JP2008128421A - Double row rolling bearing - Google Patents

Double row rolling bearing Download PDF

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Publication number
JP2008128421A
JP2008128421A JP2006316602A JP2006316602A JP2008128421A JP 2008128421 A JP2008128421 A JP 2008128421A JP 2006316602 A JP2006316602 A JP 2006316602A JP 2006316602 A JP2006316602 A JP 2006316602A JP 2008128421 A JP2008128421 A JP 2008128421A
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Prior art keywords
double
bearing
row
rolling
rolling bearing
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JP2006316602A
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Japanese (ja)
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Chiyoukoku Uchiyama
暢克 内山
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2006316602A priority Critical patent/JP2008128421A/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
    • 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
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6629—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • 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
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded 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
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6622—Details of supply and/or removal of the grease, e.g. purging grease
    • F16C33/6625—Controlling or conditioning the grease supply
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • 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
    • F16C19/38—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 two or more rows of rollers
    • F16C19/383—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7893—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a cage or integral therewith

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double row rolling bearing reduced in weight and cost by reducing the grease amount to be sealed within a bearing while ensuring satisfactory lubricity. <P>SOLUTION: The double row angular ball bearing comprises an outer ring 2 having double-row outside rolling surfaces 2a formed on the inner circumference, a pair of inner rings 3 each having an inside rolling surface 3a on the outer circumference, double-row balls 4 stored between both the rolling surfaces through a retainer 5 so as to freely roll, and seals 6 and 7 installed to an opening part of an annular space formed between the outer ring 2 and the inner ring 3, the bearing including a predetermined quantity of grease encapsulated therein. A radially protruding annular base part 10 is formed at an end portion of the retainer 5, and the annular base part 10 is opposed to an inside diameter part 2b of the outer ring 2 and an outside diameter part 3c on the minor diameter side of the inner ring 3 through radial clearances e1 and e2 set within the range of 0.5-2.0 mm. Therefore, flowing of the grease adhered to the circumference of the ball 4, the body of the retainer 5 or the like to the bearing central part can be regulated. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、自動車等の車輪を回転自在に支承する複列の転がり軸受、特に、良好な潤滑性を確保すると共に、軸受内部に封入されるグリース量を削減して軽量化と低コスト化を図った複列の転がり軸受に関するものである。   The present invention is a double-row rolling bearing that rotatably supports wheels of automobiles and the like, and in particular, ensures good lubricity and reduces the amount of grease enclosed in the bearing, thereby reducing weight and cost. The present invention relates to the double row rolling bearing shown.

従来から自動車等の車輪を支持する車輪用軸受装置は、車輪を取り付けるためのハブ輪を複列の転がり軸受を介して回転自在に支承するもので、この複列の転がり軸受には、一般的に、所望の軸受剛性を有し、ミスアライメントに対しても耐久性を発揮すると共に、何よりも燃費向上の観点から回転トルクが小さい複列アンギュラ玉軸受が多用されている。一方、オフロードカーやトラック等、車体重量が嵩む車両には複列円錐ころ軸受が使用されている。   Conventionally, a wheel bearing device for supporting a wheel of an automobile or the like is such that a hub wheel for mounting a wheel is rotatably supported via a double row rolling bearing. In addition, a double-row angular ball bearing having a desired bearing rigidity, exhibiting durability against misalignment, and having a small rotational torque from the viewpoint of improving fuel efficiency is often used. On the other hand, double row tapered roller bearings are used in vehicles such as off-road cars and trucks that have a heavy vehicle body weight.

また、車輪用軸受装置には、懸架装置を構成するナックルとハブ輪との間に複列のアンギュラ玉軸受等からなる車輪用軸受を嵌合させた第１世代と称される構造から、外方部材の外周に直接車体取付フランジまたは車輪取付フランジが形成された第２世代構造、また、ハブ輪の外周に一方の内側転走面が直接形成された第３世代構造、あるいは、ハブ輪と等速自在継手の外側継手部材の外周にそれぞれ内側転走面が直接形成された第４世代構造とに大別されている。   Further, the wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double row angular ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device. A second generation structure in which a vehicle body mounting flange or a wheel mounting flange is directly formed on the outer periphery of the side member, a third generation structure in which one inner rolling surface is directly formed on the outer periphery of the hub wheel, or a hub wheel It is roughly classified into a fourth generation structure in which the inner rolling surface is directly formed on the outer periphery of the outer joint member of the constant velocity universal joint.

図５に示す複列の転がり軸受はその代表的な一例である。この複列の転がり軸受５０は第１世代と称され、内周に円弧状の複列の外側転走面５１ａ、５１ａが形成された外輪５１と、外周に前記複列の外側転走面５１ａ、５１ａに対向する円弧状の内側転走面５２ａが形成された一対の内輪５２、５２と、両転走面間に収容された複列のボール５３、５３と、これらのボール５３を転動自在に保持する保持器５４、５４と、外輪５１の両端部に装着されたシール５５、５６とを備えている。   The double row rolling bearing shown in FIG. 5 is a typical example. This double-row rolling bearing 50 is called the first generation, and an outer ring 51 having an arc-shaped double-row outer rolling surface 51a, 51a formed on the inner periphery, and the double-row outer rolling surface 51a on the outer periphery. , 51a, a pair of inner rings 52, 52 formed with an arcuate inner rolling surface 52a, double-row balls 53, 53 accommodated between both rolling surfaces, and rolling these balls 53 Retainers 54 and 54 that are freely held, and seals 55 and 56 that are attached to both ends of the outer ring 51 are provided.

一対の内輪５２、５２の小径側（正面側）端面は突き合された状態でセットされ、所謂背面合せタイプの複列のアンギュラ玉軸受を構成している。そして、外輪５１あるいは外輪５１と内輪５２に装着されたシール５５、５６により、軸受内部に封入された潤滑グリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。   The pair of inner rings 52, 52 are set in a state where the end surfaces on the small diameter side (front side) are butted together to form a so-called back-to-back type double row angular ball bearing. The outer ring 51 or the seals 55 and 56 attached to the outer ring 51 and the inner ring 52 prevent leakage of the lubricating grease sealed inside the bearing and intrusion of rainwater and dust from the outside into the bearing. is doing.

この種の複列の転がり軸受５０は、予め保持器５４にボール５３が組み込まれ、これらサブアッシが外輪５１の両側から複列の外側転走面５１ａ、５１ａにそれぞれ嵌挿され、所定量のグリースが封入される。その後、一対の内輪５２、５２が外輪５１の両側からそれぞれ嵌挿され、外輪５１と内輪５２との間に形成される環状空間の開口部にシール５５、５６が装着されて組立が完了する。しかし、係る先行技術は、文献公知発明に係るものでないため、記載すべき先行技術文献情報はない。   In this type of double row rolling bearing 50, balls 53 are incorporated in a cage 54 in advance, and these sub-assemblies are respectively inserted into the double row outer raceway surfaces 51a and 51a from both sides of the outer ring 51, thereby providing a predetermined amount of grease. Is enclosed. Thereafter, the pair of inner rings 52, 52 are respectively inserted from both sides of the outer ring 51, and the seals 55, 56 are attached to the openings of the annular space formed between the outer ring 51 and the inner ring 52, and the assembly is completed. However, there is no prior art document information to be described because the prior art does not relate to a known literature invention.

従来、軸受内部に封入されるグリース量に関して、例えば、軸受内部の全空間容積あるいは静止空間容積に対する比率が経験則に基いて規定され、所定量のグリースが封入されるが、例えば、ボール５３、５３間のピッチが大きな軸受においては、軸受内部の空間容積に比例してグリース封入量が多くなる。ここで、全空間容積とは、ボール５３や保持器５４等、軸受構成部品間に形成される全ての内部空間の容積を言い、また、静止空間容積とは、シール５５、５６等、静止部品とボール５３等の回転部品との間に形成される環状空間の容積を言う。   Conventionally, with respect to the amount of grease enclosed in the bearing, for example, a ratio to the total space volume or static space volume inside the bearing is defined based on empirical rules, and a predetermined amount of grease is enclosed. In a bearing with a large pitch between 53, the amount of grease filled increases in proportion to the space volume inside the bearing. Here, the total space volume means the volume of all internal spaces formed between the bearing components such as the balls 53 and the cage 54, and the static space volume means the static parts such as the seals 55 and 56. And the volume of the annular space formed between the rotating parts such as the balls 53 and the like.

然しながら、封入されたグリースのうち実際に使用されるグリース、すなわち、有効に潤滑に寄与するグリースは実質的にボール５３や保持器５４周辺のグリースだけであって、それ以外の部位にあるグリース、例えば、図６に示すように、外輪５１と保持器５４との間の隙間を介して一旦外側転走面５１ａから流出したグリース５７は還流することなくその部位に滞留して殆ど潤滑に寄与することはない。これでは、封入量に対するグリースの使用効率が悪くなり、軽量化および低コスト化を阻害する要因となっていた。   However, the grease that is actually used out of the enclosed grease, that is, the grease that effectively contributes to lubrication is substantially only the grease around the balls 53 and the cage 54, and the grease in other parts, For example, as shown in FIG. 6, the grease 57 that has once flown out of the outer rolling surface 51a through the gap between the outer ring 51 and the retainer 54 stays in the portion without reflux and contributes almost to lubrication. There is nothing. This deteriorates the use efficiency of the grease with respect to the enclosed amount, and has been a factor that hinders weight reduction and cost reduction.

本発明は、このような事情に鑑みてなされたもので、良好な潤滑性を確保すると共に、軸受内部に封入されるグリース量を削減して軽量化と低コスト化を図った複列の転がり軸受を提供することを目的としている。   The present invention has been made in view of such circumstances, and ensures double lubrication while ensuring good lubricity and reducing the amount of grease enclosed in the bearing to reduce weight and cost. It aims to provide a bearing.

係る目的を達成すべく、本発明のうち請求項１記載の発明は、内周に複列の外側転走面が一体に形成された外方部材と、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、前記両転走面間に保持器を介して転動自在に収容された複列の転動体と、前記外方部材と内方部材との間に形成される環状空間の開口部に装着されたシールとを備え、軸受内部に所定量のグリースが封入された複列の転がり軸受において、前記保持器の端部に径方向に突出した環状基部が形成され、この環状基部が前記外方部材または内方部材あるいはその両方に所定の径方向隙間を介して対向されている。   In order to achieve the object, the invention according to claim 1 of the present invention includes an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and an outer rolling surface of the double row on the outer periphery. An inner member in which a double row of inner rolling surfaces facing each other is formed, a double row of rolling elements housed between the rolling surfaces via a cage, and the outer member. In a double row rolling bearing having a seal mounted in an opening of an annular space formed between the inner member and a predetermined amount of grease inside the bearing, a diameter is provided at an end of the cage. An annular base portion projecting in the direction is formed, and this annular base portion is opposed to the outer member and / or the inner member via a predetermined radial gap.

このように、軸受内部に所定量のグリースが封入された密封形の複列の転がり軸受において、保持器の端部に径方向に突出した環状基部が形成され、この環状基部が外方部材または内方部材あるいはその両方に所定の径方向隙間を介して対向されているので、転動体や保持器本体の周辺および各転走面に付着したグリースが軸受中央部に流動するのを規制することができ、転動体間のピッチが大きな軸受であっても、グリースの使用効率を高めて軸受の良好な潤滑性を確保すると共に、軸受内部に封入されるグリース量を削減して軽量化と低コスト化を図った複列の転がり軸受を提供することができる。   Thus, in a sealed double-row rolling bearing in which a predetermined amount of grease is sealed inside the bearing, an annular base portion protruding radially is formed at the end of the cage, and the annular base portion is an outer member or Since it faces the inner member or both through a predetermined radial clearance, it restricts the grease attached to the periphery of the rolling element and cage body and each rolling surface from flowing to the center of the bearing. Even for bearings with a large pitch between rolling elements, the use efficiency of grease is increased to ensure good lubricity of the bearing, and the amount of grease enclosed in the bearing is reduced to reduce weight and weight. It is possible to provide a double-row rolling bearing that achieves cost reduction.

好ましくは、請求項２に記載の発明のように、前記径方向隙間が０．５〜２．０ｍｍの範囲に設定されていれば、保持器と外方部材または内方部材に接触することなく、グリースの流動を効果的に規制することができる。   Preferably, as in the invention described in claim 2, if the radial gap is set in a range of 0.5 to 2.0 mm, the cage does not contact the outer member or the inner member. The grease flow can be effectively regulated.

また、請求項３に記載の発明のように、前記複列の転がり軸受が複列のアンギュラ玉軸受で構成され、前記内方部材が、外周に円弧状の内側転走面が形成された一対の内輪からなり、これらの内輪の小径側端面が突き合された状態でセットされた背面合せタイプで構成されていても良い。   According to a third aspect of the present invention, the double row rolling bearing is composed of a double row angular ball bearing, and the inner member has a pair of arcuate inner rolling surfaces formed on the outer periphery. These inner rings may be configured as a back-to-back type set in a state where the end faces on the small diameter side of these inner rings are abutted.

また、請求項４に記載の発明のように、前記保持器が熱可塑性合成樹脂を射出成形することにより形成され、環状の保持器本体の一端部に、周方向に一定間隔で対向する２つ一組の保持爪が設けられ、これら保持爪の間に凹球面に形成されたポケットを備えたスナップオンタイプで構成されていても良い。   Further, as in the invention described in claim 4, the cage is formed by injection-molding a thermoplastic synthetic resin, and is opposed to one end portion of the annular cage body at regular intervals in the circumferential direction. A pair of holding claws may be provided, and a snap-on type having a pocket formed in a concave spherical surface between the holding claws may be used.

また、請求項５に記載の発明のように、前記複列の転がり軸受が複列の円錐ころ軸受で構成され、前記内方部材が、外周にテーパ状の内側転走面が形成された一対の内輪からなり、これら内輪の内側転走面の大径側に前記円錐ころを案内する大鍔が形成され、前記内輪の小径側端面が突き合された状態でセットされた背面合せタイプで構成されていても良い。   Further, as in the invention described in claim 5, the double row rolling bearing is constituted by a double row tapered roller bearing, and the inner member is a pair in which a tapered inner rolling surface is formed on the outer periphery. The inner ring is composed of a back-to-back type in which a large collar for guiding the tapered roller is formed on the large diameter side of the inner raceway surface of these inner rings and the small diameter side end surface of the inner ring is abutted. May be.

本発明に係る複列の転がり軸受は、内周に複列の外側転走面が一体に形成された外方部材と、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、前記両転走面間に保持器を介して転動自在に収容された複列の転動体と、前記外方部材と内方部材との間に形成される環状空間の開口部に装着されたシールとを備え、軸受内部に所定量のグリースが封入された複列の転がり軸受において、前記保持器の端部に径方向に突出した環状基部が形成され、この環状基部が前記外方部材または内方部材あるいはその両方に所定の径方向隙間を介して対向されているので、転動体や保持器本体の周辺および各転走面に付着したグリースが軸受中央部に流動するのを規制することができ、転動体間のピッチが大きな軸受であっても、グリースの使用効率を高めて軸受の良好な潤滑性を確保すると共に、軸受内部に封入されるグリース量を削減して軽量化と低コスト化を図った複列の転がり軸受を提供することができる。   The double-row rolling bearing according to the present invention includes an outer member in which a double-row outer rolling surface is integrally formed on the inner periphery, and a double-row inner rolling bearing that faces the outer rolling surface of the double row on the outer periphery. Formed between the inner member in which a running surface is formed, a double-row rolling element that is rotatably accommodated between the both rolling surfaces via a cage, and the outer member and the inner member. In a double row rolling bearing having a seal mounted in an opening of the annular space and having a predetermined amount of grease sealed in the bearing, an annular base protruding radially is formed at the end of the cage. Since the annular base is opposed to the outer member or the inner member or both via a predetermined radial gap, the grease attached to the periphery of the rolling element and the cage body and to each rolling surface It is possible to regulate the flow to the center of the bearing, and the bearing has a large pitch between rolling elements. To provide double-row rolling bearings that increase the grease usage efficiency to ensure good lubricity of the bearings and reduce the amount of grease enclosed in the bearings to reduce weight and cost. Can do.

内周に円弧状の複列の外側転走面が一体に形成された外輪と、外周に前記複列の外側転走面に対向する円弧状の内側転走面が形成された一対の内輪と、前記両転走面間に保持器を介して転動自在に収容された複列のボールと、前記外輪と内輪との間に形成される環状空間の開口部に装着されたシールとを備え、軸受内部に所定量のグリースが封入された複列のアンギュラ玉軸受において、前記保持器の端部に径方向に突出した環状基部が形成され、この環状基部が前記外輪の内径部および前記内輪の小径側の外径部に０．５〜２．０ｍｍの範囲に設定された径方向隙間を介して対向されている。   An outer ring in which an arc-shaped double row outer rolling surface is integrally formed on the inner periphery, and a pair of inner rings in which an arc-shaped inner rolling surface facing the outer rolling surface of the double row is formed on the outer periphery. A double row of balls accommodated between the rolling surfaces via a cage, and a seal attached to an opening of an annular space formed between the outer ring and the inner ring. In the double-row angular contact ball bearing in which a predetermined amount of grease is sealed inside the bearing, an annular base portion protruding radially is formed at the end of the cage, and the annular base portion is formed by the inner diameter portion of the outer ring and the inner ring. Are opposed to each other through a radial gap set in a range of 0.5 to 2.0 mm.

以下、本発明の実施の形態を図面に基づいて詳細に説明する。
図１は、本発明に係る複列の転がり軸受の第１の実施形態を示す縦断面図、図２は、図１の要部拡大図、図３は、本発明に係る保持器を示す斜視図である。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
1 is a longitudinal sectional view showing a first embodiment of a double row rolling bearing according to the present invention, FIG. 2 is an enlarged view of a main part of FIG. 1, and FIG. 3 is a perspective view showing a cage according to the present invention. FIG.

この複列の転がり軸受１は車輪用軸受装置に用いられ、第１世代と称されている。そして、内周に円弧状の複列の外側転走面２ａ、２ａが形成された外輪（外方部材）２と、外周に前記複列の外側転走面２ａ、２ａに対向する円弧状の内側転走面３ａが形成された一対の内輪（内方部材）３、３と、両転走面間に収容された複列のボール４、４と、これらのボール４を転動自在に保持する保持器５、５と、外輪２の両端部に装着されたシール６、７とを備えている。   This double-row rolling bearing 1 is used in a wheel bearing device and is referred to as a first generation. And the outer ring | wheel (outward member) 2 in which the arcuate double row | line | column outer rolling surface 2a, 2a was formed in the inner periphery, and the circular arc shape facing the said outer surface 2a, 2a of the double row | line | column on the outer periphery A pair of inner rings (inner members) 3, 3 formed with an inner rolling surface 3 a, double row balls 4, 4 accommodated between both rolling surfaces, and holding these balls 4 in a freely rollable manner. Retainers 5 and 5 and seals 6 and 7 attached to both ends of the outer ring 2.

外輪２はＳＵＪ２（ＪＩＳ Ｇ ４８０５）等の高炭素クロム軸受鋼、あるいは浸炭鋼からなり、高炭素クロム軸受鋼は８２０〜８６０℃でズブ焼入れされた後、１６０〜２００℃で焼戻しされ、５８〜６４ＨＲＣの範囲に芯部まで硬化処理されている。また、浸炭鋼の場合は、表面が５８〜６４ＨＲＣの範囲に硬化処理されている。一方、内輪３も外輪２と同様、ＳＵＪ２等の高炭素クロム軸受鋼、あるいは浸炭鋼からなり、高炭素クロム軸受鋼は５８〜６４ＨＲＣの範囲に芯部まで硬化処理され、浸炭鋼の場合は、表面が５８〜６４ＨＲＣの範囲に硬化処理されている。また、ボール４はＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲に硬化処理されている。   The outer ring 2 is made of high carbon chrome bearing steel such as SUJ2 (JIS G 4805) or carburized steel. The high carbon chrome bearing steel is tempered at 820 to 860 ° C. and then tempered at 160 to 200 ° C. The core is hardened in the range of 64 HRC. In the case of carburized steel, the surface is hardened in the range of 58 to 64 HRC. On the other hand, the inner ring 3 is made of high carbon chrome bearing steel such as SUJ2 or carburized steel like the outer ring 2, and the high carbon chrome bearing steel is hardened to the core in the range of 58 to 64 HRC. The surface is cured in the range of 58 to 64 HRC. Further, the ball 4 is made of high carbon chrome bearing steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core part by quenching.

この複列の転がり軸受は、一対の内輪３、３の小径側（正面側）端面３ｂ、３ｂが突き合された状態でセットされ、所謂背面合せタイプの複列のアンギュラ玉軸受を構成している。また、外輪２と内輪３との間に形成された環状空間の開口部にはシール６、７が装着され、軸受内部に封入された潤滑グリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。   This double row rolling bearing is set with the small diameter side (front side) end faces 3b, 3b of the pair of inner rings 3, 3 being abutted against each other, forming a so-called back-to-back type double row angular ball bearing. Yes. Further, seals 6 and 7 are attached to the opening of the annular space formed between the outer ring 2 and the inner ring 3, leakage of the lubricating grease sealed inside the bearing, rainwater, dust, etc. from the outside Is prevented from entering the inside of the bearing.

保持器５は、ＰＡ（ポリアミド）６６等の熱可塑性合成樹脂をベースに、ＧＦ（グラスファイバー）等の強化材を適量含有させたものを射出成形することにより形成されている。この保持器５は、図３に示すように、環状の保持器本体８の一端部に、周方向に一定間隔で対向する２つ一組の保持爪８ａ、８ａが設けられている。この保持爪８ａは互いに接近する方向に湾曲させてその間に凹球面に形成されたポケット９を備えている。また、保持爪８ａの背面間には保持爪８ａが立ち上がる凹部８ｂを有し、適度な弾性を保持爪８ａに付与している。そして、この保持爪８ａを弾性変形させてボール４に装着し、ボール４を所定のポケットすきまを介して包持する、所謂スナップオンタイプで構成されている。   The cage 5 is formed by injection molding a material containing an appropriate amount of reinforcing material such as GF (glass fiber) based on a thermoplastic synthetic resin such as PA (polyamide) 66. As shown in FIG. 3, the retainer 5 is provided with a pair of retaining claws 8 a and 8 a that are opposed to each other at a constant interval in the circumferential direction at one end of an annular retainer body 8. The holding claw 8a is provided with a pocket 9 which is curved in a direction approaching each other and formed in a concave spherical surface therebetween. Further, a recess 8b where the holding claw 8a rises is provided between the back surfaces of the holding claw 8a, and appropriate elasticity is imparted to the holding claw 8a. The holding claw 8a is elastically deformed and attached to the ball 4, and is configured as a so-called snap-on type in which the ball 4 is held through a predetermined pocket clearance.

ここで、本実施形態では、環状の保持器本体８の他端部に径方向に突出して形成された環状基部１０が形成されている。この環状基部１０は、図２に示すように、外輪２の内径部２ｂに所定の径方向隙間（片側）ｅ１を介して対向する外側突起１０ａと、内輪３の小径側の外径部３ｃに所定の径方向隙間（片側）ｅ２を介して対向する内側突起１０ｂで構成されている。   Here, in the present embodiment, an annular base portion 10 formed to protrude in the radial direction is formed at the other end portion of the annular cage body 8. As shown in FIG. 2, the annular base portion 10 is formed on an outer protrusion 10 a that opposes the inner diameter portion 2 b of the outer ring 2 via a predetermined radial gap (one side) e 1 and an outer diameter portion 3 c on the smaller diameter side of the inner ring 3. It is comprised by the inner side protrusion 10b which opposes via predetermined radial direction clearance (one side) e2.

この環状基部１０によってボール４や保持器本体８の周辺および各転走面２ａ、３ａに付着したグリースが軸受中央部、すなわち、外輪２の内径部２ｂや内輪３の小径側の外径部３ｃに流動するのを規制している。したがって、ボール４、４間のピッチが大きな軸受であっても、グリースの使用効率を高めて軸受の良好な潤滑性を確保すると共に、軸受内部に封入されるグリース量を削減して軽量化と低コスト化を図った複列の転がり軸受を提供することができる。   The grease attached to the periphery of the balls 4 and the cage body 8 and the rolling surfaces 2a and 3a by the annular base 10 is the bearing central portion, that is, the inner diameter portion 2b of the outer ring 2 and the outer diameter portion 3c on the smaller diameter side of the inner ring 3. The flow is controlled. Therefore, even for a bearing having a large pitch between the balls 4 and 4, the use efficiency of the grease is increased to ensure good lubricity of the bearing, and the amount of grease enclosed in the bearing is reduced to reduce the weight. It is possible to provide a double-row rolling bearing that achieves cost reduction.

なお、外輪２の内径部２ｂと外側突起１０ａとの径方向隙間ｅ１および内輪３の外径部３ｂと内側突起１０ｂとの径方向隙間ｅ２は、０．５〜２．０ｍｍの範囲、好ましくは、０．５〜１．５ｍｍの範囲に設定されている。この径方向隙間ｅ１、ｅ２が０．５ｍｍ未満だと、保持器５と外輪２あるいは内輪３の寸法公差の関係で両者が接触して保持器５の摩耗が生じると共に、保持器５の挙動が拘束されて好ましくない。一方、径方向隙間ｅ１、ｅ２が２．０ｍｍを超えると、グリースの流動を規制する効果が少なくなるからである。ここでは、第１世代構造を例示したが、本発明はこれに限らず、第２世代乃至第４世代構造にも適用することができる。   The radial gap e1 between the inner diameter part 2b of the outer ring 2 and the outer protrusion 10a and the radial gap e2 between the outer diameter part 3b of the inner ring 3 and the inner protrusion 10b are in the range of 0.5 to 2.0 mm, preferably , 0.5 to 1.5 mm. If the radial clearances e1 and e2 are less than 0.5 mm, the cage 5 and the outer ring 2 or the inner ring 3 come into contact with each other due to the dimensional tolerance, and the cage 5 is worn. It is not preferable because it is restrained. On the other hand, when the radial gaps e1 and e2 exceed 2.0 mm, the effect of regulating the flow of grease is reduced. Here, the first generation structure is illustrated, but the present invention is not limited to this, and can be applied to second generation to fourth generation structures.

ここでは、車輪用軸受装置に使用される複列の転がり軸受として複列のアンギュラ玉軸受について詳述したが、本発明に係る複列の転がり軸受は、これに限らず、複列の円錐ころ軸受を適用することができる。図４は、本発明に係る複列の転がり軸受の第２の実施形態を示す縦断面図である。なお、前述した実施形態と同一部位、同一部品、あるいは同一の機能を有する部品、部位には同じ符号を付けて重複した説明を省略する。   Here, the double-row angular contact ball bearing has been described in detail as a double-row rolling bearing used in the wheel bearing device. However, the double-row rolling bearing according to the present invention is not limited to this, and the double-row tapered roller is not limited thereto. Bearings can be applied. FIG. 4 is a longitudinal sectional view showing a second embodiment of the double row rolling bearing according to the present invention. In addition, the same site | part, the same component as the embodiment mentioned above, the part which has the same function, and a site | part are attached | subjected with the same code | symbol, and the overlapping description is abbreviate | omitted.

この複列の転がり軸受１１は、内周にテーパ状の複列の外側転走面１２ａ、１２ａが形成された外輪１２と、この複列の外側転走面１２ａ、１２ａに対向するテーパ状の内側転走面１３ａが外周に形成された一対の内輪１３、１３と、これら両転走面間に収容された複列の円錐ころ１４、１４と、これら複列の円錐ころ１４、１４を転動自在に保持する保持器１５、１５とを備え、一対の内輪１３、１３の小径側端面１３ｂ、１３ｂが突き合された状態でセットされた背面合せタイプの複列の円錐ころ軸受を構成している。そして、外輪１２と内輪１３との間に形成される環状空間の開口部にシール１６、１７が装着され、軸受内部に封入された潤滑グリースの漏洩と、外部から軸受内部に雨水やダスト等が侵入するのを防止している。   This double row rolling bearing 11 has an outer ring 12 in which tapered double row outer raceway surfaces 12a and 12a are formed on the inner periphery, and a tapered shape facing the double row outer raceway surfaces 12a and 12a. A pair of inner rings 13, 13 having an inner rolling surface 13 a formed on the outer periphery, double row tapered rollers 14, 14 accommodated between both rolling surfaces, and these double row tapered rollers 14, 14 are rolled. A back-to-back type double row tapered roller bearing set with the small-diameter side end faces 13b and 13b of the pair of inner rings 13 and 13 in contact with each other. ing. Seals 16 and 17 are attached to the opening of the annular space formed between the outer ring 12 and the inner ring 13, leakage of the lubricating grease sealed inside the bearing, and rainwater, dust, etc. from the outside inside the bearing. Preventing intrusion.

外輪１２はＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲で硬化処理されている。一方、内輪１２および円錐ころ１４は、外輪１２と同様、ＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲で硬化処理されている。   The outer ring 12 is made of a high carbon chrome bearing steel such as SUJ2, and is hardened in the range of 58 to 64 HRC to the core portion by quenching. On the other hand, the inner ring 12 and the tapered roller 14 are made of a high carbon chrome bearing steel such as SUJ2 like the outer ring 12, and are hardened in the range of 58 to 64 HRC to the core part by quenching.

内輪１３の内側転走面１３ａの大径側には大鍔１３ｃが一体に形成され、円錐ころ１４の大端面に摺接してこの円錐ころ１４を案内している。また、内側転走面１３ａの小径側には小鍔１３ｄが一体に形成され、円錐ころ１４が脱落するのを防止している。   A large collar 13c is integrally formed on the large diameter side of the inner raceway surface 13a of the inner ring 13, and guides the tapered roller 14 in sliding contact with the large end surface of the tapered roller 14. Further, a small flange 13d is integrally formed on the small diameter side of the inner rolling surface 13a to prevent the tapered roller 14 from dropping off.

また、一対の内輪１３、１３の小径端部の内周には環状溝１８がそれぞれ形成され、この環状溝１８に連結環１９が装着されている。この連結環１９は、鋼板をプレス加工によって断面が略コの字状に、全体として円環状に形成され、輸送中に内輪１３が分離するのを防止すると共に、図示しないハブ輪から一対の内輪１３、１３を引き抜く際、一方の内輪１３がハブ輪に残らないように一対の内輪１３、１３を所定の抜け耐力をもって連結している。   An annular groove 18 is formed on the inner circumference of the small diameter end portion of the pair of inner rings 13, 13, and a connecting ring 19 is attached to the annular groove 18. The connection ring 19 is formed by pressing a steel plate into a substantially U-shaped cross section and is formed into an annular shape as a whole, preventing the inner ring 13 from being separated during transportation, and a pair of inner rings from a hub ring (not shown). When pulling out 13, 13, the pair of inner rings 13, 13 are connected with a predetermined pull-out strength so that one inner ring 13 does not remain on the hub ring.

保持器１５は、ＰＡ６６等の熱可塑性合成樹脂をベースに、ＧＦ等の強化材を適量含有させたものを射出成形することにより形成されている。この保持器１５は、傾斜したケージ状に形成された環状の保持器本体２０と環状基部２１とで構成されている。保持器本体２０には、周方向に一定間隔で開口されたポケット２２を備えている。   The cage 15 is formed by injection molding a material containing an appropriate amount of a reinforcing material such as GF based on a thermoplastic synthetic resin such as PA66. The cage 15 is composed of an annular cage body 20 and an annular base 21 formed in an inclined cage shape. The cage body 20 includes pockets 22 that are opened at regular intervals in the circumferential direction.

ここで、本実施形態では、保持器１５の環状基部２１に、外輪１２の内径部１２ｂに所定の径方向隙間（片側）ｅ１を介して対向する外側突起２１ａと、内輪１３の小径側の外径部１３ｄに所定の径方向隙間（片側）ｅ２を介して対向する内側突起２１ｂが形成されている。   Here, in the present embodiment, the outer base 21 of the retainer 15, the outer protrusion 21 a facing the inner diameter portion 12 b of the outer ring 12 via a predetermined radial gap (one side) e 1, and the outer diameter of the inner ring 13 on the smaller diameter side. An inner protrusion 21b is formed opposite to the diameter portion 13d via a predetermined radial gap (one side) e2.

これら外側突起２１ａと内側突起２１ｂによって円錐ころ１４や保持器１５の周辺および各転走面１２ａ、１３ａに付着したグリースが軸受中央部、すなわち、外輪１２の内径部１２ｂや内輪１３の小径側の外径部１３ｄに流動するのを規制している。したがって、円錐ころ１４、１４間のピッチが大きな軸受であっても、グリースの使用効率を高めて軸受の良好な潤滑性を確保すると共に、軸受内部に封入されるグリース量を削減して軽量化と低コスト化を図ることができる。   The grease attached to the periphery of the tapered roller 14 and the retainer 15 and the rolling surfaces 12a and 13a by the outer protrusions 21a and the inner protrusions 21b is formed at the bearing central portion, that is, the inner diameter portion 12b of the outer ring 12 and the smaller diameter side of the inner ring 13. The flow to the outer diameter portion 13d is restricted. Therefore, even if the pitch between the tapered rollers 14 and 14 is a large bearing, the use efficiency of grease is increased to ensure good lubricity of the bearing, and the amount of grease enclosed in the bearing is reduced to reduce the weight. And cost reduction.

以上、本発明の実施の形態について説明を行ったが、本発明はこうした実施の形態に何等限定されるものではなく、あくまで例示であって、本発明の要旨を逸脱しない範囲内において、さらに種々なる形態で実施し得ることは勿論のことであり、本発明の範囲は、特許請求の範囲の記載によって示され、さらに特許請求の範囲に記載の均等の意味、および範囲内のすべての変更を含む。   The embodiment of the present invention has been described above, but the present invention is not limited to such an embodiment, and is merely an example, and various modifications can be made without departing from the scope of the present invention. Of course, the scope of the present invention is indicated by the description of the scope of claims, and further, the equivalent meanings described in the scope of claims and all modifications within the scope of the scope of the present invention are included. Including.

本発明に係る転がり軸受は、例えば、車輪用軸受装置に使用され、車輪を回転自在に支承する複列の転がり軸受に適用することができる。   The rolling bearing according to the present invention is used in, for example, a wheel bearing device, and can be applied to a double row rolling bearing that rotatably supports a wheel.

本発明に係る複列の転がり軸受の第１の実施形態を示す縦断面図である。1 is a longitudinal sectional view showing a first embodiment of a double row rolling bearing according to the present invention. 図１の要部拡大図である。It is a principal part enlarged view of FIG. 本発明に係る保持器を示す斜視図である。It is a perspective view showing the maintenance machine concerning the present invention. 本発明に係る複列の転がり軸受の第２の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 2nd Embodiment of the double row rolling bearing which concerns on this invention. 従来の複列の転がり軸受を示す縦断面図である。It is a longitudinal cross-sectional view which shows the conventional double row rolling bearing. 図５の要部拡大図である。It is a principal part enlarged view of FIG.

符号の説明Explanation of symbols

１、１１・・・・・・・・複列の転がり軸受
２、１２・・・・・・・・外輪
２ａ、１２ａ・・・・・・外側転走面
２ｂ・・・・・・・・・・内径部
３、１２・・・・・・・・内輪
３ａ、１３ａ・・・・・・内側転走面
３ｂ、１３ｂ・・・・・・小径側端面
３ｃ・・・・・・・・・・外径部
４・・・・・・・・・・・ボール
５、１５・・・・・・・・保持器
６、７、１６、１７・・・シール
８、２０・・・・・・・・保持器本体
８ａ・・・・・・・・・・保持爪
８ｂ・・・・・・・・・・凹部
９、２２・・・・・・・・ポケット
１０、２１・・・・・・・環状基部
１０ａ、２１ａ・・・・・外側突起
１０ｂ、２１ｂ・・・・・内側突起
１３ｃ・・・・・・・・・大鍔
１３ｄ・・・・・・・・・小鍔
１４・・・・・・・・・・円錐ころ
１８・・・・・・・・・・環状溝
１９・・・・・・・・・・連結環
５０・・・・・・・・・・複列の転がり軸受
５１・・・・・・・・・・外輪
５１ａ・・・・・・・・・外側転走面
５２・・・・・・・・・・内輪
５２ａ・・・・・・・・・内側転走面
５３・・・・・・・・・・ボール
５４・・・・・・・・・・保持器
５５、５６・・・・・・・シール
５７・・・・・・・・・・グリース
ｅ１、ｅ２・・・・・・・径方向隙間 1, 11 ... Double-row rolling bearings 2, 12 ... Outer rings 2a, 12a ... Outer rolling surface 2b ...・ ・ Inner diameter part 3, 12 ・ ・ ・ ・ ・ ・ ・ ・ Inner ring 3a, 13a ・ ・ ・ ・ ・ ・ ・ ・ Inner rolling surface 3b, 13b ・ ・ ・ ・ ・ ・ ・ ・ Small diameter side end face 3c ・ ・ ・ ・ ・ ・ ・ ・・ ・ Outer diameter part 4 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Ball 5, 15 ・ ・ ・ ・ ・ ・ ・ ・ Retainer 6, 7, 16, 17 ・ ・ ・ Seal 8, 20 ... ... Retainer body 8a ... Retaining claw 8b ... Recesses 9, 22 ... Pockets 10, 21 ... ... Roller base 10a, 21a ... Outer protrusion 10b, 21b ... Inner protrusion 13c ... ..... tapered rollers 18 ... ·················································· 50 ········· Outer rolling surface 52 ······················································· Ball 54 ... Cage 55, 56 ... Seal 57 ... Grease e1, e2 ... Radial clearance

Claims (5)

内周に複列の外側転走面が一体に形成された外方部材と、
外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、
前記両転走面間に保持器を介して転動自在に収容された複列の転動体と、
前記外方部材と内方部材との間に形成される環状空間の開口部に装着されたシールとを備え、
軸受内部に所定量のグリースが封入された複列の転がり軸受において、
前記保持器の端部に径方向に突出した環状基部が形成され、この環状基部が前記外方部材または内方部材あるいはその両方に所定の径方向隙間を介して対向されていることを特徴とする複列の転がり軸受。 An outer member in which a double row outer rolling surface is integrally formed on the inner periphery;
An inner member in which a double row inner rolling surface facing the outer row rolling surface of the double row is formed on the outer periphery;
A double-row rolling element accommodated between the rolling surfaces via a cage, and capable of rolling freely;
A seal attached to an opening of an annular space formed between the outer member and the inner member;
In double row rolling bearings where a predetermined amount of grease is sealed inside the bearing,
An annular base portion projecting in a radial direction is formed at an end portion of the cage, and the annular base portion is opposed to the outer member or the inner member or both via a predetermined radial gap. Double row rolling bearing. 前記径方向隙間が０．５〜２．０ｍｍの範囲に設定されている請求項１に記載の複列の転がり軸受。   The double-row rolling bearing according to claim 1, wherein the radial clearance is set in a range of 0.5 to 2.0 mm. 前記複列の転がり軸受が複列のアンギュラ玉軸受で構成され、前記内方部材が、外周に円弧状の内側転走面が形成された一対の内輪からなり、これらの内輪の小径側端面が突き合された状態でセットされた背面合せタイプで構成されている請求項１または２に記載の複列の転がり軸受。   The double-row rolling bearing is composed of a double-row angular contact ball bearing, and the inner member is composed of a pair of inner rings in which an arc-shaped inner rolling surface is formed on the outer periphery, and the end faces on the small diameter side of these inner rings are The double row rolling bearing according to claim 1, wherein the double row rolling bearing is configured as a back-to-back type set in a face-to-face state. 前記保持器が熱可塑性合成樹脂を射出成形することにより形成され、環状の保持器本体の一端部に、周方向に一定間隔で対向する２つ一組の保持爪が設けられ、これら保持爪の間に凹球面に形成されたポケットを備えたスナップオンタイプで構成されている請求項３に記載の複列の転がり軸受。   The retainer is formed by injection-molding a thermoplastic synthetic resin, and one pair of retaining claws facing each other in the circumferential direction is provided at one end of the annular retainer body. The double-row rolling bearing according to claim 3, wherein the double-row rolling bearing is configured as a snap-on type having pockets formed in a concave spherical surface therebetween. 前記複列の転がり軸受が複列の円錐ころ軸受で構成され、前記内方部材が、外周にテーパ状の内側転走面が形成された一対の内輪からなり、これら内輪の内側転走面の大径側に前記円錐ころを案内する大鍔が形成され、前記内輪の小径側端面が突き合された状態でセットされた背面合せタイプで構成されている請求項１または２に記載の複列の転がり軸受。   The double-row rolling bearing is composed of a double-row tapered roller bearing, and the inner member is composed of a pair of inner rings having a tapered inner rolling surface formed on the outer periphery. The double row according to claim 1 or 2, wherein a large collar for guiding the tapered roller is formed on the large diameter side, and the back ring type is set in a state where the small diameter side end surfaces of the inner rings are abutted. Rolling bearings.
JP2006316602A 2006-11-24 2006-11-24 Double row rolling bearing Pending JP2008128421A (en)

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Publication number Priority date Publication date Assignee Title
WO2018074199A1 (en) * 2016-10-17 2018-04-26 日本精工株式会社 Retainer for angular ball bearings
JP2019074214A (en) * 2014-03-28 2019-05-16 日本精工株式会社 Angular ball bearing and its manufacturing method

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Publication number Priority date Publication date Assignee Title
JPS57124618A (en) * 1981-01-24 1982-08-03 Pegasus Kiyandoru Kk Ornamental candle
JPS58161226A (en) * 1982-03-18 1983-09-24 シャープ株式会社 Latch relay driving circuit
JP2002235751A (en) * 2001-02-13 2002-08-23 Nsk Ltd Rolling bearing

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57124618A (en) * 1981-01-24 1982-08-03 Pegasus Kiyandoru Kk Ornamental candle
JPS58161226A (en) * 1982-03-18 1983-09-24 シャープ株式会社 Latch relay driving circuit
JP2002235751A (en) * 2001-02-13 2002-08-23 Nsk Ltd Rolling bearing

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019074214A (en) * 2014-03-28 2019-05-16 日本精工株式会社 Angular ball bearing and its manufacturing method
WO2018074199A1 (en) * 2016-10-17 2018-04-26 日本精工株式会社 Retainer for angular ball bearings
JP2018066385A (en) * 2016-10-17 2018-04-26 日本精工株式会社 Cage for angular ball bearing, angular ball bearing and bearing device
CN109844336A (en) * 2016-10-17 2019-06-04 日本精工株式会社 Angular contact ball bearing retainer, angular contact ball bearing and bearing arrangement

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