JP2012241828A - Tapered roller bearing - Google Patents

Tapered roller bearing Download PDF

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Publication number
JP2012241828A
JP2012241828A JP2011113646A JP2011113646A JP2012241828A JP 2012241828 A JP2012241828 A JP 2012241828A JP 2011113646 A JP2011113646 A JP 2011113646A JP 2011113646 A JP2011113646 A JP 2011113646A JP 2012241828 A JP2012241828 A JP 2012241828A
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Japan
Prior art keywords
diameter side
tapered roller
inner ring
outer ring
side flange
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JP2011113646A
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Japanese (ja)
Inventor
Akiyuki Suzuki
章之 鈴木
Hiroshi Jo
宏 城
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JTEKT Corp
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JTEKT Corp
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Priority to JP2011113646A priority Critical patent/JP2012241828A/en
Publication of JP2012241828A publication Critical patent/JP2012241828A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
    • F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
    • F16C33/4676—Details of individual pockets, e.g. shape or roller retaining means of the stays separating adjacent cage pockets, e.g. guide means for the bearing-surface of the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
    • F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
    • 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements

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

Abstract

PROBLEM TO BE SOLVED: To prevent seizure at a slide contact portion between a large-diameter side flange surface of an inner race and a tapered roller bearing.SOLUTION: In the tapered roller bearing, raceways 12 and 22 are formed at an outer race 11 and an inner race 20. In the inner race 20, a small-diameter side flange part 23 is formed on one of both axial sides of the raceway 22, and a large-diameter side flange part 24 is formed on the other. The space formed between the outer race 11 and the inner race 20 serves as an oil flow path in which a lubricant flows from the small-diameter side flange part 23 of the inner race 20 to the large-diameter side flange part 24. A holder 30 located on the small-diameter side flange part 23 side of the inner race 20 is located apart from the outer race 11 toward an inner diameter side, to form an oil introducing space 38 between the outer race 11 and the holder 30. An axial middle portion of the holder 30 is swollen to an outer diameter side, to form a swollen part 60. A constriction 39 for constricting the oil flow path is formed between the raceway 12 of the outer race 11 and the swollen part 60. An oil introducing passage 32 which introduces a lubricant in the oil introducing space 38 to an oil flow path between the holder 30 and the inner race 20, is formed in the holder 30 positioned before the constriction 39.

Description

本発明は、外輪および内輪間に複数の円すいころと保持器を配置した円すいころ軸受に関する。   The present invention relates to a tapered roller bearing in which a plurality of tapered rollers and a cage are arranged between an outer ring and an inner ring.

図４および図５（特許文献１）に示すように、円すいころ軸受１００は、外輪１１０、内輪１２０、円すいころ１４０、保持器１３０とからなり、内輪１２０の大径側鍔部１２１の大径側内側端面１２２と、円すいころ１４０の大径側端面１４１とが滑り接触し、この箇所の焼付き防止のために、矢印１５０、１５１で示すように、内輪１２０の小径側鍔部１２３側から大径側鍔部１２１へ、潤滑油を積極的に流している。また、前記保持器１３０には、円すいころ１４０を転動可能に保持するポケット１３１が円周方向に等間隔に形成され、さらに各ポケット１３０の円周方向の両側に油対流用切欠き１３２が形成されているが、この油対流用切欠き１３２は、矢印１５０に示す、外輪１１０側、内輪１２０側、外輪１１０側の順に流れる流れと、矢印１５１に示す、内輪１２０側、外輪１１０側の順に流れる流れを引き起こすために設けたものであって、内輪１２０の大径側鍔部１２１の大径側内側端面１２２へ供給される潤滑油を増やすために設けたものでない。   As shown in FIGS. 4 and 5 (Patent Document 1), the tapered roller bearing 100 includes an outer ring 110, an inner ring 120, a tapered roller 140, and a cage 130, and the large diameter side flange 121 of the inner ring 120 has a large diameter. The side inner end surface 122 and the large-diameter side end surface 141 of the tapered roller 140 are in sliding contact with each other, and, as shown by arrows 150 and 151, from the small-diameter side flange 123 side of the inner ring 120, in order to prevent seizure at this location. Lubricating oil is actively flowing to the large-diameter side flange 121. Further, pockets 131 for holding the tapered rollers 140 to be rollable are formed in the retainer 130 at equal intervals in the circumferential direction, and further, oil convection notches 132 are provided on both sides of each pocket 130 in the circumferential direction. The oil convection notch 132 is formed on the outer ring 110 side, the inner ring 120 side, and the outer ring 110 side in the order indicated by an arrow 150, and on the inner ring 120 side and the outer ring 110 side indicated by an arrow 151. It is provided to cause a flow that flows in order, and is not provided to increase the lubricating oil supplied to the large diameter side inner end surface 122 of the large diameter side flange 121 of the inner ring 120.

特開平９−３２８５８号公報JP-A-9-32858

このため、自動車の発進時等で車速が低いときは、内輪１２０の小径側鍔部１２３側から大径側鍔部１２１へ流れる潤滑油の全体流量が少なく、内輪１２０の大径側鍔部１２１の大径側内側端面１２２と、円すいころ１４０の大径側端面１４１とが滑り接触する箇所に焼き付きが発生しやすい。本発明は上述した問題点を解決するためになされたもので、その目的は、内輪１２０の大径側鍔部１２１の大径側内側端面１２２と、円すいころ１４０の大径側端面１４１とが滑り接触する箇所の焼き付きを防止する。   For this reason, when the vehicle speed is low, such as when the vehicle starts, the overall flow rate of the lubricating oil flowing from the small diameter side flange 123 side of the inner ring 120 to the large diameter side flange 121 is small, and the large diameter side flange 121 of the inner ring 120 is small. The large-diameter side inner end surface 122 and the large-diameter side end surface 141 of the tapered roller 140 are likely to be seized. The present invention has been made to solve the above-described problems. The purpose of the present invention is to provide a large-diameter inner end surface 122 of the large-diameter side flange 121 of the inner ring 120 and a large-diameter side end surface 141 of the tapered roller 140. Prevent seizure at the point of sliding contact.

請求項１に記載の発明は、外輪と、前記外輪の内周側に配置される内輪と、前記外輪および前記内輪間に配置され円周上等間隔に複数のポケットを有する保持器と、前記ポケットに配置される複数の円すいころとからなり、前記外輪の内周および前記内輪の外周に前記円すいころが転動する軌道面を形成し、前記内輪に前記軌道面の軸方向両側の一方に小径側鍔部を、他方に大径側鍔部を形成し、この大径側鍔部に前記円すいころが滑り接触する大径側端面を形成し、前記外輪および前記内輪間にできる空間が、前記内輪の小径側鍔部から大径側鍔部へ潤滑油が流れる油流路とされている円すいころ軸受において、前記内輪の前記小径側鍔部側にある前記保持器を、前記外輪に対し内径側へ離して設けることにより、前記外輪および前記保持器間に油導入空間を形成し、前記保持器の軸方向中間を外径側へ膨らませて膨らみ部を形成し、前記外輪の軌道面および前記膨らみ部間に前記油流路を絞る絞りを形成し、この絞り前の前記保持器に、前記油導入空間の潤滑油を前記保持器および前記内輪間の油流路へ導く油導入通路を形成したものである。   The invention according to claim 1 is an outer ring, an inner ring disposed on an inner circumferential side of the outer ring, a cage disposed between the outer ring and the inner ring and having a plurality of pockets at equal intervals on the circumference, A plurality of tapered rollers disposed in a pocket, and a raceway surface on which the tapered rollers roll is formed on an inner periphery of the outer ring and an outer periphery of the inner ring, and the inner ring is provided on one of both axial sides of the raceway surface. A small-diameter side collar is formed on the other side, a large-diameter side collar is formed on the other side, a large-diameter side end surface is formed on the large-diameter side collar and the tapered roller is in sliding contact, and a space formed between the outer ring and the inner ring is formed. In the tapered roller bearing in which the lubricating oil flows from the small-diameter side collar of the inner ring to the large-diameter side collar, the retainer on the small-diameter side collar of the inner ring is connected to the outer ring. By providing the inner ring away from the outer ring, the outer ring and the holding An oil introduction space is formed in between, the middle in the axial direction of the cage is bulged to the outer diameter side to form a bulge portion, and a throttle for narrowing the oil flow path is formed between the raceway surface of the outer ring and the bulge portion. The retainer before throttling is formed with an oil introduction passage for guiding the lubricating oil in the oil introduction space to the oil passage between the retainer and the inner ring.

本発明によれば、油導入空間へ導かれた潤滑油が、油導入通路を経て保持器および内輪間の油流路へ導かれ、内輪の大径側鍔部の大径側端面へ供給される潤滑油が増えるので、内輪の大径側鍔部の大径側端面と、円すいころの大径側端面とが滑り接触する箇所の焼き付きを防止できる。   According to the present invention, the lubricating oil guided to the oil introduction space is guided to the oil flow path between the retainer and the inner ring through the oil introduction passage, and is supplied to the large diameter side end surface of the large diameter side flange of the inner ring. Therefore, seizure of a portion where the large-diameter side end surface of the large-diameter side flange of the inner ring and the large-diameter side end surface of the tapered roller are in sliding contact with each other can be prevented.

本発明の実施形態における円すいころ軸受の縦断面図である。It is a longitudinal cross-sectional view of the tapered roller bearing in the embodiment of the present invention. 本発明の実施形態における図１のＡ矢視図である。It is A arrow directional view of FIG. 1 in embodiment of this invention. 本発明の実施形態における図１のＢ方向から見た保持器の展開図である。It is an expanded view of the holder | retainer seen from the B direction of FIG. 1 in embodiment of this invention. 従来における円すいころ軸受の縦断面図である。It is a longitudinal cross-sectional view of the conventional tapered roller bearing. 従来における保持器の外観図である。It is an external view of the conventional retainer.

本発明の一実施形態について、図１乃至図３を参酌しつつ説明する。図１は、円すいころ軸受の縦断面図であり、図２は、図１のＡ矢視図であり、図３は、図１のＢ方向から見た保持器の展開図である。   An embodiment of the present invention will be described with reference to FIGS. 1 to 3. FIG. 1 is a longitudinal sectional view of a tapered roller bearing, FIG. 2 is a view taken in the direction of arrow A in FIG. 1, and FIG. 3 is a developed view of the cage as viewed from the direction B in FIG.

図１乃至図２に示すように、円すいころ軸受１０は、リング状の外輪１１と、外輪１１の内周側に配置されるリング状の内輪２０と、外輪１１と内輪２０間に配置されるリング状の保持器３０と、保持器３０に保持される複数の円すいころ４０とからなっている。外輪１１、内輪２０、保持器３０、円すいころ４０は、いずれも金属製の材料で構成され、特に鉄系の材料がよく使われる。   As shown in FIGS. 1 and 2, the tapered roller bearing 10 is disposed between a ring-shaped outer ring 11, a ring-shaped inner ring 20 disposed on the inner peripheral side of the outer ring 11, and the outer ring 11 and the inner ring 20. It consists of a ring-shaped cage 30 and a plurality of tapered rollers 40 held by the cage 30. The outer ring 11, the inner ring 20, the retainer 30, and the tapered roller 40 are all made of a metal material, and particularly iron-based materials are often used.

前記外輪１１の内周には、外輪１１の軸線に対して傾斜した外輪側軌道面１２が形成されている。前記内輪２０の外周には、内輪２０の軸線に対して傾斜した内輪側軌道面２２が形成されている。内輪側軌道面２２の軸方向両側の一方に外径方向へ突出した小径側鍔部２３が形成され、他方に外径方向へ突出した大径側鍔部２４が形成されている。小径側鍔部２３の円すいころ４０側の端面には、円すいころ４０の後述する小径側端面４２に滑り接触する小径側内側端面２３ａが形成されている。大径側鍔部２４の円すいころ４０側の端面には、円すいころ４０の後述する大径側端面４３に滑り接触する大径側内側端面２４ａが形成されている。   On the inner periphery of the outer ring 11, an outer ring side raceway surface 12 that is inclined with respect to the axis of the outer ring 11 is formed. On the outer periphery of the inner ring 20, an inner ring side raceway surface 22 that is inclined with respect to the axis of the inner ring 20 is formed. A small-diameter side flange 23 projecting in the outer diameter direction is formed on one of both axial sides of the inner ring side raceway surface 22, and a large-diameter side collar 24 projecting in the outer diameter direction is formed on the other side. A small-diameter inner end surface 23a is formed on the end surface on the tapered roller 40 side of the small-diameter side flange 23 so as to be in sliding contact with a small-diameter side end surface 42 described later of the tapered roller 40. A large-diameter inner end surface 24a that slides into contact with a large-diameter side end surface 43 (to be described later) of the tapered roller 40 is formed on the end surface of the large-diameter flange 24 on the tapered roller 40 side.

図１および図３に示すように、前記保持器３０は、円周方向に等間隔にポケット３１が形成され、各ポケット３１の円周方向両側に油導入通路３２が形成されている。保持器３０は、軸方向の４箇所で折れ曲がり成形され、1番目の折れ曲がりまでの折れ曲がり部３３と、１番目の折れ曲がりから２番目の折れ曲がりまでの第１の案内部３４と、２番目の折れ曲がりから３番目の折れ曲がりまでの傾斜部３５と、３番目の折れ曲がりから４番目の折れ曲がりまでの平行部３６と、４番目の折れ曲がり以降の第２の案内部３７とからなっている。折れ曲がり部３３は、保持器３０の軸線に対しほぼ直角な方向に延びており、第１の案内部３４は、円すいころ４０の軸線に対して緩やかな傾斜を有する。傾斜部３５は、保持器３０の軸線に対し直角に近い角度で持って傾斜しており、平行部３６は、外輪側軌道面１２と平行な方向に延びており、第２の案内部３７は、保持器３０の軸線と平行な方向に延びている。   As shown in FIGS. 1 and 3, the retainer 30 has pockets 31 formed at equal intervals in the circumferential direction, and oil introduction passages 32 are formed on both sides of each pocket 31 in the circumferential direction. The cage 30 is bent and formed at four locations in the axial direction. From the first bent portion 33 to the first bent portion, the first guide portion 34 from the first bent portion to the second bent portion, and the second bent portion. It comprises an inclined portion 35 up to the third bend, a parallel portion 36 from the third bend to the fourth bend, and a second guide portion 37 after the fourth bend. The bent portion 33 extends in a direction substantially perpendicular to the axis of the cage 30, and the first guide portion 34 has a gentle inclination with respect to the axis of the tapered roller 40. The inclined portion 35 is inclined at an angle close to a right angle with respect to the axis of the cage 30, the parallel portion 36 extends in a direction parallel to the outer ring side raceway surface 12, and the second guide portion 37 is , Extending in a direction parallel to the axis of the cage 30.

折れ曲がり部３３は、第１の案内部３４に対して内輪２０側へ折れ曲がっており、第１の案内部３４は、円すいころ４０の軸線とほぼ同軸線上にある。このように、第１の案内部３４は、外輪側軌道面１２に対し内径方向に離れた位置にあるので、外輪１１および第１の案内部３４間に油導入空間３８が形成されている。平行部３６は、外輪側軌道面１２に最も接近した位置にあり、外輪側軌道面１２および平行部３６間に潤滑油の流れを絞る絞り３９が形成されている。傾斜部３５の全域、平行部３６の全域、第２の案内部３７の大半により、保持器３０を外輪１１側へ膨らませた膨らみ部６０が形成される。   The bent portion 33 is bent toward the inner ring 20 with respect to the first guide portion 34, and the first guide portion 34 is substantially coaxial with the axis of the tapered roller 40. Thus, the first guide portion 34 is located away from the outer ring-side raceway surface 12 in the inner diameter direction, so that an oil introduction space 38 is formed between the outer ring 11 and the first guide portion 34. The parallel portion 36 is at a position closest to the outer ring side raceway surface 12, and a throttle 39 for restricting the flow of the lubricating oil is formed between the outer ring side raceway surface 12 and the parallel portion 36. A bulging portion 60 that bulges the cage 30 toward the outer ring 11 is formed by the entire area of the inclined portion 35, the entire area of the parallel portion 36, and most of the second guide portion 37.

外輪１１および内輪２０間の空間が、小径側鍔部２３から大径側鍔部２４へ潤滑油が流れる油流路となっている。つまり、外輪１１および保持器３０間の空間も油流路の一つであり、保持器３０および内輪２０間の空間も油流路の一つである。油導入通路３２は、一部の第１の案内部３４、傾斜部３５の全域、一部の平行部３６に渡って形成され、絞り３９を通過できない大半の潤滑油を保持器３０および内輪２０間の油流路へ導く役割を持つ。   The space between the outer ring 11 and the inner ring 20 serves as an oil passage through which lubricating oil flows from the small diameter side flange 23 to the large diameter side flange 24. That is, the space between the outer ring 11 and the cage 30 is also one of the oil channels, and the space between the cage 30 and the inner ring 20 is also one of the oil channels. The oil introduction passage 32 is formed across a part of the first guide part 34, the entire region of the inclined part 35, and a part of the parallel part 36. It has a role to lead to the oil passage between.

ポケット３１は、第１の案内部３４の大半、傾斜部３５の全域、平行部３６の全域、第２の案内部３７の大半に渡って形成されている。ポケット３１を形成することによって、保持器３０は、小径側鍔部２３側で円周方向に繋がる第１の環状部と、大径側鍔部２４側で円周方向に繋がる第２の環状部と、第１の環状部および第２の環状部を軸方向に連結する柱部とに分けられる。第１の環状部は、折れ曲がり部３３の全域と、一部の第１の案内部３４で構成される。第２の環状部は、一部の第２の案内部３７で構成される。保持器３０は、板状の金属板からプレスによって、切り抜き、折り曲げ等により製作される。   The pocket 31 is formed over most of the first guide portion 34, the entire region of the inclined portion 35, the entire region of the parallel portion 36, and most of the second guide portion 37. By forming the pocket 31, the retainer 30 has a first annular portion connected in the circumferential direction on the small diameter side flange portion 23 side and a second annular portion connected in the circumferential direction on the large diameter side flange portion 24 side. And a pillar part that connects the first annular part and the second annular part in the axial direction. The first annular portion includes the entire bent portion 33 and a part of the first guide portion 34. The second annular portion includes a part of the second guide portion 37. The retainer 30 is manufactured from a plate-like metal plate by pressing, bending, or the like.

ポケット３１は、油導入通路３２を除いた全周で、円すいころ４０に当接するような形状に加工されている。膨らみ部６０は、内輪２０、円すいころ４０、保持器３０からなるサブアッシィを、外輪１１に組み付ける際の円すいころ４０の飛び出しを防止する機能も有する。   The pocket 31 is processed into a shape that makes contact with the tapered roller 40 on the entire circumference excluding the oil introduction passage 32. The bulging portion 60 also has a function of preventing the tapered roller 40 from popping out when the sub-assembly including the inner ring 20, the tapered roller 40, and the cage 30 is assembled to the outer ring 11.

前記円すいころ４０は、円すい形状から頂部を除去した形状を有するもので、前記外輪側軌道面１２と前記内輪側軌道面２２上を転動する転動面４１と、小径側の端面に形成された小径側端面４２と、大径側の端面に形成された大径側端面４３を有する。   The tapered roller 40 has a shape obtained by removing the top from the conical shape, and is formed on the outer ring side raceway surface 12, the rolling surface 41 rolling on the inner ring side raceway surface 22, and the end surface on the small diameter side. A small-diameter side end surface 42 and a large-diameter side end surface 43 formed on the large-diameter side end surface.

続いて上述した構成にもとづいて、作用について説明する。   Next, the operation will be described based on the configuration described above.

外輪１１に対して内輪２０が回転すると、円すいころ４０は外輪側軌道面１２上と内輪側軌道面２２上を転動しながら内輪２０の回転方向と同方向に移動する。円すいころ４０の転動によって保持器３０が内輪２０と同方向に回転する。   When the inner ring 20 rotates with respect to the outer ring 11, the tapered roller 40 moves in the same direction as the rotation direction of the inner ring 20 while rolling on the outer ring side raceway surface 12 and the inner ring side raceway surface 22. The retainer 30 rotates in the same direction as the inner ring 20 by the rolling of the tapered roller 40.

内輪２０に軸方向のスラスト力が作用すると、円すいころ４０の大径側端面４３が大径側内側端面２４ａに接触し、さらに円すいころ４０を介して外輪１１に前記スラスト力が作用する。円すいころ４０の大径側端面４３および大径側内側端面２４ａ間は滑り接触しながら、前記スラスト力の一部を受け止めるため、焼付きが発生しやすい。   When axial thrust force acts on the inner ring 20, the large-diameter side end surface 43 of the tapered roller 40 comes into contact with the large-diameter side inner end surface 24 a, and further, the thrust force acts on the outer ring 11 via the tapered roller 40. Since a part of the thrust force is received while sliding between the large-diameter side end face 43 and the large-diameter side inner end face 24a of the tapered roller 40, seizure is likely to occur.

これに対し、外輪１１および内輪２０間の油流路へ潤滑油が供給され、小径側鍔部２３から大径側鍔部２４へ潤滑油が流れる。このとき、矢印５０に示すように、保持器３０および内輪２０間の油流路を流れる流れと、矢印５１に示すように、油導入空間３８、油導入通路３２の順に流れ、さらに保持器３０および内輪２０間の油流路を流れる流れの２つがあり、いずれの流れも、円すいころ４０の大径側端面４３および大径側内側端面２４ａ間の滑り接触する箇所へ供給されるので、焼付きを防止できる。油導入空間３８、油導入通路３２、絞り３９によって、円すいころ４０の大径側端面４３および大径側内側端面２４ａ間へ供給される潤滑油の流量が増え、自動車の発進時等の車速が低い状態で全体の潤滑油の供給量が少なくても、円すいころ４０の大径側端面４３および大径側内側端面２４ａ間の焼き付きを防止できる。   In contrast, the lubricating oil is supplied to the oil flow path between the outer ring 11 and the inner ring 20, and the lubricating oil flows from the small diameter side flange 23 to the large diameter side flange 24. At this time, as indicated by an arrow 50, a flow that flows through the oil flow path between the retainer 30 and the inner ring 20, and as indicated by an arrow 51, the oil introduction space 38 and the oil introduction passage 32 flow in this order. There are two flows that flow through the oil flow path between the inner ring 20 and each flow is supplied to the point of sliding contact between the large-diameter side end face 43 and the large-diameter side inner end face 24a of the tapered roller 40. Can prevent sticking. The oil introduction space 38, the oil introduction passage 32, and the restrictor 39 increase the flow rate of the lubricating oil supplied between the large diameter side end face 43 and the large diameter side inner end face 24a of the tapered roller 40, so that the vehicle speed at the start of the automobile is increased. Even if the supply amount of the entire lubricating oil is small in a low state, seizure between the large diameter side end face 43 and the large diameter side inner end face 24a of the tapered roller 40 can be prevented.

本発明はこうした実施形態に何等限定されるものではなく、本発明の要旨を逸脱しない範囲において、種々なる態様で実施し得ることは勿論である。   The present invention is not limited to these embodiments, and can of course be implemented in various modes without departing from the gist of the present invention.

上述した実施形態は、油導入通路３２を除いた全周で、円すいころ４０が当接するようにポケット３１を加工した。他の実施形態として、油導入通路３２を除いた全周ではなく、一部でポケット３１と円すいころ４０とが接触するようにすれば、ポケット３１の形状をより簡単化できる。   In the above-described embodiment, the pocket 31 is processed so that the tapered roller 40 contacts the entire circumference excluding the oil introduction passage 32. As another embodiment, if the pocket 31 and the tapered roller 40 are in contact with each other instead of the entire circumference excluding the oil introduction passage 32, the shape of the pocket 31 can be further simplified.

上述した実施形態は、第１の案内部３４に対して内輪２０側へ折れ曲がった折れ曲がり部３３を有する。他の実施形態として、膨らみ部６０によって保持器３０全体の強度を確保できれば、折れ曲がり部３３を省略することもできる。折れ曲がり部３３を無くすと、保持器３０および内輪２０間へ流入する潤滑油が増大するメリットがある。   The embodiment described above includes the bent portion 33 that is bent toward the inner ring 20 with respect to the first guide portion 34. As another embodiment, if the strength of the entire cage 30 can be secured by the bulging portion 60, the bent portion 33 can be omitted. If the bent portion 33 is eliminated, there is an advantage that the lubricating oil flowing between the cage 30 and the inner ring 20 increases.

１１：外輪、１２：外輪側軌道面（軌道面）、２０：内輪、２２：内輪側軌道面（軌道面）、２３：小径側鍔部、２４：大径側鍔部、２４ａ：大径側内側端面、３０：保持器、３１：ポケット、３２：油導入通路、３８：油導入空間、３９：絞り、４０：円すいころ、６０：膨らみ部   11: Outer ring, 12: Outer ring side raceway surface (track surface), 20: Inner ring, 22: Inner ring side raceway surface (track surface), 23: Small diameter side collar, 24: Large diameter side collar, 24a: Large diameter side Inner end face, 30: cage, 31: pocket, 32: oil introduction passage, 38: oil introduction space, 39: throttle, 40: tapered roller, 60: bulge

Claims (1)

外輪と、前記外輪の内周側に配置される内輪と、前記外輪および前記内輪間に配置され円周上等間隔に複数のポケットを有する保持器と、前記ポケットに配置される複数の円すいころとからなり、前記外輪の内周および前記内輪の外周に前記円すいころが転動する軌道面を形成し、前記内輪に前記軌道面の軸方向両側の一方に小径側鍔部を、他方に大径側鍔部を形成し、この大径側鍔部に前記円すいころが滑り接触する大径側内側端面を形成し、前記外輪および前記内輪間にできる空間が、前記内輪の小径側鍔部から大径側鍔部へ潤滑油が流れる油流路とされている円すいころ軸受において、前記内輪の前記小径側鍔部側にある前記保持器を、前記外輪に対し内径側へ離して設けることにより、前記外輪および前記保持器間に油導入空間を形成し、前記保持器の軸方向中間を外径側へ膨らませて膨らみ部を形成し、前記外輪の軌道面および前記膨らみ部間に前記油流路を絞る絞りを形成し、この絞り前の前記保持器に、前記油導入空間の潤滑油を前記保持器および前記内輪間の油流路へ導く油導入通路を形成したことを特徴とする円すいころ軸受。   An outer ring, an inner ring disposed on the inner peripheral side of the outer ring, a cage disposed between the outer ring and the inner ring and having a plurality of pockets at equal intervals on the circumference, and a plurality of tapered rollers disposed in the pockets A raceway surface on which the tapered roller rolls is formed on the inner periphery of the outer ring and the outer periphery of the inner ring, and the inner ring has a small-diameter side flange on one side of the raceway surface in the axial direction and a large on the other side. A diameter side flange is formed, a large diameter side inner end surface on which the tapered roller is in sliding contact with the large diameter side flange is formed, and a space formed between the outer ring and the inner ring is formed from the small diameter side flange of the inner ring. In the tapered roller bearing in which the lubricating oil flows into the large-diameter side flange, the retainer on the small-diameter side flange of the inner ring is provided away from the outer ring toward the inner diameter side. An oil introduction space is formed between the outer ring and the cage. Then, the axial middle of the cage is bulged to the outer diameter side to form a bulge portion, and a throttle is formed to squeeze the oil flow path between the raceway surface of the outer ring and the bulge portion. The tapered roller bearing is characterized in that an oil introduction passage is formed in the container to guide the lubricating oil in the oil introduction space to an oil flow path between the cage and the inner ring.
JP2011113646A 2011-05-20 2011-05-20 Tapered roller bearing Withdrawn JP2012241828A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015102133A (en) * 2013-11-22 2015-06-04 株式会社ジェイテクト Conical roller bearing
US9140303B2 (en) 2013-08-14 2015-09-22 Aktiebolaget Skf Cage for a roller bearing and roller bearing
DE102014219311A1 (en) * 2014-09-24 2016-03-24 Aktiebolaget Skf Rolling bearing cage
US9897139B2 (en) 2013-11-22 2018-02-20 Jtekt Corporation Tapered roller bearing and power transmission apparatus
CN110159654A (en) * 2019-05-21 2019-08-23 人本集团有限公司 Differential mechanism tapered roller bearing

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9140303B2 (en) 2013-08-14 2015-09-22 Aktiebolaget Skf Cage for a roller bearing and roller bearing
JP2015102133A (en) * 2013-11-22 2015-06-04 株式会社ジェイテクト Conical roller bearing
US9897139B2 (en) 2013-11-22 2018-02-20 Jtekt Corporation Tapered roller bearing and power transmission apparatus
DE102014219311A1 (en) * 2014-09-24 2016-03-24 Aktiebolaget Skf Rolling bearing cage
CN110159654A (en) * 2019-05-21 2019-08-23 人本集团有限公司 Differential mechanism tapered roller bearing
CN110159654B (en) * 2019-05-21 2021-01-12 人本股份有限公司 Tapered roller bearing for differential

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