WO2022044901A1 - Needle bearing - Google Patents
Needle bearing Download PDFInfo
- Publication number
- WO2022044901A1 WO2022044901A1 PCT/JP2021/030111 JP2021030111W WO2022044901A1 WO 2022044901 A1 WO2022044901 A1 WO 2022044901A1 JP 2021030111 W JP2021030111 W JP 2021030111W WO 2022044901 A1 WO2022044901 A1 WO 2022044901A1
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- WIPO (PCT)
- Prior art keywords
- cage
- axial direction
- needle roller
- needle
- roller
- Prior art date
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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
Definitions
- the present invention relates to rolling bearings, and particularly to a cage for holding rollers.
- the shell type needle roller bearing described in Patent Document 1 and Patent Document 2 is known.
- the cage of Patent Document 1 extends straight from one end in the axial direction of the column portion to the other end in the axial direction, and the radial dimension of the entire column portion is equal to the radial thickness of the pair of ring portions. Also called.
- the cage of Patent Document 2 is also referred to as a V-shaped cage because the axially central portion of the pillar portion is arranged on the inner diameter side of both ends in the axial direction.
- the straight shape cage has a limited plate thickness because if the plate thickness is large, burrs and drool will be large. Further, since the needle-shaped roller is designed so as not to fall off from the cage, the outer diameter of the cage is made smaller than the pitch circle PCD of the needle-shaped roller. Therefore, the needle-shaped roller is guided by the outer diameter side of the pillar portion of the cage and comes into contact with the outer diameter side corner portion of the pillar portion. Not only is no oil film formed at the corners, but the corners inhibit the formation of an oil film on the rolling surface. In addition, the stress generated by the needle-shaped roller pushing the cage becomes large, so that the cage strength is inferior.
- the V-shaped cage 112 is more advantageous than the straight shape cage in that the cage is made of a thin plate and the radial thickness dimension of the entire cage can be increased.
- the V-shaped cage 112 has a pair of ring portions 113, 113 separated in the axial direction, and a plurality of pillar portions 114 connecting the ring portions 113 to each other.
- the step between the axially end portions 116 and the axially central portion 117 of the column portion 114 is formed by roll forming.
- the pitch circle PCD of the needle roller 111 intersects the axially end portions 116 corresponding to the radial outer steps.
- the axial central portion 117 corresponding to the radial inner step is arranged on the inner diameter side of the pitch circle PCD, and prevents the needle-shaped roller 111 from falling out from the pocket 115 in the radial direction.
- the needle-shaped rollers are guided by the surface of the cage. The advantage of being guided by a surface rather than a corner is that it has better oil permeability than the straight shape cage described above, and the stress generated by the roller pushing the cage is less than that of the straight shape cage.
- Patent Document 1 and Patent Document 2 are mainly used for rolling support of rotating elements of the drive system of an engine vehicle.
- the force exerted by the needle roller 111 on the V-shaped cage 112 is greater than before.
- the needle-shaped roller 111 does not abut on the axial central portion 117 that becomes the inner diameter step, and is guided only by the axial end portions 116 that become the outer diameter step, so that the needle-shaped roller 111 and the V-shaped cage 112
- the guide surface is limited to both end portions 116 in the axial direction when the pillar portions 114 of the above come into contact with each other. Then, the following problems are concerned.
- the pocket corner R is generally divided at a joint portion between the pillar portion 14 and the ring portion 13, and is cut out in an arc shape. Since it is cut out in an arc shape, the principal stress generated in the pocket corner R has been relaxed in the past. However, in the future, the principal stress generated in the pocket corner R will become a new problem for the above-mentioned reason.
- An object of the present invention is to provide a technique that can be advantageously used in a high-speed rotation environment that has never been used before.
- the needle roller bearing according to the present invention has a pair of ring portions and a plurality of column portions having both ends coupled to the pair of ring portions, and between the column portions adjacent to each other in the circumferential direction. It is provided with a cage for partitioning the pocket and a needle roller held in the pocket.
- the both ends in the axial direction of the pillar are arranged on the outer diameter side, the central portion in the axial direction of the pillar is arranged on the inner diameter side, and both ends in the axial direction and the central portion in the axial direction have a pocket wall surface facing the pocket.
- the inner diameter side region of the pocket wall surfaces provided at both end portions in the axial direction and the outer diameter side region of the pocket wall surface provided at the central portion in the axial direction form an overlapping region with respect to the radial position.
- the overlapping region includes a roller guide surface for guiding the needle-shaped roller.
- the roller guide surface has a length from one end to the other end of the pillar, so that the roller guide surface is larger than the conventional one. Therefore, the main stress generated in the pocket corner R is reduced, and the durability of the V-shaped cage is improved. Further, since the contact surface pressure (Pressure) is smaller than before, it is possible to suppress an increase in PV value even when the needle roller bearing rotates at high speed, and premature wear of the column portion is eliminated. Further, since the main stress of the pocket corner R can be reduced, it is not necessary to particularly increase the width of the ring portion. Therefore, it is possible to secure the load capacity of the needle roller bearing by keeping the roller length of the needle roller as before.
- the roller guide surface is a surface of the pocket wall surface that comes into contact with the rolling surface of the needle-shaped roller.
- the roller guide surface has a width dimension in the radial direction of the cage.
- the roller guide surface may coincide with the overlapping region or may be smaller than the overlapping region.
- the cage is allowed some eccentric movement in view of the pitch circle when the plurality of needle rollers are all in the neutral position.
- the overlapping region of the pocket wall surface intersects the pitch circle of the needle-shaped roller. According to this aspect, since the needle-shaped rollers can be guided in the tangential direction of the pitch circle, the contact surface pressure can be reduced.
- the overlapping region of the pocket wall surface may be deviated to the outer diameter side from the pitch circle of the needle-shaped roller, or may be deviated to the inner diameter side.
- the needle roller bearing of the present invention can be used together with various outer rings.
- the needle roller bearing further comprises a shell outer ring constituting the outer raceway surface on which the needle roller rolls.
- the outer ring of the shell is not welded into a cylindrical shape, but is made into a cylindrical shape by deep drawing.
- the needle roller bearing further comprises a solid outer ring constituting the outer raceway surface on which the needle roller rolls.
- the solid outer ring is formed by carving.
- the needle roller bearing may be a roller with a cage.
- the cage includes a flange portion protruding from the axial outer edge of the ring portion toward the inner diameter side. According to this aspect, the cage strength is increased and the durability is improved. Alternatively, the axial dimension of the ring portion can be reduced, and the axial dimension of the pocket and the roller length of the needle-shaped roller can be increased to increase the load capacity.
- the cage is guided by a needle-shaped roller.
- the cage is an outer ring guide guided to the outer raceway surface.
- both ends in the axial direction and the central portion in the axial direction of the pillar are cages.
- Overlapping regions overlapping in the radial direction can be provided in the pillar portion.
- the radial step at both ends in the axial direction and the central portion in the axial direction of the pillar portion is included in the range of 0.2 times or more and 0.8 times or less the radial wall thickness of the central portion in the axial direction. ..
- the upper limit value of the above-mentioned overlapping region can be set to 80%, and the lower limit value can be set to 20%.
- the present invention even when the present invention is operated at a high speed as compared with the conventional needle roller bearing, the main stress generated in the pocket corner R of the cage is reduced to reduce the main stress of the cage. Durability can be improved. In addition, the PV value is reduced and wear is reduced. Further, the load capacity of the needle roller bearing can be increased.
- FIG. 1 is a front view showing a cage according to an embodiment of the present invention, and shows a state seen from the outer diameter side.
- FIG. 2 is a vertical cross-sectional view showing a cage and a needle-shaped roller according to the same embodiment, and shows an enlarged cut surface of the cage on a plane including the axis of the cage.
- FIG. 3 is a cross-sectional view showing a cage and a needle-shaped roller according to the same embodiment, in which the cage is cut in a plane perpendicular to the axis of the cage, and the cut surface above and below the axis are cut. Take out the surface and enlarge it.
- FIGS. 2 and 2 the pockets and pillars at the top or bottom of the paper are shown, and the rest are omitted.
- the needle roller bearing of the present embodiment includes a needle roller (hereinafter, simply referred to as a roller 11) and a cage 12.
- the roller length Lr of the roller 11 is included in the range of 3 times or more and 10 times or less of the roller diameter ⁇ r (3 ⁇ r ⁇ Lr ⁇ 10 ⁇ r.
- the cage 12 has a pair of ring portions 13, 13 and a pair of both ends. Each of the ring portions 13 and 13 has a plurality of pillar portions 14 to be coupled to each other.
- the pair of ring portions 13, 13 extend in the circumferential direction of the cage 12 and are arranged at intervals in the axial direction.
- the rollers 11 partition the pockets 15 between the pillar portions 14 and 14 adjacent to each other in the circumferential direction. It is held in each pocket 15.
- the pillar portion 14 includes the axial end portions 16, 16 and the axial central portion 17. As shown in FIG. 2, both end portions 16 and 16 in the axial direction are arranged on the outer diameter side far from the axis O of the cage 12, while the central portion 17 in the axial direction is arranged on the inner diameter side close to the axis O. Therefore, the pillar portion 14 has a so-called V-shape. Therefore, the cage 12 is also referred to as a V-shaped cage.
- a strip-shaped steel plate is first prepared, then the strip-shaped steel plate is roll-formed to form a V-shaped cross section, and then a pocket 15 is formed in the strip-shaped steel plate by punching. Then, the strip-shaped steel plate is cut to a predetermined length, then the strip-shaped steel plate is rolled into a cylindrical shape, the ends are welded to each other, and then polishing is performed.
- the axial end portions 16 and 16 and the axial central portion 17 of the present embodiment are not completely displaced in the radial direction of the cage 12, but the radial positions partially overlap each other, and the rollers 11 are formed at the overlapping region Rb.
- the overlapping region Rb is displayed by hatching with a broken line.
- the inner diameter edge of the overlapping region Rb is the inner diameter surface 16d of both end portions 16 in the axial direction.
- the outer diameter edge of the overlapping region Rb is the outer diameter surface 17c of the central portion 17 in the axial direction. That is, the overlapping region Rb of this embodiment is a roller guide surface.
- Rd is smaller than the plate thickness Tp of the central portion 17 in the axial direction (Rd ⁇ Tp). More preferably, the radial step Rd is included in the range of 0.2 times or more and 0.8 times or less of the plate thickness Tp (0.2 Tp ⁇ Rd ⁇ 0.8 Tp).
- the first advantage of the V-shaped cage that is, the thinning of the plate thickness Tp and the increase of the radial thickness dimension of the cage 12.
- the second advantage of the V-shaped cage since the roller 11 is guided by the planar overlapping region Rb, lubricating oil is supplied when the roller rolling surface comes into contact with the overlapping region Rb which becomes the roller guide surface, and the needle is used. The oil permeability of roller bearings is improved. Further, since the pitch circle PCD overlaps with the overlapping region Rb, the contact surface pressure becomes small when the roller rolling surface comes into contact with the overlapping region Rb which is the roller guide surface.
- the plate thickness Tp is the plate thickness of the ring portion 13, the plate thickness of both end portions 16 in the axial direction, or the plate thickness of the central portion 17 in the axial direction. These plate thicknesses are approximately equal.
- the radial step Rd 0.2Tp
- the overlapping rate of the overlapping region Rb is 80% of the plate thickness Tp.
- the inner diameter side region of the pocket wall surface 18 belonging to both end portions 16 in the axial direction and the outer diameter side region of the pocket wall surface 18 belonging to the central portion 17 in the axial direction are overlapping regions that are roller guide surfaces.
- the circumferential distance between the pillar portions 14, 14 extending in parallel with each other is the largest between the outer diameter edges of the axial end portions 16, and the axial central portions 17, 17 The distance between them is the smallest at the inner diameter edge, and the pocket gap Gp is 97% or less of the roller diameter ⁇ r.
- the roller 11 is held in the pocket 15 and is prevented from falling out to the inner diameter side due to an impact during handling or the like.
- the pocket gap Gp is 90% or more and 97% or less of the roller diameter ⁇ r. If the pocket gap Gp is less than 90% of the roller diameter ⁇ r, the pitch circle PCD may deviate from the overlapping region Rb to the outer diameter side. If it exceeds 97%, the rollers may fall out of the cage due to impact during handling.
- the cage 12 is fitted with a shell outer ring 21.
- the shell outer ring 21 is a press outer ring formed by bending a flat disk into a cylindrical shape by deep drawing or the like, and has a cylindrical portion 22 and a pair of flange portions 23, 24.
- the flange portions 23 and 24 are inward flanges formed at both ends of the cylindrical portion 22 in the axial direction, and the inner diameter dimension of the flange portions 23 and 24 is smaller than the outer diameter dimension of the cage 12.
- the cage 12 is arranged between the flange portions 23 and 24.
- the flange portions 23, 24 abut on the ring portion 13 of the cage 12 in the axial direction, and restrict the axial movement of the cage 12 between the collar portions 23, 24.
- the collar portion 24 is thinner than the collar portion 23.
- the cylindrical portion 22 surrounds the outer circumference of the cage 12 and constitutes an outer raceway surface 22w on which the rollers 11 roll.
- the roller 11 is prevented from falling out of the pocket 15 toward the outer diameter side by the shell outer ring 21.
- FIG. 4 The embodiment shown in FIG. 4 is referred to as a shell type needle roller bearing.
- a shaft (not shown) is passed through the center hole of the cage 12.
- the outer peripheral surface of the shaft constitutes an inner raceway surface on which the rollers 11 roll.
- the cage 12 is represented by a case where the cage 12 is biased toward U above the paper surface when viewed from the pitch circle PCD.
- the roller 11 at the top of the paper surface falls to the lower side D of the paper surface, and is sandwiched between the axial central portions 17 and 17 facing each other across the pocket 15 from both sides in the circumferential direction.
- the cage 12 is a roller guide and does not come into contact with the outer raceway surface and the inner raceway surface.
- the cage 12 may be an outer ring guide and may not come into contact with the inner raceway surface.
- the cage 12 may be an inner ring guide or an axial guide and may not come into contact with the outer raceway surface.
- the pitch circle PCD intersects the overlapping region Rb at the most biased points (top and bottom) of the cage 12. Further, although not shown, the pitch circle PCD intersects the overlapping region Rb even at a position where the cage 12 is less biased. Even in the neutral position of the cage 12, the pitch circle PCD intersects the overlapping region Rb.
- 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 comes into contact with at least the overlapping region Rb on the revolution direction B side.
- a comparison experiment was conducted between the needle roller bearing of the present embodiment shown in FIG. 2 and the needle roller bearing provided with the conventional V-shaped cage shown in FIG. 7.
- the comparison experiment is based on FEM analysis by the finite element method.
- the radial step Rd 0.4 Tp (overlap rate 60%) of the V-shaped cage of the present embodiment, whereas the conventional V-shaped cage has an overlap rate of 0%.
- Conditions other than the shape of the cage are common.
- the pitch circle PCDs of the rollers are both 18 [mm], and the load is 100 [N].
- the maximum principal stress generated in the pocket corner R was 253.76 [MPa].
- the maximum principal stress generated in the pocket corner R is 375.25 [MPa]. That is, assuming that the principal stress generated in the pocket corner R of the conventional cage is 1, it was found that the principal stress generated in the pocket corner R (FIG. 1) of the cage 12 of the present embodiment is 0.68. It was found that the V-shaped cage 12 of the present embodiment has higher strength than the conventional V-shaped cage.
- the axial dimension of the cage 12 is the same as the conventional one, the axial width dimension of the ring portion 13 is reduced, and the axial length of the pillar portion 14, the pocket 15, and the roller 11 is increased to form a needle.
- the load capacity of the roller bearing can be increased.
- the conventional contact length shown in FIG. 7 It is larger than 2Lc. Therefore, the contact surface pressure of the roller guide surface becomes smaller than the conventional one, and the PV value is lowered, so that the wear resistance is improved as compared with the conventional one.
- the cage of the present embodiment is superior in strength, wear resistance, and load capacity as compared with the conventional V-shaped cage.
- FIG. 5 is a vertical sectional view showing another embodiment of the present invention.
- the configurations common to the above-described embodiments are designated by the same reference numerals and the description thereof will be omitted, and the different configurations will be described below.
- Another embodiment is a solid needle roller bearing in which the shell outer ring 21 shown in FIG. 4 described above is replaced with a solid outer ring 31.
- the solid outer ring 31 includes a cylindrical portion 32 and a flange portion 33 protruding from both ends of the cylindrical portion toward the inner diameter side.
- the solid outer ring 31 is formed by carving out a metal element, and is thicker than the shell outer ring 21 described above.
- the outer diameter of the ring portion 13 corresponding to the outer diameter of the cage 12 is smaller than the inner diameter of the flange portion 33, so that the axial position of the pair of ring portions 13 overlaps with the axial position of the pair of flange portions 33. , Assembled.
- the inner peripheral surface of the cylindrical portion 32 constitutes the outer raceway surface 32w, and the roller 11 rolls on the outer raceway surface 32w.
- the pitch circle PCD of the roller 11 is located on the outer shape side of the cage 12 and does not intersect the overlapping region (see the overlapping region Rb in FIG. 2).
- the other embodiment shown in FIG. 5 is also superior in strength, wear resistance, and load capacity as compared with the conventional V-shaped cage.
- FIG. 6 is a vertical sectional view showing still another embodiment of the present invention.
- the configurations common to those of the above-described embodiments are designated by the same reference numerals and the description thereof will be omitted, and the different configurations will be described below.
- Yet another embodiment is a roller with cage, which is incorporated into a hole in a housing (not shown). The inner peripheral surface of the hole in the housing constitutes the outer raceway surface on which the rollers 11 roll.
- the flanges 19 and 19 are formed at both ends of the cage 12 in the axial direction, respectively.
- the flange portion 19 is coupled to the axial outer edge of the ring portion 13 and projects inward.
- the other embodiment shown in FIG. 6 is also superior in strength, wear resistance, and load capacity as compared with the conventional V-shaped cage. Moreover, since the cage 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, the pillar portion 14 can be lengthened to increase the roller length of the roller 11, or the pillar portions 14 and 14 can be widened in the circumferential direction to increase the roller diameter of the roller 11. Contributes to high load capacity of bearings.
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Abstract
Both axially terminal portions (16) of a column (14) of a retainer (12) are positioned at the outside diameter; an axially central portion (17) of the column (14) is positioned at the inside diameter; the axially terminal portions (16) and the axially central portion (17) each have a pocket wall surface (18) facing a pocket (15); the regions at the inside diameter in the pocket wall surfaces (18) provided in the axially terminal portions (16), and the regions at the outside diameter in the pocket wall surface (18) provided in the axially central portion (17) constitute overlapping regions (Rb) that overlap in a radial position; the overlapping regions (Rb) include an overlapping region (Rb) that guides needle rollers (11); and the overlapping regions (Rb) intersect with the pitch circle (PCD) of the needle rollers (11).
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 particularly to a cage for holding 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 provided with a needle roller and a cage, for example, the shell type needle roller bearing described in Patent Document 1 and Patent Document 2 is known. The cage of Patent Document 1 extends straight from one end in the axial direction of the column portion to the other end in the axial direction, and the radial dimension of the entire column portion is equal to the radial thickness of the pair of ring portions. Also called. The cage of Patent Document 2 is also referred to as a V-shaped cage because the axially central portion of the pillar portion is arranged on the inner diameter side of both ends in the axial direction.
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。
The straight shape cage has a limited plate thickness because if the plate thickness is large, burrs and drool will be large. Further, since the needle-shaped roller is designed so as not to fall off from the cage, the outer diameter of the cage is made smaller than the pitch circle PCD of the needle-shaped roller. Therefore, the needle-shaped roller is guided by the outer diameter side of the pillar portion of the cage and comes into contact with the outer diameter side corner portion of the pillar portion. Not only is no oil film formed at the corners, but the corners inhibit the formation of an oil film on the rolling surface. In addition, the stress generated by the needle-shaped roller pushing the cage becomes large, so that the cage strength is inferior.
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, the conventional V-shaped cage is shown in the vertical sectional view and the front view of FIG. 7. The V-shaped cage 112 is more advantageous than the straight shape cage in that the cage is made of a thin plate and the radial thickness dimension of the entire cage can be increased. The V-shaped cage 112 has a pair of ring portions 113, 113 separated in the axial direction, and a plurality of pillar portions 114 connecting the ring portions 113 to each other. The step between the axially end portions 116 and the axially central portion 117 of the column portion 114 is formed by roll forming. The pitch circle PCD of the needle roller 111 intersects the axially end portions 116 corresponding to the radial outer steps. The axial central portion 117 corresponding to the radial inner step is arranged on the inner diameter side of the pitch circle PCD, and prevents the needle-shaped roller 111 from falling out from the pocket 115 in the radial direction. According to the V-shaped cage, the needle-shaped rollers are guided by the surface of the cage. The advantage of being guided by a surface rather than a corner is that it has better oil permeability than the straight shape cage described above, and the stress generated by the roller pushing the cage is less than that of the straight shape 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 shell type needle roller bearings of Patent Document 1 and Patent Document 2 are mainly used for rolling support of rotating elements of the drive system of an engine vehicle.
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 saving, as the gasoline-fueled engine vehicle shifts to electric vehicles and hybrid vehicles, the vehicle will be replaced from engine drive to electric motor drive. As a result, bearings for drivetrain rotating elements are often used at higher 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 exerted by the needle roller 111 on the V-shaped cage 112 is greater than before. On the other hand, the needle-shaped roller 111 does not abut on the axial central portion 117 that becomes the inner diameter step, and is guided only by the axial end portions 116 that become the outer diameter step, so that the needle-shaped roller 111 and the V-shaped cage 112 The guide surface is limited to both end portions 116 in the axial direction when the pillar portions 114 of the above come into contact with each other. Then, the following problems are concerned.
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 problem of cage strength. Since the contact between the needle roller 111 and the pillar portion 114 of the V-shaped cage 112 is limited to both ends 116 in the axial direction, the main stress generated in the pocket corner R increases, and the durability of the V-shaped cage 112 deteriorates. .. Referring to FIG. 1, the pocket corner R is generally divided at a joint portion between the pillar portion 14 and the ring portion 13, and is cut out in an arc shape. Since it is cut out in an arc shape, the principal stress generated in the pocket corner R has been relaxed in the past. However, in the future, the principal stress generated in the pocket corner R will become a new problem for the above-mentioned reason.
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 the problem of wear. When the rotation speed at which the bearing is used increases, the product (PV value) of the contact surface pressure (Pressure) and the slip speed (Velocity) generated by the needle roller 111 pushing the pillar portion 114 of the V-shaped cage 112 becomes larger. growing. Further, since the contact length Lc between the needle roller 111 and the V-shaped cage 112 is limited to the outer diameter stage, the contact surface pressure (Pressure) calculated by the pushing force F / contact length Lc becomes large. Then, there is a concern about premature wear of the pillar portion 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 a concern that the load capacity of needle roller bearings will decrease. In order to cope with the above-mentioned increase in principal stress, it is necessary to increase the width Ln of the ring portion 113. When the width Ln of the ring portion 113 is increased, the pocket axial dimension, which is the remainder of the limited circumferential dimension of the bearing, becomes smaller, the roller length of the needle roller 111 becomes smaller, and the load capacity of the needle roller bearing becomes smaller. Is disadvantageous because it becomes smaller.
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。
An object of the present invention is to provide a technique that can be advantageously used in a high-speed rotation environment that has never 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 has a pair of ring portions and a plurality of column portions having both ends coupled to the pair of ring portions, and between the column portions adjacent to each other in the circumferential direction. It is provided with a cage for partitioning the pocket and a needle roller held in the pocket. The both ends in the axial direction of the pillar are arranged on the outer diameter side, the central portion in the axial direction of the pillar is arranged on the inner diameter side, and both ends in the axial direction and the central portion in the axial direction have a pocket wall surface facing the pocket. However, the inner diameter side region of the pocket wall surfaces provided at both end portions in the axial direction and the outer diameter side region of the pocket wall surface provided at the central portion in the axial direction form an overlapping region with respect to the radial position. The overlapping region includes a roller guide surface for guiding the needle-shaped roller.
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 has a length from one end to the other end of the pillar, so that the roller guide surface is larger than the conventional one. Therefore, the main stress generated in the pocket corner R is reduced, and the durability of the V-shaped cage is improved. Further, since the contact surface pressure (Pressure) is smaller than before, it is possible to suppress an increase in PV value even when the needle roller bearing rotates at high speed, and premature wear of the column portion is eliminated. Further, since the main stress of the pocket corner R can be reduced, it is not necessary to particularly increase the width of the ring portion. Therefore, it is possible to secure the load capacity of the needle roller bearing by keeping the roller length of the needle roller as before. The roller guide surface is a surface of the pocket wall surface that comes into contact with the rolling surface of the needle-shaped 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-shaped roller can move slightly relative to 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 region or may be smaller than the overlapping region. In other words, the cage is allowed some eccentric movement in view of the pitch circle when the plurality of needle rollers are all in the neutral position. As one aspect of the present invention, the overlapping region of the pocket wall surface intersects the pitch circle of the needle-shaped roller. According to this aspect, since the needle-shaped rollers can be guided in the tangential direction of the pitch circle, the contact surface pressure can be reduced. As another aspect, the overlapping region of the pocket wall surface may be deviated to the outer diameter side from the pitch circle of the needle-shaped roller, or may be deviated to the inner diameter side.
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 together with various outer rings. As a preferred aspect of the present invention, the needle roller bearing further comprises a shell outer ring constituting the outer raceway surface on which the needle roller rolls. The outer ring of the shell is not welded into a cylindrical shape, but is made into a cylindrical shape by deep drawing. As another aspect of the present invention, the needle roller bearing further comprises a solid outer ring constituting the outer raceway surface on which the needle roller rolls. The solid outer ring is formed by carving. As 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。
As yet another aspect of the present invention, the cage includes a flange portion protruding from the axial outer edge of the ring portion toward the inner diameter side. According to this aspect, the cage strength is increased and the durability is improved. Alternatively, the axial dimension of the ring portion can be reduced, and the axial dimension of the pocket and the roller length of the needle-shaped roller can be increased to increase the load capacity.
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。
As one aspect of the present invention, the cage is guided by a needle-shaped roller. As another aspect of the present invention, the cage is an outer ring guide guided to the outer raceway surface.
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。
Since the radial step at both ends in the axial direction and the central portion in the axial direction of the pillar is less than 1.0 times the radial wall thickness of the central portion in the axial direction, both ends in the axial direction and the central portion in the axial direction are cages. Overlapping regions overlapping in the radial direction can be provided in the pillar portion. As one aspect of the present invention, the radial step at both ends in the axial direction and the central portion in the axial direction of the pillar portion is included in the range of 0.2 times or more and 0.8 times or less the radial wall thickness of the central portion in the axial direction. .. As a result, the upper limit value of the above-mentioned overlapping region can be set to 80%, and the lower limit value can be set 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, even when the present invention is operated at a high speed as compared with the conventional needle roller bearing, the main stress generated in the pocket corner R of the cage is reduced to reduce the main stress of the cage. Durability can be improved. In addition, the PV value is reduced and wear is reduced. Further, 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。
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a front view showing a cage according to an embodiment of the present invention, and shows a state seen from the outer diameter side. FIG. 2 is a vertical cross-sectional view showing a cage and a needle-shaped roller according to the same embodiment, and shows an enlarged cut surface of the cage on a plane including the axis of the cage. FIG. 3 is a cross-sectional view showing a cage and a needle-shaped roller according to the same embodiment, in which the cage is cut in a plane perpendicular to the axis of the cage, and the cut surface above and below the axis are cut. Take out the surface and enlarge it. In order to avoid complication of the figure, in FIGS. 2 and 2, the pockets and pillars at the top or bottom of the paper 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 the present embodiment includes a needle roller (hereinafter, simply referred to as a roller 11) and a cage 12. The roller length Lr of the roller 11 is included in the range of 3 times or more and 10 times or less of the roller diameter φr (3φr ≦ Lr <10φr. The cage 12 has a pair of ring portions 13, 13 and a pair of both ends. Each of the ring portions 13 and 13 has a plurality of pillar portions 14 to be coupled to each other. The pair of ring portions 13, 13 extend in the circumferential direction of the cage 12 and are arranged at intervals in the axial direction. Since the cages 12 extend in the axial direction and are arranged at equal intervals in the circumferential direction of the ring portion 13, the rollers 11 partition the pockets 15 between the pillar portions 14 and 14 adjacent to each other in the circumferential direction. It is 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 pillar portion 14 includes the axial end portions 16, 16 and the axial central portion 17. As shown in FIG. 2, both end portions 16 and 16 in the axial direction are arranged on the outer diameter side far from the axis O of the cage 12, while the central portion 17 in the axial direction is arranged on the inner diameter side close to the axis O. Therefore, the pillar portion 14 has a so-called V-shape. Therefore, the cage 12 is also referred to as 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。
Here, as a supplement to the manufacturing method of the cage 12, a strip-shaped steel plate is first prepared, then the strip-shaped steel plate is roll-formed to form a V-shaped cross section, and then a pocket 15 is formed in the strip-shaped steel plate by punching. Then, the strip-shaped steel plate is cut to a predetermined length, then the strip-shaped steel plate is rolled into a cylindrical shape, the ends are welded to each other, and then polishing is performed.
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。
The axial end portions 16 and 16 and the axial central portion 17 of the present embodiment are not completely displaced in the radial direction of the cage 12, but the radial positions partially overlap each other, and the rollers 11 are formed at the overlapping region Rb. Contact the rolling surface of. In FIG. 2, the overlapping region Rb is displayed by hatching with a broken line. The inner diameter edge of the overlapping region Rb is the inner diameter surface 16d of both end portions 16 in the axial direction. The outer diameter edge of the overlapping region Rb is the outer diameter surface 17c of the central portion 17 in the axial direction. That is, the overlapping region Rb of 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 the present embodiment, in order to obtain the overlapping region Rb, the step between the outer diameter step and the inner diameter step of the pillar portion 14, that is, the radial step between the outer diameter surface 17c of the axial end portion 16 and the outer diameter surface 16c of the axial central portion 17. Rd is smaller than the plate thickness Tp of the central portion 17 in the axial direction (Rd <Tp). More preferably, the radial step Rd is included in the range of 0.2 times or more and 0.8 times or less of the plate thickness Tp (0.2 Tp ≦ Rd ≦ 0.8 Tp). As a result, it is possible to obtain the first advantage of the V-shaped cage, that is, the thinning of the plate thickness Tp and the increase of the radial thickness dimension of the cage 12. Further, as a second advantage of the V-shaped cage, since the roller 11 is guided by the planar overlapping region Rb, lubricating oil is supplied when the roller rolling surface comes into contact with the overlapping region Rb which becomes the roller guide surface, and the needle is used. The oil permeability of roller bearings is improved. Further, since the pitch circle PCD overlaps with the overlapping region Rb, the contact surface pressure becomes small when the roller rolling surface comes into contact with the overlapping 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 cage. On the contrary, when the step is large (0.8 Tp <Rd), the overlapping region Rb is reduced (overlapping rate is less than 20%), and the pitch circle PCD may deviate from the overlapping region. The plate thickness Tp is the plate thickness of the ring portion 13, the plate thickness of both end portions 16 in the axial direction, or the plate thickness of the central portion 17 in the axial direction. 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 the present embodiment, the radial step Rd = 0.2Tp, and the overlapping rate of the overlapping 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。
Further, in the present embodiment, the inner diameter side region of the pocket wall surface 18 belonging to both end portions 16 in the axial direction and the outer diameter side region of the pocket wall surface 18 belonging to the central portion 17 in the axial direction are overlapping regions that are roller guide surfaces. Includes Rb.
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。
With reference to FIG. 3, in the pocket wall surfaces 18, 18, the circumferential distance between the pillar portions 14, 14 extending in parallel with each other is the largest between the outer diameter edges of the axial end portions 16, and the axial central portions 17, 17 The distance between them is the smallest at the inner diameter edge, and the pocket gap Gp is 97% or less of the roller diameter φr. As a result, the roller 11 is held in the pocket 15 and is prevented from falling out to the inner diameter side due to an impact during handling or the like.
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 is preferable that the pocket gap Gp is 90% or more and 97% or less of the roller diameter φr. If the pocket gap Gp is less than 90% of the roller diameter φr, the pitch circle PCD may deviate from the overlapping region Rb to the outer diameter side. If it exceeds 97%, the rollers may fall out of the cage due to impact during handling.
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。
With reference to FIG. 4, the cage 12 is fitted with a shell outer ring 21. The shell outer ring 21 is a press outer ring formed by bending a flat disk into a cylindrical shape by deep drawing or the like, and has a cylindrical portion 22 and a pair of flange portions 23, 24. The flange portions 23 and 24 are inward flanges formed at both ends of the cylindrical portion 22 in the axial direction, and the inner diameter dimension of the flange portions 23 and 24 is smaller than the outer diameter dimension of the cage 12. The cage 12 is arranged between the flange portions 23 and 24. The flange portions 23, 24 abut on the ring portion 13 of the cage 12 in the axial direction, and restrict the axial movement of the cage 12 between the collar portions 23, 24. As a result, the cage 12 is inseparably incorporated into the shell outer ring 21. The collar portion 24 is thinner than the collar portion 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 circumference of the cage 12 and constitutes an outer raceway surface 22w on which the rollers 11 roll. The roller 11 is prevented from falling out of the pocket 15 toward 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 FIG. 4 is referred to as a shell type needle roller bearing. A shaft (not shown) is passed through the center hole of the cage 12. The outer peripheral surface of the shaft constitutes an 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 cage 12 is represented by a case where the cage 12 is biased toward U above the paper surface when viewed from the pitch circle PCD. The roller 11 at the top of the paper surface falls to the lower side D of the paper surface, and is sandwiched between the axial central portions 17 and 17 facing each other across the pocket 15 from both sides in the circumferential direction. The cage 12 is a roller guide and does not come into contact with the outer raceway surface and the inner raceway surface. Alternatively, although not shown, the cage 12 may be an outer ring guide and may not come into contact with the inner raceway surface. Alternatively, although not shown, the cage 12 may be an inner ring guide or an axial guide and may not come into contact with 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 the overlapping region Rb at the most biased points (top and bottom) of the cage 12. Further, although not shown, the pitch circle PCD intersects the overlapping region Rb even at a position where the cage 12 is less biased. Even in the neutral position of the cage 12, the pitch circle PCD intersects the overlapping region Rb.
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 comes into contact with at least the overlapping 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 comparison experiment was conducted between the needle roller bearing of the present embodiment shown in FIG. 2 and the needle roller bearing provided with the conventional V-shaped cage shown in FIG. 7. The comparison experiment is based on FEM analysis by the finite element method. The radial step Rd = 0.4 Tp (overlap rate 60%) of the V-shaped cage of the present embodiment, whereas the conventional V-shaped cage has an overlap rate of 0%. Conditions other than the shape of the cage are common. The pitch circle PCDs of the rollers are both 18 [mm], 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 comparison experiment, in the V-shaped cage of this embodiment, the maximum principal stress generated in the pocket corner R was 253.76 [MPa]. On the other hand, in the conventional V-shaped cage, the maximum principal stress generated in the pocket corner R is 375.25 [MPa]. That is, assuming that the principal stress generated in the pocket corner R of the conventional cage is 1, it was found that the principal stress generated in the pocket corner R (FIG. 1) of the cage 12 of the present embodiment is 0.68. It was found that the V-shaped cage 12 of the present embodiment has higher strength than the conventional V-shaped cage.
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 the conventional one, the axial width dimension of the ring portion 13 is reduced, and the axial length of the pillar portion 14, the pocket 15, and the roller 11 is increased to form a needle. The load capacity of the roller bearing can be increased.
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。
Further, according to the cage 12 of the present embodiment, as shown in FIG. 2, since the length of the overlapping region Rb which is the roller guide surface extends over substantially the entire pillar portion 14, the conventional contact length shown in FIG. 7 It is larger than 2Lc. Therefore, the contact surface pressure of the roller guide surface becomes smaller than the conventional one, and the PV value is lowered, so that the wear resistance is improved as compared with the conventional one.
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 described above, the cage of the present embodiment is superior in strength, wear resistance, and load capacity as compared with the conventional V-shaped cage.
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. FIG. 5 is a vertical sectional view showing another embodiment of the present invention. Regarding the other embodiments, the configurations common to the above-described embodiments are designated by the same reference numerals and the description thereof will be omitted, and the different configurations will be described below. Another embodiment is a solid needle roller bearing in which the shell outer ring 21 shown in FIG. 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 includes a cylindrical portion 32 and a flange portion 33 protruding from both ends of the cylindrical portion toward the inner diameter side. The solid outer ring 31 is formed by carving out a metal element, 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 corresponding to the outer diameter of the cage 12 is smaller than the inner diameter of the flange portion 33, so that the axial position of the pair of ring portions 13 overlaps with the axial position of the pair of flange portions 33. , Assembled. The inner peripheral surface of the cylindrical portion 32 constitutes the outer raceway surface 32w, and the roller 11 rolls on the outer raceway surface 32w. In the embodiment shown in FIG. 5, the pitch circle PCD of the roller 11 is located on the outer shape side of the cage 12 and does not intersect the overlapping region (see the 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 FIG. 5 is also superior in strength, wear resistance, and load capacity as compared with the conventional V-shaped cage.
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, still another embodiment of the present invention will be described. FIG. 6 is a vertical sectional view showing still another embodiment of the present invention. Further, with respect to the other embodiments, the configurations common to those of the above-described embodiments are designated by the same reference numerals and the description thereof will be omitted, and the different configurations will be described below. Yet another embodiment is a roller with cage, which is incorporated into a hole in a housing (not shown). The inner peripheral surface of the hole in the housing constitutes the outer raceway surface on which the rollers 11 roll.
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。
The flanges 19 and 19 are formed at both ends of the cage 12 in the axial direction, respectively. The flange portion 19 is coupled to the axial outer edge of the ring portion 13 and projects 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 is also superior in strength, wear resistance, and load capacity as compared with the conventional V-shaped cage. Moreover, since the cage 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, the pillar portion 14 can be lengthened to increase the roller length of the roller 11, or the pillar portions 14 and 14 can be widened in the circumferential direction to increase the roller diameter of the roller 11. Contributes to high load capacity of bearings.
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 embodiments of the present invention have been described above with reference to the drawings, the present invention is not limited to those of the illustrated embodiments. Various modifications and modifications can be made to the illustrated embodiment within the same range as the present invention or within the same range. For example, a part of the configurations may be extracted from the above-mentioned one embodiment, another part of the configurations may be extracted from the above-mentioned other embodiments, 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。 Around 11, 12 cage, 13 ring part,
14 pillars, 15 pockets, 16 axial ends,
17 Axial center, 18 Pocket wall,
21 Shell outer ring, 31 Solid outer ring.
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。 Around 11, 12 cage, 13 ring part,
14 pillars, 15 pockets, 16 axial ends,
17 Axial center, 18 Pocket wall,
21 Shell outer ring, 31 Solid outer ring.
Claims (7)
- 1対のリング部、および両端が前記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、周方向で隣り合う前記柱部同士間にポケットを区画する保持器と、
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む、針状ころ軸受。 A cage having a pair of ring portions and a plurality of pillar portions having both ends connected to the pair of ring portions, and partitioning pockets between the pillar portions adjacent to each other in the circumferential direction.
With a needle-shaped roller held in the pocket,
Both ends in the axial direction of the pillar are arranged on the outer diameter side, the central portion in the axial direction of the pillar is arranged on the inner diameter side, and both ends in the axial direction and the central portion in the axial direction face the pocket. Has a pocket wall,
The inner diameter side region of the pocket wall surface provided at both end portions in the axial direction and the outer diameter side region of the pocket wall surface provided at the central portion in the axial direction form an overlapping region with respect to the radial position.
The overlapping region is a needle roller bearing including a roller guide surface that guides the needle roller. - 前記重複領域は、前記針状ころのピッチ円と交差する、請求項1に記載の針状ころ軸受。 The needle roller bearing according to claim 1, wherein the overlapping region intersects the pitch circle of the needle roller.
- 前記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、請求項1または2に記載の針状ころ軸受。 The needle roller bearing according to claim 1 or 2, further comprising a shell outer ring constituting the outer raceway surface on which the needle roller rolls.
- 前記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、請求項1または2に記載の針状ころ軸受。 The needle roller bearing according to claim 1 or 2, further comprising a solid outer ring constituting the outer raceway surface on which the needle roller rolls.
- 前記リング部は、前記柱部の前記両端部分から内径側へ突出する鍔部を含む、請求項1または2に記載の針状ころ軸受。 The needle roller bearing according to claim 1 or 2, wherein the ring portion includes a flange portion protruding from both end portions of the pillar portion toward the inner diameter side.
- 前記保持器は針状ころに案内されるころ案内とされる、請求項1~5のいずれかに記載の針状ころ軸受。 The needle roller bearing according to any one of claims 1 to 5, wherein the cage is a roller guide guided by a needle roller.
- 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、請求項1~6のいずれかに記載の針状ころ軸受。 Any of claims 1 to 6, wherein the radial steps at both ends in the axial direction and the central portion in the axial direction are included in a range of 0.2 times or more and 0.8 times or less the radial wall thickness of the central portion in the axial direction. Needle roller bearing described in the direction.
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH11351145A (en) * | 1998-06-05 | 1999-12-21 | Ntn Corp | Needle roller bearing for swash plate compressor |
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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Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11351145A (en) * | 1998-06-05 | 1999-12-21 | Ntn Corp | Needle roller bearing for swash plate compressor |
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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