JP2013015201A - Conical bearing - Google Patents

Conical bearing Download PDF

Info

Publication number
JP2013015201A
JP2013015201A JP2011149142A JP2011149142A JP2013015201A JP 2013015201 A JP2013015201 A JP 2013015201A JP 2011149142 A JP2011149142 A JP 2011149142A JP 2011149142 A JP2011149142 A JP 2011149142A JP 2013015201 A JP2013015201 A JP 2013015201A
Authority
JP
Japan
Prior art keywords
tapered roller
diameter
inner ring
engaging
outer ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
JP2011149142A
Other languages
Japanese (ja)
Inventor
Kohei Yamaguchi
高平 山口
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
JTEKT Corp
Original Assignee
JTEKT Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by JTEKT Corp filed Critical JTEKT Corp
Priority to JP2011149142A priority Critical patent/JP2013015201A/en
Publication of JP2013015201A publication Critical patent/JP2013015201A/en
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • F16C19/225—Details of the ribs supporting the end 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
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
    • 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
    • F16C33/4682—Details of individual pockets, e.g. shape or roller retaining means of the end walls, e.g. interaction with the end faces 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
    • F16C33/49—Cages for rollers or needles comb-shaped
    • F16C33/494—Massive or moulded comb cages
    • F16C33/495—Massive or moulded comb cages formed as one piece cages, i.e. monoblock comb cages
    • 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
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage

Landscapes

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

Abstract

PROBLEM TO BE SOLVED: To further enhance the tolerable load of a conical bearing without increase in outer diameter of the conical bearing.SOLUTION: The conical bearing includes: an outer ring 11, an inner ring 20 disposed on the inner peripheral side of the outer ring 11, a conical roller 40 rolled between the outer ring 11 and the inner ring 20, and a retainer 30 for disposing a plurality of conical rollers 40 at circumferential intervals. A large diameter-side collar portion 24 protruding to the outer diameter side is formed on the large diameter side of the inner ring 20, and the retainer 30 is disposed between the large diameter-side collar portion 24 and the conical rollers 40. The retainer 30 has a first sliding surface 31 formed so as to make slide contact with the large diameter-side collar portion 24 in the rotating direction, a second sliding surface 32 formed so as to make slide contact with the conical rollers 40, and an engagement portion 33 formed so as to engage with the conical rollers 40 in the circumferential direction to hold the conical rollers 40 at circumferential intervals.

Description

本発明は、外輪と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７（特許文献１）に示すように、円すいころ軸受１００は、内輪１１０と、外輪１２０と、内輪１１０および外輪１２０間を転動する円すいころ１３０と、円すいころ１３０を円周方向に間隔を空けて回転可能に保持する保持器１４０とを有する。   As shown in FIG. 7 (Patent Document 1), the tapered roller bearing 100 includes an inner ring 110, an outer ring 120, a tapered roller 130 that rolls between the inner ring 110 and the outer ring 120, and a tapered roller 130 spaced in the circumferential direction. And a retainer 140 that holds the shaft rotatably.

一般的な円すいころ１３０は、図８の一部に示すように、保持器１４０のポケット１４１に回転可能に保持されるが、図７および図８（特許文献１）に示すものは、一部の柱部１４２のみを残して、大半の柱部を無くし、保持器１４０の小径側環状部１４３に凸部１４４を形成し、保持器１４０の大径側環状部１４５に凸部１４６に形成し、円すいころ１３０の両端面に凹部１３１、１３２を形成し、凸部１４４、１４６に凹部１３１、１３２を係合させることで、円すいころ１３０を回転可能に保持している。   The general tapered roller 130 is rotatably held in the pocket 141 of the retainer 140 as shown in a part of FIG. 8, but the part shown in FIG. 7 and FIG. Most of the pillar portions are eliminated, the convex portion 144 is formed on the small-diameter side annular portion 143 of the cage 140, and the convex portion 146 is formed on the large-diameter side annular portion 145 of the cage 140. The tapered rollers 130 are rotatably held by forming concave portions 131 and 132 on both end faces of the tapered rollers 130 and engaging the concave portions 131 and 132 with the convex portions 144 and 146, respectively.

このものは、大半の柱部を無くして円すいころ１３０の数を増やすことで、円すいころ軸受１００の耐えられる荷重を高めている。   This increases the load that the tapered roller bearing 100 can withstand by eliminating most of the column portions and increasing the number of tapered rollers 130.

前記保持器１４０は、ポケット１４１を介して円すいころ１３０に円すいころ軸受１００の軸線回りに回転可能に保持されているため、最低限の柱部１４２が必要となり、円すいころ１３０の数を増やすのに限界があり、これ以上、円すいころ軸受の耐えられる荷重を高めることが出来なかった。   Since the retainer 140 is held by the tapered roller 130 via the pocket 141 so as to be rotatable around the axis of the tapered roller bearing 100, a minimum number of column portions 142 are required, and the number of tapered rollers 130 is increased. However, the load that can be withstood by the tapered roller bearing could not be increased.

特開２００８−１２１７４３号公報JP 2008-121743 A

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、円すいころ軸受の外径を大きくすること無しに、円すいころ軸受の耐えられる荷重をより高める。   The present invention has been made to solve the above-described problems, and an object of the present invention is to further increase the load that the tapered roller bearing can withstand without increasing the outer diameter of the tapered roller bearing.

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を転動する円すいころと、複数の円すいころを円周方向に間隔を空けて配置する保持器とからなる円すいころ軸受において、
前記内輪の大径側に外径側へ突出した大径側鍔部を形成し、この大径側鍔部および前記円すいころ間に前記保持器を配置し、この保持器に前記大径側鍔部に対しこれの回転方向に摺接する第１の摺接面を形成し、前記保持器に前記円すいころに対しこれの回転方向に摺接する第２の摺接面を形成し、前記保持器に前記円すいころに対し円周方向に係合し、前記円すいころを円周方向に間隔を空けて保持する係合部を形成したものである。 According to the first aspect of the present invention, an outer ring, an inner ring disposed on the inner peripheral side of the outer ring, a tapered roller that rolls between the outer ring and the inner ring, and a plurality of tapered rollers are spaced in the circumferential direction. In a tapered roller bearing consisting of a cage that is arranged in a space,
A large-diameter flange that protrudes toward the outer diameter is formed on the large-diameter side of the inner ring, and the cage is disposed between the large-diameter flange and the tapered roller, and the large-diameter flange is disposed on the cage. Forming a first slidable contact surface that is slidably contacted in the rotational direction with respect to the portion, and forming a second slidable contact surface that is slidably contacted with the tapered roller in the rotational direction on the retainer; An engagement portion is formed that engages with the tapered roller in the circumferential direction and holds the tapered roller at an interval in the circumferential direction.

請求項２に記載の発明は、前記係合部が、前記円すいころの前記外輪側の外周に摺接する係合突起であることを特徴とするものである。   The invention according to claim 2 is characterized in that the engaging portion is an engaging protrusion which is in sliding contact with the outer periphery of the tapered roller on the outer ring side.

請求項３に記載の発明は、前記係合部が、前記円すいころの大径側端面へ突出した係合凸部であり、前記円すいころの大径側端面に前記係合凸部に係合する係合凹部を形成し、前記係合凸部および前記係合凹部を円すいころの回転軸線と同軸に設けたことを特徴とするものである。   According to a third aspect of the present invention, the engaging portion is an engaging convex portion protruding to the large-diameter side end surface of the tapered roller, and is engaged with the engaging convex portion on the large-diameter side end surface of the tapered roller. The engaging concave portion is formed, and the engaging convex portion and the engaging concave portion are provided coaxially with the rotation axis of the tapered roller.

本発明によれば、円すいころ軸受の外径を大きくすること無しに、円すいころ軸受の耐えられる荷重をより高めることができる。   According to the present invention, it is possible to further increase the load that the tapered roller bearing can withstand without increasing the outer diameter of the tapered roller bearing.

本発明の実施形態における円すいころ軸受の断面図である。It is sectional drawing of the tapered roller bearing in embodiment of this invention. 本発明の実施形態における円すいころ軸受の図１のＡ矢視図である。It is an A arrow line view of Drawing 1 of a tapered roller bearing in an embodiment of the present invention. 本発明の実施形態における円すいころ軸受の図１のＢ矢視図である。It is a B arrow directional view of FIG. 1 of the tapered roller bearing in embodiment of this invention. 本発明の実施形態における円すいころ軸受の図１のＤ−Ｄ線における平面展開図である。It is a plane development view in the DD line of Drawing 1 of a tapered roller bearing in an embodiment of the present invention. 本発明の実施形態における円すいころ軸受の図１のＦ−Ｆ線断面図である。It is the FF sectional view taken on the line of FIG. 1 of the tapered roller bearing in embodiment of this invention. 本発明の他の実施形態における円すいころ軸受の断面図である。It is sectional drawing of the tapered roller bearing in other embodiment of this invention. 従来の円すいころ軸受の断面図である。It is sectional drawing of the conventional tapered roller bearing. 従来の円すいころ軸受の保持器の正面図である。It is a front view of the retainer of the conventional tapered roller bearing.

本発明の一実施形態について、図１乃至図６を参酌しつつ説明する。図１は、円すいころ軸受の断面図であり、図２は、図１のＡ矢視図であり、図３は、図１のＢ矢視図であり、図４は、図１のＤ−Ｄ線における平面展開図であり、図５は、円すいころ軸受の図１のＦ−Ｆ線断面図である。   An embodiment of the present invention will be described with reference to FIGS. 1 is a cross-sectional view of a tapered roller bearing, FIG. 2 is a view as viewed from an arrow A in FIG. 1, FIG. 3 is a view as viewed from an arrow B in FIG. 1, and FIG. FIG. 5 is a developed plan view along line D, and FIG. 5 is a cross-sectional view of the tapered roller bearing taken along line FF in FIG.

図１乃至図３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および内輪２０間に配置されるリング状の保持器３０と、保持器３０によって円周方向に間隔を空けて配置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 to 3, 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 that are spaced apart in the circumferential direction by the cage 30. The outer ring 11, the inner ring 20, the cage 30, and the tapered roller 40 are all made of a metal material, and in particular, an iron-based material is often used.

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。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と、内輪２０の軸線に対して平行な嵌合面２７とが形成されている。また内輪２０には、内輪側軌道面２２および嵌合面２７を挟んで小径側に外径方向へ突出した小径側鍔部２３が形成され、内輪側軌道面２２および嵌合面２７を挟んで大径側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４１に接触する小径側内側端面２５が形成されている。   An outer ring-side raceway surface 12 that is inclined with respect to the axis of the outer ring 11 is formed on the inner periphery of the outer ring 11. On the outer circumference of the inner ring 20, an inner ring side raceway surface 22 inclined with respect to the axis of the inner ring 20 and a fitting surface 27 parallel to the axis of the inner ring 20 are formed. Further, the inner ring 20 is formed with a small-diameter flange 23 projecting in the outer diameter direction on the small diameter side with the inner ring-side raceway surface 22 and the fitting surface 27 interposed therebetween. A large-diameter side flange 24 that protrudes in the outer diameter direction is formed on the large-diameter side. A small-diameter inner end surface 25 that contacts a small-diameter end surface 41 (to be described later) of the tapered roller 40 is formed on the end surface of the small-diameter flange portion 23 on the tapered roller 40 side.

大径側鍔部２４の円すいころ４０側の端面には、保持器３０の後述する第１の摺動面３１に接触する大径側内側端面２６が形成され、この大径側内側端面２６には内径側から順に、第１の油溝５１、第２の油溝５２、第３の油溝５３が形成されている。第１の油溝５１は、円弧状の形状を有し、円周方向に等間隔に複数形成されている。第２の油溝５２および第３の油溝５３は、内輪２０の軸線回りに形成された環状の溝である。第１の油溝５１、第２の油溝５２、第３の油溝５３は、潤滑油を保持する機能を有し、第１の油溝５１、第２の油溝５２、第３の油溝５３に保持された潤滑油を、第１の摺動面３１および大径側内側端面２６間に供給することによって、第１の摺動面３１および大径側内側端面２６間の焼き付きを防止できる。   A large-diameter inner end surface 26 that contacts a later-described first sliding surface 31 of the retainer 30 is formed on the end surface of the large-diameter side flange 24 on the tapered roller 40 side. Are formed with a first oil groove 51, a second oil groove 52, and a third oil groove 53 in order from the inner diameter side. The first oil grooves 51 have a circular arc shape, and a plurality of first oil grooves 51 are formed at equal intervals in the circumferential direction. The second oil groove 52 and the third oil groove 53 are annular grooves formed around the axis of the inner ring 20. The first oil groove 51, the second oil groove 52, and the third oil groove 53 have a function of holding lubricating oil, and the first oil groove 51, the second oil groove 52, and the third oil. By supplying the lubricating oil held in the groove 53 between the first sliding surface 31 and the large-diameter inner end surface 26, seizure between the first sliding surface 31 and the large-diameter inner end surface 26 is prevented. it can.

内輪２０は、内輪側軌道面２２および大径側鍔部２４を形成した大径側部材５０と、小径側鍔部２３を形成した小径側部材５５とからなり、大径側部材５０および小径側部材５５は、ボルト５６を介して互いに同軸に連結されている。内輪２０の内周側には、保持軸６０が挿入できるよう嵌合面が形成され、保持軸６０は、大径側部材５０および小径側部材５５を互いに同軸に組付ける役目を有する。   The inner ring 20 includes a large-diameter side member 50 in which the inner ring-side raceway surface 22 and the large-diameter side flange 24 are formed, and a small-diameter side member 55 in which the small-diameter side flange 23 is formed. The members 55 are coaxially connected to each other via bolts 56. A fitting surface is formed on the inner peripheral side of the inner ring 20 so that the holding shaft 60 can be inserted. The holding shaft 60 serves to assemble the large diameter side member 50 and the small diameter side member 55 coaxially with each other.

図１、図３および図４に示すように、保持器３０は、リング状の形状を有し、径方向においては外輪１１および内輪２０間に配置され、軸方向においては大径側鍔部２４および円すいころ４０間に配置される。また保持器３０は、内輪２０の大径側内側端面２６に対し内輪２０の回転方向に摺接する第１の摺動面３１を有し、円すいころ４０の後述する大径側端面４２に対し円すいころ４０の回転方向に摺接する第２の摺動面３２を有する。さらに保持器３０は、円すいころ４０側へ軸方向に突出し、かつ複数の円すいころ４０間に配置された係合突起３３を有する。係合突起３３の円周方向両側には、円すいころ４０の外周に摺接する第３の摺動面３４が形成され、係合突起３３は複数の円すいころ４０を円周方向に間隔を空けて保持する機能を有する。第１の摺動面３１は、保持器３０の軸線に対し垂直な面であり、第２の摺動面３２は、円すいころ４０の回転軸線に対し垂直な面である。保持器３０は、鍛造等により成形され、切削により所定の寸法に仕上げられる。   As shown in FIGS. 1, 3, and 4, the retainer 30 has a ring shape, is disposed between the outer ring 11 and the inner ring 20 in the radial direction, and has a large-diameter side flange 24 in the axial direction. And between the tapered rollers 40. The retainer 30 has a first sliding surface 31 that is in sliding contact with the large-diameter inner end surface 26 of the inner ring 20 in the rotational direction of the inner ring 20, and is tapered with respect to a later-described large-diameter end surface 42 of the tapered roller 40. It has the 2nd sliding surface 32 which slidably contacts to the rotation direction of the roller 40. FIG. Furthermore, the retainer 30 has an engagement protrusion 33 that protrudes in the axial direction toward the tapered roller 40 and is disposed between the plurality of tapered rollers 40. A third sliding surface 34 is formed on both sides of the engaging protrusion 33 in the circumferential direction so as to be in sliding contact with the outer periphery of the tapered roller 40, and the engaging protrusion 33 has a plurality of tapered rollers 40 spaced apart in the circumferential direction. Has the function of holding. The first sliding surface 31 is a surface perpendicular to the axis of the cage 30, and the second sliding surface 32 is a surface perpendicular to the rotational axis of the tapered roller 40. The cage 30 is formed by forging or the like and finished to a predetermined dimension by cutting.

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と、小径側の端面に形成された小径側端面４１と、大径側の端面に形成された大径側端面４２を有する。   The tapered roller 40 has a shape obtained by removing a top portion from a conical shape, and is formed on a rolling surface that rolls on the outer ring side raceway surface 12 and the inner ring side raceway surface 22 and an end surface on the small diameter side. It has a small-diameter side end surface 41 and a large-diameter side end surface 42 formed on the large-diameter side end surface.

続いて上述した構成にもとづいて、組付け動作を説明する。   Next, the assembling operation will be described based on the configuration described above.

保持軸６０に大径側部材５０を嵌合させ、大径側部材５０の嵌合面２７に保持器３０を遊嵌させる。次に、円すいころ４０を内輪側軌道面２２上に配置し、円すいころ４０の外周を係合突起３３に係合させる。保持軸６０に小径側部材５５を嵌合させ、ボルト５６をねじ込むことにより大径側部材５０および小径側部材５５を互いに同軸に連結する。大径側部材５０および小径側部材５５から保持軸６０を抜き取る。こうして、内輪２０、保持器３０、円すいころ４０がバラバラにならないように一体化し、一体化した内輪２０、保持器３０、円すいころ４０は、図略の回転軸に組付けられる。図略のハウジングに外輪１１が取り付けられ、この外輪１１に回転軸と一体化した内輪２０、保持器３０、円すいころ４０が挿入される。こうして、回転軸はハウジングに対し円すいころ軸受１０を介して軸承される。   The large-diameter side member 50 is fitted to the holding shaft 60, and the cage 30 is loosely fitted to the fitting surface 27 of the large-diameter side member 50. Next, the tapered roller 40 is disposed on the inner ring side raceway surface 22, and the outer periphery of the tapered roller 40 is engaged with the engaging protrusion 33. The small diameter side member 55 is fitted to the holding shaft 60 and the bolt 56 is screwed to connect the large diameter side member 50 and the small diameter side member 55 coaxially. The holding shaft 60 is extracted from the large diameter side member 50 and the small diameter side member 55. Thus, the inner ring 20, the cage 30 and the tapered roller 40 are integrated so as not to fall apart, and the integrated inner ring 20, the cage 30 and the tapered roller 40 are assembled to a rotating shaft (not shown). The outer ring 11 is attached to a housing (not shown), and the inner ring 20, the retainer 30, and the tapered roller 40 integrated with the rotating shaft are inserted into the outer ring 11. Thus, the rotating shaft is supported on the housing via the tapered roller bearing 10.

このようにして組付けられた回転軸および内輪２０を回転させると、円すいころ４０は外輪側軌道面１２および内輪側軌道面２２上を転動しながら内輪２０の回転方向と同方向へ移動する。このとき、保持器３０は、軸方向において、大径側鍔部２４と円すいころ４０とで挟み込まれ、大径側内側端面２６で案内支持され、円周方向において、係合突起３３と円すいころ４０とが係合しているので、円すいころ４０の転動によって保持器３０が内輪２０と同方向へ回転する。   When the rotating shaft and the inner ring 20 assembled in this way are rotated, 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. . At this time, the retainer 30 is sandwiched between the large-diameter side flange portion 24 and the tapered roller 40 in the axial direction, is guided and supported by the large-diameter side inner end surface 26, and the engagement protrusion 33 and the tapered roller are disposed in the circumferential direction. 40 is engaged, the retainer 30 is rotated in the same direction as the inner ring 20 by the rolling of the tapered roller 40.

回転軸に作用する軸方向の力は、主に、内輪側軌道面２２を介して円すいころ４０に作用し、さらに外輪側軌道面１２を介して外輪１１に作用する。また回転軸に作用する軸方向の力は、補助的に、大径側内側端面２６を介して保持器３０に作用し、さらに、大径側端面４２を介して円すいころ４０に作用し、またさらに、外輪側軌道面１２を介して外輪１１に作用する。円すいころ４０および大径側鍔部２４間に保持器３０を介挿することにより、円すいころ４０の大径側端面４２の接触面積が増え、円すいころ軸受１０の耐えられる荷重が高められる。円すいころ４０の回転による接触と、保持器３０の回転による接触が分散され、第２の摺動面３２、大径側内側端面２６のそれぞれで接触による摩耗が発生し、摩耗による寿命を延ばすことができる。従来の保持器の柱部に代えて係合突起３３を使用することにより、円すいころ４０を内輪２０の円周方向に多数配置することができ、円すいころ軸受１０の耐えられる荷重を高めることができる。   The axial force acting on the rotating shaft mainly acts on the tapered roller 40 via the inner ring side raceway surface 22 and further acts on the outer ring 11 via the outer ring side raceway surface 12. Further, the axial force acting on the rotating shaft acts on the retainer 30 via the large-diameter inner end surface 26 in an auxiliary manner, and further acts on the tapered roller 40 via the large-diameter end surface 42. Further, it acts on the outer ring 11 via the outer ring side raceway surface 12. By inserting the retainer 30 between the tapered roller 40 and the large diameter side flange 24, the contact area of the large diameter side end surface 42 of the tapered roller 40 increases, and the load that the tapered roller bearing 10 can withstand is increased. Contact due to rotation of the tapered roller 40 and contact due to rotation of the cage 30 are dispersed, and wear due to contact occurs on each of the second sliding surface 32 and the large-diameter inner end surface 26, thereby extending the life due to wear. Can do. By using the engaging protrusions 33 in place of the conventional retainer column portion, a large number of tapered rollers 40 can be arranged in the circumferential direction of the inner ring 20, and the load that the tapered roller bearing 10 can withstand is increased. it can.

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、円すいころ４０の外輪１１側の外周に係合突起３３を係合させた。他の実施形態として、図６に示すように、保持器３０の第２の摺動面３２に円すいころ４０側へ突出した係合凸部３５を形成し、この係合凸部３５が係合する係合凹部４５を円すいころ４０の大径側端面４２に形成しても良い。係合凸部３５および係合凹部４５は、円すいころ４０の回転軸線と同軸上に形成される。このものは、円すいころ４０間に係合突起３３が無い分だけ、円すいころ４０をより多く配置することができる反面、円すいころ４０および保持器３０間の接触面積が減る。上述した実施形態と同じ部品、同じ面については、同一の番号を付与し、説明は省略する。   In the embodiment described above, the engagement protrusion 33 is engaged with the outer periphery of the tapered roller 40 on the outer ring 11 side. As another embodiment, as shown in FIG. 6, an engagement convex portion 35 protruding to the tapered roller 40 side is formed on the second sliding surface 32 of the cage 30, and this engagement convex portion 35 is engaged. The engaging recess 45 may be formed on the large-diameter side end face 42 of the tapered roller 40. The engaging convex portion 35 and the engaging concave portion 45 are formed coaxially with the rotation axis of the tapered roller 40. Although this can arrange more tapered rollers 40 by the amount of the engagement projections 33 between the tapered rollers 40, the contact area between the tapered rollers 40 and the cage 30 is reduced. The same parts and the same surfaces as those in the above-described embodiment are given the same numbers, and descriptions thereof are omitted.

１１：外輪、２０：内輪、２４：大径側鍔部、３０：保持器、３１：第１の摺動面、３２：第２の摺動面、３３：係合突起（係合部）、３５：係合凸部（係合部）、４０：円すいころ、４５：係合凹部 11: Outer ring, 20: Inner ring, 24: Large-diameter side flange, 30: Cage, 31: First sliding surface, 32: Second sliding surface, 33: Engaging protrusion (engaging portion), 35: engagement convex part (engagement part), 40: tapered roller, 45: engagement concave part

Claims (3)

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を転動する円すいころと、複数の円すいころを円周方向に間隔を空けて配置する保持器とからなる円すいころ軸受において、
前記内輪の大径側に外径側へ突出した大径側鍔部を形成し、この大径側鍔部および前記円すいころ間に前記保持器を配置し、この保持器に前記大径側鍔部に対しこれの回転方向に摺接する第１の摺接面を形成し、前記保持器に前記円すいころに対しこれの回転方向に摺接する第２の摺接面を形成し、前記保持器に前記円すいころに対し円周方向に係合し、前記円すいころを円周方向に間隔を空けて保持する係合部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 tapered roller that rolls between the outer ring and the inner ring, and a cage that disposes a plurality of tapered rollers at intervals in the circumferential direction. In tapered roller bearings,
A large-diameter flange that protrudes toward the outer diameter is formed on the large-diameter side of the inner ring, and the cage is disposed between the large-diameter flange and the tapered roller, and the large-diameter flange is disposed on the cage. Forming a first slidable contact surface that is slidably contacted in the rotational direction with respect to the portion, and forming a second slidable contact surface that is slidably contacted with the tapered roller in the rotational direction on the retainer; A tapered roller bearing comprising: an engaging portion that engages with the tapered roller in a circumferential direction and holds the tapered roller at an interval in the circumferential direction. 前記係合部は、前記円すいころの前記外輪側の外周に摺接する係合突起であることを特徴とする請求項１に記載の円すいころ軸受。   2. The tapered roller bearing according to claim 1, wherein the engaging portion is an engaging protrusion that is in sliding contact with an outer periphery of the tapered roller on the outer ring side. 前記係合部は、前記円すいころの大径側端面へ突出した係合凸部であり、前記円すいころの大径側端面に前記係合凸部に係合する係合凹部を形成し、前記係合凸部および前記係合凹部を円すいころの回転軸線と同軸に設けたことを特徴とする請求項１に記載の円すいころ軸受。   The engaging portion is an engaging convex portion protruding to the large-diameter side end surface of the tapered roller, and an engaging concave portion that engages with the engaging convex portion is formed on the large-diameter side end surface of the tapered roller, The tapered roller bearing according to claim 1, wherein the engaging convex portion and the engaging concave portion are provided coaxially with a rotation axis of the tapered roller.
JP2011149142A 2011-07-05 2011-07-05 Conical bearing Withdrawn JP2013015201A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2011149142A JP2013015201A (en) 2011-07-05 2011-07-05 Conical bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011149142A JP2013015201A (en) 2011-07-05 2011-07-05 Conical bearing

Publications (1)

Publication Number Publication Date
JP2013015201A true JP2013015201A (en) 2013-01-24

Family

ID=47688051

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2011149142A Withdrawn JP2013015201A (en) 2011-07-05 2011-07-05 Conical bearing

Country Status (1)

Country Link
JP (1) JP2013015201A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016133005A1 (en) * 2015-02-19 2016-08-25 Ntn株式会社 Tapered roller bearing
WO2023204161A1 (en) * 2022-04-20 2023-10-26 日本精工株式会社 Roller bearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016133005A1 (en) * 2015-02-19 2016-08-25 Ntn株式会社 Tapered roller bearing
WO2023204161A1 (en) * 2022-04-20 2023-10-26 日本精工株式会社 Roller bearing

Similar Documents

Publication Publication Date Title
JP2013015200A (en) Conical roller bearing
WO2013051696A1 (en) Rolling bearing
JP2009063165A (en) Roller bearing
JP2018109448A (en) Conical roller bearing
JP2013174283A (en) Solid-type needle roller bearing
JP2013015201A (en) Conical bearing
JP2012219994A (en) Rolling bearing
JP2013217482A (en) Tapered roller bearing
JP2014122649A (en) Roller bearing
JP6318632B2 (en) Double row rolling bearing
JP6343920B2 (en) Combined radial and thrust bearings
JP5218231B2 (en) Roller bearing cage, inner ring assembly, outer ring assembly and rolling bearing provided with the cage
WO2016194981A1 (en) Tapered roller bearing
JP6094637B2 (en) Roller bearing cage
JP6003022B2 (en) Roller bearing cage
JP2014047798A (en) Turning gear
JP5540366B2 (en) Cylindrical roller bearing device
WO2018101038A1 (en) Roller bearing
JP2015004440A (en) Radial-thrust combined needle bearing
JPWO2022074862A5 (en)
JP2013130242A (en) Thrust roller bearing
JP2014240672A (en) Bearing device
JP2006194375A (en) Thrust cylindrical roller bearing
JP2012072869A (en) Tapered roller bearing
JP2012229718A (en) Rolling bearing

Legal Events

Date Code Title Description
A300 Withdrawal of application because of no request for examination

Free format text: JAPANESE INTERMEDIATE CODE: A300

Effective date: 20141007