Ｏに近い内径側に配置されることから、柱部１４はいわゆるＶ字形状とされる。このため保持器１２はＶ形保持器ともいう。 As shown in FIG. 1, the column portion 14 includes both axial end portions 16, 16 and an axial center portion 17. As shown in FIG. 2, the both axial end portions 16, 16 are located on the outer diameter side far from the axis O of the cage 12, while the axial center portion 17 is located on the inner diameter side closer to the axis O, so that the column portion 14 is formed into a so-called V-shape. For this reason, the cage 12 is also called a V-shaped cage.
ここで保持器１２の製造方法につき附言すると、まず帯状鋼板を準備し、次に帯板鋼板をロール成形して断面Ｖ字状に形成し、次に打ち抜き加工によって帯状鋼板にポケット１５を形成し、次に帯状鋼板を所定の長さに切断し、次に帯状鋼板を円筒形状に丸めて端部同士を溶接し、次に研摩加工を施す。 In addition, the manufacturing method of the retainer 12 involves first preparing a strip of steel plate, then roll forming the strip of steel plate to form a V-shaped cross section, then punching to form pockets 15 in the strip of steel plate, then cutting the strip of steel plate to a specified length, then rolling the strip of steel plate into a cylindrical shape and welding the ends together, and then polishing.
本実施形態の軸方向両端部分１６，１６および軸方向中央部分１７は、保持器１２の径方向に完全にずれているのではなく、径方向位置が一部重なり、かかる重複領域Ｒｂでころ１１の転動面と接触する。図２中、重複領域Ｒｂを破線のハッチングで表示する。重複領域Ｒｂの内径縁は、軸方向両端部分１６の内径面１６ｄになる。重複領域Ｒｂの外径縁は、軸方向中央部分１７の外径面１７ｃになる。つまり本実施形態の重複領域Ｒｂはころ案内面である。 In this embodiment, the axial end portions 16, 16 and the axial center portion 17 are not completely offset in the radial direction of the cage 12, but rather overlap in radial positions, and contact the rolling surfaces of the rollers 11 in this overlap region Rb. In FIG. 2, the overlap region Rb is shown by dashed hatching. The inner diameter edge of the overlap region Rb becomes the inner diameter surface 16d of the axial end portions 16. The outer diameter edge of the overlap region Rb becomes the outer diameter surface 17c of the axial center portion 17. In other words, the overlap region Rb in this embodiment is a roller guide surface.
本実施形態では重複領域Ｒｂを得るため、柱部１４の外径段と内径段の段差、すなわち軸方向両端部分１６の外径面１７ｃと軸方向中央部分１７の外径面１６ｃの径方向段差Ｒｄが軸方向中央部分１７の板厚Ｔｐよりも小さい（Ｒｄ＜Ｔｐ）。より好ましくは、径方向段差Ｒｄが、板厚Ｔｐの０．２倍以上０．８倍以下の範囲に含まれるようにされる（０．２Ｔｐ≦Ｒｄ≦０．８Ｔｐ）。これにより、Ｖ形保持器の第１の利点である、板厚Ｔｐの薄肉化と、保持器１２の径方向厚み寸法の増大を得ることができる。またＶ形保持器の第２の利点として、平面状の重複領域Ｒｂでころ１１を案内するため、ころ転動面がころ案内面になる重複領域Ｒｂに接触するに際して潤滑油が供給され、針状ころ軸受の通油性が向上する。さらにピッチ円ＰＣＤが重複領域Ｒｂと重なるので、ころ転動面がころ案内面である重複領域Ｒｂに接触するに際して接触面圧が小さくなる。なお段差が小さい場合（Ｒｄ＜０．２Ｔｐ）、重複率が８０％を超えてしまい、Ｖ形保持器の利点を得難くなる。反対に段差が大きい場合（０．８Ｔｐ＜Ｒｄ）、重複領域Ｒｂが少なくなってしまい（重複率２０％未満）、ピッチ円ＰＣＤが重複領域から外れる場合が生じる。板厚Ｔｐは、リング部１３の板厚、あるいは軸方向両端部分１６の板厚、あるいは軸方向中央部分１７の板厚である。これらの板厚は略等しい。 In this embodiment, in order to obtain the overlap region Rb, the step between the outer diameter step and the inner diameter step of the column portion 14, i.e., the radial step Rd between the outer diameter surface 17c of the axial end portions 16 and the outer diameter surface 16c of the axial center portion 17, is smaller than the plate thickness Tp of the axial center portion 17 (Rd<Tp). More preferably, the radial step Rd is set to be within the range of 0.2 to 0.8 times the plate thickness Tp (0.2Tp≦Rd≦0.8Tp). This provides the first advantage of the V-shaped retainer, namely, the thinning of the plate thickness Tp and the increase in the radial thickness dimension of the retainer 12. The second advantage of the V-shaped retainer is that the rollers 11 are guided by the planar overlap region Rb, so that lubricating oil is supplied when the roller rolling surface comes into contact with the overlap region Rb, which becomes the roller guide surface, improving the oil permeability of the needle roller bearing. Furthermore, since the pitch circle PCD overlaps with the overlap region Rb, the contact pressure is reduced when the roller rolling surface comes into contact with the overlap region Rb, which is the roller guide surface. If the step is small (Rd<0.2Tp), the overlap rate exceeds 80%, making it difficult to obtain the advantages of the V-shaped retainer. Conversely, if the step is large (0.8Tp<Rd), the overlap region Rb becomes small (overlap rate less than 20%), and the pitch circle PCD may deviate from the overlap region. The plate thickness Tp is the plate thickness of the ring portion 13, or the plate thickness of both axial end portions 16, or the plate thickness of the axial center portion 17. These plate thicknesses are approximately equal.
本実施形態では、径方向段差Ｒｄ＝０．２Ｔｐであり、重複領域Ｒｂの重複率は板厚Ｔｐの８０％である。 In this embodiment, the radial step Rd = 0.2Tp, and the overlap rate of the overlap region Rb is 80% of the plate thickness Tp.
さらに本実施形態では、軸方向両端部分１６に属するポケット壁面１８のうちの内径側領域と、軸方向中央部分１７に属するポケット壁面１８のうちの外径側領域が、ころ案内面である重複領域Ｒｂを含む。 Furthermore, in this embodiment, the inner diameter side region of the pocket wall surface 18 belonging to both axial end portions 16 and the outer diameter side region of the pocket wall surface 18 belonging to the axial center portion 17 include an overlap region Rb which is a roller guide surface.
図３を参照して、ポケット壁面１８，１８は、互いに平行に延びる柱部１４，１４の周方向間隔は、軸方向両端部分１６の外径縁同士で最も大きく、軸方向中央部分１７，１７同士の間隔は内径縁で最も小さく、かかるポケット隙間Ｇｐはころ径φｒの９７％以下である。これによりころ１１はポケット１５に保持され、取扱い時の衝撃などにより内径側へ抜け落ちることを防止される。 Referring to FIG. 3, the circumferential spacing between the parallel column sections 14, 14 of the pocket walls 18, 18 is greatest at the outer diameter edges of the axial end sections 16, and the spacing between the axial center sections 17, 17 is smallest at the inner diameter edges, and the pocket gap Gp is 97% or less of the roller diameter φr. This holds the rollers 11 in the pockets 15 and prevents them from falling out to the inner diameter side due to shock during handling, etc.
ここで附言すると、ポケット隙間Ｇｐはころ径φｒの９０％以上９７％以下であることが好ましい。ポケット隙間Ｇｐがころ径φｒの９０％未満であると、ピッチ円ＰＣＤが重複領域Ｒｂから外径側に外れる虞がある。９７％を超えると、取扱い時の衝撃などにより、ころが保持器から抜け落ちる可能性がある。 It should be noted here that the pocket gap Gp is preferably 90% to 97% of the roller diameter φr. If the pocket gap Gp is less than 90% of the roller diameter φr, there is a risk that the pitch circle PCD will deviate from the overlap region Rb toward the outer diameter side. If it exceeds 97%, there is a risk that the rollers will fall out of the cage due to shock during handling, etc.
図４を参照して、保持器１２はシェル外輪２１が装着される。シェル外輪２１は、深絞り加工等によって平坦な円板から円筒状に曲げ作成されるプレス外輪であり、円筒部２２と、１対の鍔部２３，２４を有する。鍔部２３，２４は、円筒部２２の軸方向両端に形成される内向きフランジであり、鍔部２３，２４の内径寸法は保持器１２の外径寸法よりも小さい。保持器１２は鍔部２３，２４間に配置される。鍔部２３，２４は、保持器１２のリング部１３に軸方向に当接して、保持器１２の軸方向移動を鍔部２３，２４間に規制する。これにより保持器１２はシェル外輪２１に分離不能に組み込まれる。なお鍔部２４は、鍔部２３よりも薄肉である。 Referring to FIG. 4, the retainer 12 is fitted with a shell outer ring 21. The shell outer ring 21 is a pressed outer ring formed by bending a flat disc into a cylindrical shape by deep drawing or the like, and has a cylindrical portion 22 and a pair of flanges 23, 24. The flanges 23, 24 are inward flanges formed on both axial ends of the cylindrical portion 22, and the inner diameters of the flanges 23, 24 are smaller than the outer diameter of the retainer 12. The retainer 12 is disposed between the flanges 23, 24. The flanges 23, 24 abut against the ring portion 13 of the retainer 12 in the axial direction, restricting the axial movement of the retainer 12 between the flanges 23, 24. As a result, the retainer 12 is assembled inseparably into the shell outer ring 21. The flanges 24 are thinner than the flanges 23.
円筒部２２は、保持器１２の外周を包囲し、ころ１１が転動する外側軌道面２２ｗを構成する。そしてころ１１は、シェル外輪２１により、ポケット１５から外径側へ抜け落ちることを防止される。 The cylindrical portion 22 surrounds the outer periphery of the cage 12 and forms the outer raceway surface 22w on which the rollers 11 roll. The rollers 11 are prevented from falling out of the pockets 15 to the outer diameter side by the shell outer ring 21.
図４に示す実施形態をシェル形針状ころ軸受という。保持器１２の中心孔には、図示しないシャフトが通される。シャフトの外周面は、ころ１１が転動する内側軌道面を構成する。 The embodiment shown in Figure 4 is called a drawn cup needle roller bearing. A shaft (not shown) passes through the central hole of the cage 12. The outer peripheral surface of the shaft forms the inner raceway surface on which the rollers 11 roll.
図３中、保持器１２はピッチ円ＰＣＤからみて紙面上方Ｕへ偏っている場合で表される。紙面最上部のころ１１は、紙面下方Ｄに落ち込み、周方向両側から、ポケット１５を挟んで向き合う軸方向中央部分１７，１７に挟まれる。保持器１２はころ案内とされ、外側軌道面および内側軌道面と接触しない。あるいは図示はしなかったが、保持器１２は外輪案内とされ、内側軌道面と接触しないものであってもよい。あるいは図示はしなかったが、保持器１２は内輪案内か軸案内とされ、外側軌道面と接触しないものであってもよい。 In FIG. 3, the retainer 12 is shown as being biased toward the upper U on the paper as viewed from the pitch circle PCD. The rollers 11 at the top of the paper drop to the lower D on the paper and are sandwiched between axially central portions 17, 17 that face each other on both circumferential sides with a pocket 15 in between. The retainer 12 is roller guided and does not contact the outer raceway surface or the inner raceway surface. Alternatively, although not shown, the retainer 12 may be outer ring guided and does not contact the inner raceway surface. Alternatively, although not shown, the retainer 12 may be inner ring guided or shaft guided and does not contact the outer raceway surface.
図３に示すように保持器１２が最も偏った箇所（最上部および最下部）で、ピッチ円ＰＣＤは重複領域Ｒｂと交差する。また図示はしなかったが保持器１２の偏りが少ない箇所でも、ピッチ円ＰＣＤは重複領域Ｒｂと交差する。保持器１２の中立位置でも、ピッチ円ＰＣＤは重複領域Ｒｂと交差する。 As shown in FIG. 3, the pitch circle PCD intersects with the overlap region Rb at the points where the cage 12 is most biased (at the top and bottom). Although not shown, the pitch circle PCD also intersects with the overlap region Rb at points where the cage 12 is least biased. The pitch circle PCD also intersects with the overlap region Rb at the neutral position of the cage 12.
図３中、ころ１１の自転方向Ｔと、ころ１１の公転方向Ｂをそれぞれ矢で表す。各ころ１１の転動面は、少なくとも公転方向Ｂ側の重複領域Ｒｂと当接する。 In FIG. 3, the rotation direction T of the roller 11 and the revolution direction B of the roller 11 are represented by arrows. The rolling surface of each roller 11 abuts at least the overlap region Rb on the revolution direction B side.
図２に示す本実施形態の針状ころ軸受と、図７に示す従来のＶ形保持器を備える針状ころ軸受について、対比実験を行った。対比実験は、有限要素法によるＦＥＭ解析に基づく。本実施形態のＶ形保持器の径方向段差Ｒｄ＝０．４Ｔｐ（重複率６０％）であるのに対し、従来のＶ形保持器は重複率０％である。保持器の形状以外の条件は共通する。ころのピッチ円ＰＣＤはともに１８[mm]であり、負荷荷重は１００[N]である。 A comparative experiment was conducted between the needle roller bearing of this embodiment shown in Figure 2 and a needle roller bearing equipped with a conventional V-shaped retainer shown in Figure 7. The comparative experiment was based on FEM analysis using the finite element method. The radial step Rd of the V-shaped retainer of this embodiment is 0.4Tp (overlap rate 60%), while the conventional V-shaped retainer has an overlap rate of 0%. All conditions are the same except for the shape of the retainer. The roller pitch circle PCD is 18 [mm] for both, and the load is 100 [N].
対比実験の結果、本実施形態のＶ形保持器では、ポケット隅Ｒに発生する最大主応力＝２５３．７６[MPa]であった。これに対し従来のＶ形保持器では、ポケット隅Ｒに発生する最大主応力＝３７５．２５[MPa]であった。つまり従来の保持器のポケット隅Ｒに発生する主応力を１とすると、本実施形態の保持器１２のポケット隅Ｒ（図１）に発生する主応力は０．６８であることが分かった。本実施形態のＶ形の保持器１２は、従来のＶ形保持器よりも強度が大きいことが分かった。 As a result of the comparative experiment, the maximum principal stress generated at the pocket corner R of the V-shaped retainer of this embodiment was 253.76 [MPa]. In contrast, the maximum principal stress generated at the pocket corner R of the conventional V-shaped retainer was 375.25 [MPa]. In other words, if the principal stress generated at the pocket corner R of the conventional retainer is set to 1, it was found that the principal stress generated at the pocket corner R (Figure 1) of the retainer 12 of this embodiment was 0.68. It was found that the V-shaped retainer 12 of this embodiment has greater strength than the conventional V-shaped retainer.
したがって保持器１２の軸方向寸法が従来と同じ場合に、リング部１３の軸方向幅寸法を小さくしつつ、柱部１４、ポケット１５、およびころ１１の軸方向長さを大きくして、針状ころ軸受の負荷容量を大きくすることができる。 Therefore, when the axial dimension of the cage 12 is the same as in the conventional case, the axial width dimension of the ring portion 13 can be reduced while the axial length of the column portion 14, pocket 15, and rollers 11 can be increased, thereby increasing the load capacity of the needle roller bearing.
また本実施形態の保持器１２によれば、図２に示すようにころ案内面である重複領域Ｒｂの長さが柱部１４の略全体に亘ることから、図７に示す従来の接触長さ２Ｌｃよりも大きい。したがって、ころ案内面の接触面圧は従来よりも小さくなり、PV値が下がるため、従来よりも耐摩耗性が向上する。 In addition, according to the cage 12 of this embodiment, as shown in FIG. 2, the length of the overlap region Rb, which is the roller guide surface, extends over almost the entire column portion 14, and is therefore longer than the conventional contact length 2Lc shown in FIG. 7. Therefore, the contact surface pressure of the roller guide surface is smaller than in the past, and the PV value is reduced, resulting in improved wear resistance compared to the past.
このように本実施形態の保持器は、従来のＶ形保持器と対比して、強度、耐摩耗性、負荷容量で優れる。 As such, the cage of this embodiment is superior in strength, wear resistance, and load capacity compared to conventional V-shaped cages.
次に本発明の他の実施形態を説明する。図５は本発明の他の実施形態を示す縦断面図である。他の実施形態につき、前述した実施形態と共通する構成については同一の符号を付して説明を省略し、異なる構成について以下に説明する。他の実施形態は、ソリッド型針状ころ軸受であって、前述した図４に示すシェル外輪２１を、ソリッド外輪３１に置き換えたものである。 Next, another embodiment of the present invention will be described. Figure 5 is a vertical cross-sectional view showing another embodiment of the present invention. In this other embodiment, the same components as those in the previously described embodiment are given the same reference numerals and will not be described again, and only the different components will be described below. This other embodiment is a solid type needle roller bearing in which the shell outer ring 21 shown in Figure 4 described above is replaced with a solid outer ring 31.
ソリッド外輪３１は、円筒部３２と、円筒部の両端から内径側へ突出する鍔部３３を備える。ソリッド外輪３１は、金属製の素形材を削り出すことにより形成され、前述したシェル外輪２１よりも肉厚である。 The solid outer ring 31 has a cylindrical portion 32 and flange portions 33 that protrude from both ends of the cylindrical portion toward the inner diameter side. The solid outer ring 31 is formed by cutting out a metal blank, and is thicker than the shell outer ring 21 described above.
保持器１２の外径に相当するリング部１３の外径は、鍔部３３の内径よりも小さく、１対のリング部１３の軸方向位置が１対の鍔部３３の軸方向位置と重なるよう、組み立てられる。円筒部３２の内周面は外側軌道面３２ｗを構成し、ころ１１が外側軌道面３２ｗを転動する。図５に示す実施形態では、ころ１１のピッチ円ＰＣＤが、保持器１２よりも外形側に位置し、重複領域（図２の重複領域Ｒｂを参照のこと）と交差しない。 The outer diameter of the ring portion 13, which corresponds to the outer diameter of the cage 12, is smaller than the inner diameter of the flange portion 33, and the pair of ring portions 13 are assembled so that their axial positions overlap with the axial positions of the pair of flange portions 33. The inner peripheral surface of the cylindrical portion 32 forms an outer raceway surface 32w, and the rollers 11 roll on the outer raceway surface 32w. In the embodiment shown in FIG. 5, the pitch circle PCD of the rollers 11 is located on the outer side of the cage 12 and does not intersect with the overlapping region (see overlapping region Rb in FIG. 2).
図５に示す他の実施形態も、従来のＶ形保持器と対比して、強度、耐摩耗性、負荷容量で優れる。 The other embodiment shown in Figure 5 also has superior strength, wear resistance, and load capacity compared to conventional V-shaped retainers.
次に本発明のさらに他の実施形態を説明する。図６は本発明のさらに他の実施形態を示す縦断面図である。さらに他の実施形態につき、前述した実施形態と共通する構成については同一の符号を付して説明を省略し、異なる構成について以下に説明する。さらに他の実施形態は、保持器付きころであり、図示しないハウジングの孔に組み込まれる。ハウジングの孔の内周面は、ころ１１が転動する外側軌道面を構成する。 Next, a further embodiment of the present invention will be described. Figure 6 is a vertical cross-sectional view showing a further embodiment of the present invention. In this further embodiment, the same components as those in the previously described embodiment are given the same reference numerals and will not be described again, and the different components will be described below. The further embodiment is a roller with a cage, which is incorporated into a hole in a housing (not shown). The inner peripheral surface of the hole in the housing forms the outer raceway surface on which the roller 11 rolls.
保持器１２の軸方向両端には鍔部１９，１９がそれぞれ形成される。鍔部１９は、リング部１３の軸方向外側縁と結合し、内向きに突出する。 Flanges 19, 19 are formed on both axial ends of the cage 12. The flanges 19 are connected to the axial outer edge of the ring portion 13 and protrude inward.
図６に示す他の実施形態も、従来のＶ形保持器と対比して、強度、耐摩耗性、負荷容量で優れる。しかも図６に示す保持器１２は鍔部１９を有することから、リング部１３の強度が補強され、ポケット隅Ｒの強度を大きくすることができる。したがって、柱部１４を長くして、ころ１１のころ長を大きくしたり、柱部１４，１４同士の周方向間隔を広げてころ１１のころ径を大きくしたりすることができ、針状ころ軸受の高負荷容量化に資する。 The other embodiment shown in FIG. 6 also has superior strength, wear resistance, and load capacity compared to conventional V-shaped retainers. Moreover, because the retainer 12 shown in FIG. 6 has a flange portion 19, the strength of the ring portion 13 is reinforced, and the strength of the pocket corner R can be increased. Therefore, it is possible to lengthen the column portion 14 to increase the roller length of the roller 11, or to widen the circumferential spacing between the column portions 14, 14 to increase the roller diameter of the roller 11, which contributes to a high load capacity of the needle roller bearing.
以上、図面を参照して本発明の実施の形態を説明したが、本発明は、図示した実施の形態のものに限定されない。図示した実施の形態に対して、本発明と同一の範囲内において、あるいは均等の範囲内において、種々の修正や変形を加えることが可能である。例えば上述した１の実施形態から一部の構成を抜き出し、上述した他の実施形態から他の一部の構成を抜き出し、これら抜き出された構成を組み合わせてもよい。 Although the embodiment of the present invention has been described above with reference to the drawings, the present invention is not limited to the illustrated embodiment. Various modifications and variations can be made to the illustrated embodiment within the same scope as the present invention or within an equivalent scope. For example, a portion of the configuration may be extracted from one embodiment described above, and another portion of the configuration may be extracted from another embodiment described above, and these extracted configurations may be combined.
１１ ころ、 １２ 保持器、 １３ リング部、
１４ 柱部、 １５ ポケット、 １６ 軸方向両端部分、
１７ 軸方向中央部分、 １８ ポケット壁面、
２１ シェル外輪、 ３１ ソリッド外輪。
11 roller, 12 cage, 13 ring portion,
14 pillar portion, 15 pocket, 16 axial end portions,
17 Axial center portion; 18 Pocket wall surface;
21 shell outer ring; 31 solid outer ring.
Claims (6)
前記ポケットに保持される針状ころとを備え、
前記柱部のうち軸方向両端部分が外径側に配置され、前記柱部のうち軸方向中央部分が内径側に配置され、前記軸方向両端部分および前記軸方向中央部分は前記ポケットに面するポケット壁面を有し、
前記軸方向両端部分に設けられる前記ポケット壁面のうち内径側領域と、前記軸方向中央部分に設けられる前記ポケット壁面のうち外径側領域が、径方向位置に関して重複する重複領域を構成し、
前記重複領域は、前記針状ころを案内するころ案内面を含み、
前記ころ案内面は前記柱部の一端部から他端部まで連続的に延びており、
前記軸方向両端部分および前記軸方向中央部分の径方向段差が前記軸方向中央部分の径方向肉厚の０．２倍以上０．８倍以下の範囲に含まれる、針状ころ軸受。 a cage including a pair of ring portions and a plurality of pillar portions, both ends of which are coupled to the pair of ring portions, and defining pockets between adjacent pillar portions in a circumferential direction;
A needle roller is held in the pocket,
an axial end portion of the column portion is disposed on an outer diameter side, an axial center portion of the column portion is disposed on an inner diameter side, the axial end portions and the axial center portion have pocket wall surfaces facing the pocket,
an inner diameter side region of the pocket wall surface provided at both axial end portions and an outer diameter side region of the pocket wall surface provided at the axial center portion constitute an overlapping region that overlaps with respect to a radial position,
the overlap region includes a roller guide surface that guides the needle roller,
The roller guide surface extends continuously from one end to the other end of the column portion ,
a radial step between the two axial end portions and the axial center portion is in the range of 0.2 to 0.8 times the radial thickness of the axial center portion.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020144350A JP7505941B2 (en) | 2020-08-28 | 2020-08-28 | Needle roller bearings |
| CN202180052354.9A CN115989374A (en) | 2020-08-28 | 2021-08-18 | Needle roller bearing |
| PCT/JP2021/030111 WO2022044901A1 (en) | 2020-08-28 | 2021-08-18 | Needle bearing |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020144350A JP7505941B2 (en) | 2020-08-28 | 2020-08-28 | Needle roller bearings |
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| JP2022039366A JP2022039366A (en) | 2022-03-10 |
| JP7505941B2 true JP7505941B2 (en) | 2024-06-25 |
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| JP2020144350A Active JP7505941B2 (en) | 2020-08-28 | 2020-08-28 | Needle roller bearings |
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| JP (1) | JP7505941B2 (en) |
| CN (1) | CN115989374A (en) |
| WO (1) | WO2022044901A1 (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000179555A (en) | 1998-12-17 | 2000-06-27 | Ntn Corp | Needle roller having holder, and reduction gear using it |
| JP2004084706A (en) | 2002-08-23 | 2004-03-18 | Koyo Seiko Co Ltd | Retainer for roller bearing |
| WO2006098276A1 (en) | 2005-03-14 | 2006-09-21 | Ntn Corporation | Needle roller bearing and method of producing the same |
| JP2009156388A (en) | 2007-12-27 | 2009-07-16 | Ntn Corp | Cage for roller bearing and needle roller bearing |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4408970B2 (en) * | 1998-06-05 | 2010-02-03 | Ｎｔｎ株式会社 | Needle roller bearings for swash plate compressors |
-
2020
- 2020-08-28 JP JP2020144350A patent/JP7505941B2/en active Active
-
2021
- 2021-08-18 CN CN202180052354.9A patent/CN115989374A/en active Pending
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000179555A (en) | 1998-12-17 | 2000-06-27 | Ntn Corp | Needle roller having holder, and reduction gear using it |
| JP2004084706A (en) | 2002-08-23 | 2004-03-18 | Koyo Seiko Co Ltd | Retainer for roller bearing |
| WO2006098276A1 (en) | 2005-03-14 | 2006-09-21 | Ntn Corporation | Needle roller bearing and method of producing the same |
| JP2009156388A (en) | 2007-12-27 | 2009-07-16 | Ntn Corp | Cage for roller bearing and needle roller bearing |
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| CN115989374A (en) | 2023-04-18 |
| JP2022039366A (en) | 2022-03-10 |
| WO2022044901A1 (en) | 2022-03-03 |
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