JP2008151181A - Roller bearing - Google Patents

Roller bearing Download PDF

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Publication number
JP2008151181A
JP2008151181A JP2006337203A JP2006337203A JP2008151181A JP 2008151181 A JP2008151181 A JP 2008151181A JP 2006337203 A JP2006337203 A JP 2006337203A JP 2006337203 A JP2006337203 A JP 2006337203A JP 2008151181 A JP2008151181 A JP 2008151181A
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Japan
Prior art keywords
cage
retainer
outer diameter
rolling bearing
outer ring
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Pending
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JP2006337203A
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Japanese (ja)
Inventor
Futoshi Kosugi
太 小杉
Satoshi Kuruhara
聡 来原
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2006337203A priority Critical patent/JP2008151181A/en
Publication of JP2008151181A publication Critical patent/JP2008151181A/en
Pending legal-status Critical Current

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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
    • F16C33/38—Ball cages
    • F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
    • 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
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3843—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F16C33/3856—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window 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
    • F16C33/6607—Retaining the grease in or near the bearing
    • F16C33/6614—Retaining the grease in or near the bearing in recesses or cavities provided in retainers, races or 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
    • 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
    • F16C19/16—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 a single row of balls
    • F16C19/163—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 a single row of balls with angular contact

Abstract

<P>PROBLEM TO BE SOLVED: To provide a roller bearing which can prevent retainer noise from being generated by stabilizing the lubricating state of a retainer guide surface, and prevent retainer deformation caused by a centrifugal force applied to the retainer, furthermore, smoothly rotate a ball held by the retainer by guiding it stably, additionally, reduce its manufacturing cost. <P>SOLUTION: A retainer 5 is guided by the inner circumference surface 6 of an outer ring 3, and an annular grease sump recess 7 is formed at an end among guide surfaces of retainer outer diameters 5D guided by the inner circumference surface 6. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

この発明は、例えば、高速回転する工作機械主軸等を支持するアンギュラ玉軸受等に好適に適用される技術に関する。   The present invention relates to a technique suitably applied to, for example, an angular ball bearing that supports a machine tool main shaft or the like that rotates at high speed.

高速回転する工作機械主軸等を支持するアンギュラ玉軸受が実用に供されている。このアンギュラ玉軸受は、例えば、図８に示すような外輪案内型の保持器８０が適用される。この外輪案内型の保持器８０は、保持器外径面８０ａが外輪内径面で案内される。この案内面８１の潤滑状態が不安定になると、保持器音を発生しやすい。そのため、次のような構造が採用されていた（例えば、特許文献１参照）。   Angular contact ball bearings that support machine tool spindles and the like that rotate at high speed are in practical use. For example, an outer ring guide type cage 80 as shown in FIG. 8 is applied to this angular ball bearing. In the outer ring guide type cage 80, the cage outer diameter surface 80a is guided by the outer ring inner diameter surface. If the lubrication state of the guide surface 81 becomes unstable, a cage sound is likely to be generated. For this reason, the following structure has been adopted (see, for example, Patent Document 1).

前記構造を図９、図１０と共に説明する。図９に示すように、外輪内径面に、半径方向外方に凹む凹部８２が形成され、該凹部８２に潤滑剤８３を保持させている。これにより、案内面８４の摩耗や焼付き等の潤滑不良を抑制している。また図１０に示すように、外輪案内型のアンギュラ玉軸受において、組込まれる保持器８５の外径面に、半径方向内方に凹む断面凹形状の貯油周溝８５ａを設け、この貯油周溝８５ａに油を保持し、潤滑に寄与させる技術が開示されている。   The said structure is demonstrated with FIG. 9, FIG. As shown in FIG. 9, a recess 82 that is recessed outward in the radial direction is formed on the inner surface of the outer ring, and a lubricant 83 is held in the recess 82. Thereby, poor lubrication such as wear and seizure of the guide surface 84 is suppressed. As shown in FIG. 10, in the outer ring guide type angular contact ball bearing, an oil storage circumferential groove 85a having a concave cross section that is recessed inward in the radial direction is provided on the outer diameter surface of the cage 85 to be incorporated, and this oil storage circumferential groove 85a. A technique for retaining oil and contributing to lubrication is disclosed.

特開２００６−１１８５２５号公報JP 2006-118525 A

前述の外輪内径面に凹部を形成して、この凹部に潤滑剤を保持させる技術では、外輪内径面を加工する工数が大きく、軸受の製造コストが高くつく。前述の保持器の外径面に、断面凹形状の貯油周溝を設ける技術では、保持器に高速で遠心力が加わった場合、図１１に示すように、該保持器が半径方向外方に凸形状に変形することが懸念される。このように保持器が変形すると、保持器に保持される玉の案内を不安定にし、円滑な玉の回転を阻害し、回転不具合に繋がるおそれがある。   In the above-described technology for forming a recess in the inner surface of the outer ring and retaining the lubricant in the recess, the man-hour for processing the inner surface of the outer ring is large, and the manufacturing cost of the bearing is high. In the technique of providing the oil storage circumferential groove having a concave cross section on the outer diameter surface of the cage, when the centrifugal force is applied to the cage at a high speed, the cage is radially outward as shown in FIG. There is concern about deformation into a convex shape. When the cage is deformed in this manner, the guidance of the balls held by the cage is unstable, and smooth rotation of the balls may be hindered, leading to a rotation failure.

本発明の目的は、保持器案内面の潤滑状態を安定化して保持器音の発生を抑えると共に、保持器に作用する遠心力に起因する保持器変形を防止し、保持器に保持される玉を安定して案内させて円滑に回転させる転がり軸受であって、その製造コストの低減を図ることができる転がり軸受を提供することである。   An object of the present invention is to stabilize the lubrication state of the cage guide surface to suppress the generation of cage noise, to prevent cage deformation due to centrifugal force acting on the cage, and to hold the ball held by the cage. It is a rolling bearing that stably guides and rotates smoothly, and that can reduce the manufacturing cost.

この発明の転がり軸受は、内輪と外輪との間に、保持器に保持された玉を介在させた転がり軸受において、前記保持器は、外輪の内周面に案内されるものであり、且つ、この内周面に案内される保持器外径の案内面のうち端部に、環状のグリース溜り凹部を設けたことを特徴とする。   The rolling bearing of the present invention is a rolling bearing in which a ball held by a cage is interposed between an inner ring and an outer ring, and the cage is guided to an inner peripheral surface of the outer ring, and An annular grease retaining recess is provided at the end of the guide surface having the outer diameter of the cage guided by the inner peripheral surface.

この構成によると、軸受運転時において、外輪の内周面に保持器外径が案内される。また、保持器外径の案内面のうち端部に設けられた環状のグリース溜り凹部によって、保持器の案内面積を減少させると共に、このグリース溜り凹部に、潤滑剤であるグリースが溜まることで、案内面にグリースが行き届き易くなる。換言すれば、案内面に存在するグリースは、グリース溜り凹部に溜まるグリース自体によって阻止され、保持器外径の案内面の端部から軸受側方に飛散し難くなる。よって、案内面の摩耗や焼き付き等の潤滑不良を防止することができ、保持器音の発生を抑えることができる。
特に、保持器外径の案内面のうち端部に、環状のグリース溜り凹部を設けたので、保持器の剛性強度が低くなり過ぎず、軸受運転時に保持器に作用する遠心力に起因して当該保持器が不所望に変形することを防止することができる。また、外輪内径面に凹部を加工する前述の従来技術よりも工数低減が可能となり、製造コストの低減を図ることが可能となる。 According to this configuration, the outer diameter of the cage is guided to the inner peripheral surface of the outer ring during bearing operation. In addition, by reducing the guide area of the cage by the annular grease reservoir recess provided at the end of the guide surface of the outer diameter of the cage, grease as a lubricant is accumulated in the grease reservoir recess. Grease easily reaches the guide surface. In other words, the grease existing on the guide surface is blocked by the grease itself that accumulates in the grease reservoir recess, and is difficult to be scattered from the end portion of the guide surface having the outer diameter of the cage to the bearing side. Therefore, poor lubrication such as wear and seizure of the guide surface can be prevented, and generation of cage noise can be suppressed.
In particular, since the annular grease reservoir recess is provided at the end of the guide surface of the outer diameter of the cage, the rigidity strength of the cage does not become too low, resulting from the centrifugal force acting on the cage during bearing operation. It is possible to prevent the retainer from being undesirably deformed. Further, the number of steps can be reduced as compared with the above-described conventional technique in which the recess is formed on the inner surface of the outer ring, and the manufacturing cost can be reduced.

この発明において、前記保持器の環状のグリース溜り凹部は、保持器外径に対し、半径方向内方に段差を有する段差部であることが望ましい。この構成によると、グリース溜り凹部の形状を簡単化し、金型、後加工のいずれによっても、このグリース溜り凹部を容易に形成することができる。   In this invention, it is desirable that the annular grease retaining recess of the cage is a step portion having a step inward in the radial direction with respect to the outer diameter of the cage. According to this configuration, the shape of the grease reservoir recess can be simplified, and the grease reservoir recess can be easily formed by either a mold or post-processing.

この発明において、前記保持器のうち、保持器外径から段差部の外周面までの段差寸法を、保持器外径から保持器内径までの半径方向寸法の１／２以下に規定することが望ましい。この構成によると、段差寸法を、保持器外径から保持器内径までの前記半径方向寸法の１／２よりも大きくすると、保持器の剛性強度が小さくなり、保持器の変形を引き起こすおそれがある。段差寸法を保持器リング幅の１／２以下にした場合には、保持器の剛性強度の低下を極力抑え、その変形を未然に防止することができる。   In the present invention, among the cages, it is desirable that the step size from the cage outer diameter to the outer peripheral surface of the step portion is defined to be 1/2 or less of the radial dimension from the cage outer diameter to the cage inner diameter. . According to this configuration, if the step size is larger than ½ of the radial dimension from the outer diameter of the cage to the inner diameter of the cage, the rigidity strength of the cage is reduced, which may cause deformation of the cage. . When the step size is ½ or less of the cage ring width, it is possible to suppress a reduction in the rigidity strength of the cage as much as possible, and to prevent the deformation.

この発明において、前記保持器は樹脂製であることが望ましい。この構成によると、工作機械主軸等を支持するアンギュラ玉軸受等のように高速回転（ピッチ円直径ｄｍに回転速度ｎを乗じたいわゆるｄｍｎ値が、例えば１４０万）しても、保持器の軽量性および樹脂材料の有する自己潤滑性により、潤滑不良となるおそれを低減することができる。   In the present invention, the cage is preferably made of resin. According to this configuration, the weight of the cage can be reduced even when rotating at high speed (the so-called dmn value obtained by multiplying the rotational speed n by the pitch circle diameter dm is, for example, 1.4 million) such as an angular ball bearing that supports the spindle of the machine tool and the like. The possibility of poor lubrication can be reduced by the self-lubricating property and the resin material.

この発明の転がり軸受によると、保持器外径の案内面のうち端部に、環状のグリース溜り凹部を設けたので、保持器の案内面積を減少させ、保持器案内面の潤滑状態を安定化して保持器音の発生を抑えることができる。これと共に、保持器に作用する遠心力に起因する保持器変形を防止し、保持器に保持される玉を安定して案内させて円滑に回転させることができる。また、外輪内径面に凹部を加工する前述の従来技術よりも、製造コストの低減を図ることが可能となる。   According to the rolling bearing of the present invention, since the annular grease retaining recess is provided at the end of the guide surface having the outer diameter of the cage, the guide area of the cage is reduced and the lubrication state of the cage guide surface is stabilized. The generation of cage noise can be suppressed. At the same time, the cage deformation caused by the centrifugal force acting on the cage can be prevented, and the balls held by the cage can be stably guided and rotated smoothly. Further, the manufacturing cost can be reduced as compared with the above-described conventional technique in which the concave portion is processed on the inner surface of the outer ring.

この発明の第１の実施形態を図１〜図４と共に説明する。この第１の実施形態に係る転がり軸受１は、アンギュラ玉軸受に適用される。この転がり軸受１は、内輪２と外輪３との間に玉４を介在させたものであり、グリース潤滑で使用される。玉４は、保持器５によって、周方向に所定の間隔で転動自在に保持されている。内輪２の外周面および外輪３の内周面には、玉４との接触角が予め定める角度となるように、軌道溝２ａ、軌道溝３ａがそれぞれ設けられている。   A first embodiment of the present invention will be described with reference to FIGS. The rolling bearing 1 according to the first embodiment is applied to an angular ball bearing. This rolling bearing 1 has a ball 4 interposed between an inner ring 2 and an outer ring 3 and is used for grease lubrication. The balls 4 are held by a cage 5 so as to roll freely at a predetermined interval in the circumferential direction. A raceway groove 2 a and a raceway groove 3 a are provided on the outer peripheral surface of the inner ring 2 and the inner peripheral surface of the outer ring 3 so that the contact angle with the ball 4 is a predetermined angle.

保持器５は、リング状で全周において肉厚（後述するリング幅）が一定となるように形成されている。この保持器５の幅方向中央に、玉４を転動可能に保持する円筒孔状のポケット５ａが形成されている。該ポケット５ａは円周方向一定間隔おきに複数配設されている（図４参照）。この保持器５は、樹脂材料からなり、且つ外輪３の内周面６に案内されるものである。この保持器５を案内する外輪３の内周面６における外輪案内面６ａとなる部分は、軌道溝３ａの軸方向両側に設けられている。前記外輪３の内周面６は、円筒面状とされ、いわゆるカウンタボアは設けられていない。外輪３の内周面６に案内される保持器外径５Ｄの案内面のうち、軸方向一端部および他端部（図１の左右）に、環状のグリース溜り凹部７，７が設けられている。これらグリース溜り凹部７，７は、保持器５の幅方向中心位置に対し左右対称に構成されている。したがって、軸方向一端部のグリース溜り凹部７について符号を付して説明し、軸方向他端部のグリース溜り凹部７は、軸方向一端部のグリース溜り凹部に付した符号と同一の符号を付して、その説明を省略する。なお、これらグリース溜り凹部７は左右対称の構成に限定されるものではない。   The cage 5 is formed in a ring shape so that the wall thickness (ring width described later) is constant over the entire circumference. A cylindrical hole-shaped pocket 5 a that holds the ball 4 in a rollable manner is formed at the center in the width direction of the cage 5. A plurality of pockets 5a are arranged at regular intervals in the circumferential direction (see FIG. 4). The cage 5 is made of a resin material and is guided to the inner peripheral surface 6 of the outer ring 3. The portions of the inner peripheral surface 6 of the outer ring 3 that guides the cage 5 that serve as the outer ring guide surface 6a are provided on both axial sides of the raceway groove 3a. The inner peripheral surface 6 of the outer ring 3 has a cylindrical surface shape, and no so-called counterbore is provided. Out of the guide surface of the cage outer diameter 5D guided by the inner peripheral surface 6 of the outer ring 3, annular grease reservoir recesses 7, 7 are provided at one end and the other end (left and right in FIG. 1) in the axial direction. Yes. These grease reservoir recesses 7 and 7 are configured symmetrically with respect to the center position in the width direction of the cage 5. Accordingly, the grease reservoir recess 7 at one end in the axial direction will be described with reference numerals, and the grease reservoir recess 7 at the other end in the axial direction will be denoted by the same reference numerals as those attached to the grease reservoir recesses at one end in the axial direction. Therefore, the description is omitted. Note that these grease reservoir recesses 7 are not limited to a symmetrical configuration.

グリース溜り凹部７は、保持器外径５Ｄに対し、半径方向内方に予め定める距離段差を有する段差部７Ａである。保持器外径５Ｄから段差部７Ａの外周面までの段差寸法ｄ１は、保持器外径５Ｄから保持器内径５Ｉまでの半径方向寸法ＲＨ（「保持器リング幅ＲＨ」ともいう）の１／２以下に規定されている。前記段差寸法ｄ１を、保持器リング幅ＲＨの１／２よりも大きくすると、保持器５の剛性強度が小さくなり、保持器５の変形を引き起こすおそれがある。本実施形態では、段差寸法ｄ１を保持器リング幅ＲＨの１／２以下にしているため、保持器５の剛性強度の低下を極力抑え、その変形を未然に防止し得る。段差部７Ａのうち軸方向に垂直な壁部８から保持器端部９までの幅方向寸法ｈ１は、例えば、当該保持器５の柱幅Ｗｈの１／２よりもやや大きくなるように規定されている。ただし、この幅方向寸法ｈ１に限定されるものではない。   The grease reservoir recess 7 is a step portion 7A having a predetermined distance step radially inward with respect to the cage outer diameter 5D. The step dimension d1 from the cage outer diameter 5D to the outer peripheral surface of the stepped portion 7A is ½ of the radial dimension RH (also referred to as “cage ring width RH”) from the cage outer diameter 5D to the cage inner diameter 5I. It is defined below. When the step size d1 is larger than ½ of the cage ring width RH, the rigidity of the cage 5 is reduced, and the cage 5 may be deformed. In the present embodiment, since the step size d1 is set to ½ or less of the cage ring width RH, a decrease in the rigidity strength of the cage 5 can be suppressed as much as possible, and deformation thereof can be prevented. Of the stepped portion 7A, the width direction dimension h1 from the wall portion 8 perpendicular to the axial direction to the cage end 9 is defined to be slightly larger than 1/2 of the column width Wh of the cage 5, for example. ing. However, it is not limited to this width direction dimension h1.

内輪２の外周面において、軌道溝２ａの片側に、外径が端面に向かうに従って次第に小径となるカウンタボア１０が設けられている。該カウンタボア１０は、前記外周面のうち、接触角の生じる方向と反対側部分に設けられている。軸受組立時において、この転がり軸受１は、玉４が組付けられた外輪３を加熱することによって、該外輪３を半径方向外方に所定小距離膨張させ、カウンタボア１０側から軸方向に内輪２を挿入することにより組付け得る。   On the outer peripheral surface of the inner ring 2, a counter bore 10 is provided on one side of the raceway groove 2a. The counter bore 10 gradually decreases in diameter toward the end surface. The counter bore 10 is provided on a portion of the outer peripheral surface opposite to the direction in which the contact angle occurs. When the bearing is assembled, the rolling bearing 1 heats the outer ring 3 to which the balls 4 are assembled to expand the outer ring 3 radially outward by a predetermined small distance, and from the counter bore 10 side to the inner ring in the axial direction. Can be assembled by inserting 2.

以上説明した第１の実施形態に係る転がり軸受１によると、軸受運転時において、外輪３の内周面６に保持器外径５Ｄが案内される。また、保持器外径５Ｄの案内面のうち軸方向一端部および他端部に設けられた環状のグリース溜り凹部７，７によって、保持器５の案内面積を減少させると共に、このグリース溜り凹部７，７に、潤滑剤であるグリースＧｒが溜まることで、案内面にグリースＧｒが行き届き易くなる。換言すれば、案内面に存在するグリースＧｒは、グリース溜り凹部７，７に溜まるグリースＧｒ自体によって阻止され、保持器外径５Ｄの案内面の端部から軸受側方に飛散し難くなる。よって、案内面の摩耗や焼き付き等の潤滑不良を防止することができ、保持器音の発生を抑えることができる。保持器５に設けたグリース溜り凹部７によって、シールやシールドを設けることなくグリースＧｒの飛散を抑制できるので、シールド等を有する軸受に比べて軸受構造を簡単化でき、製造コストの低減を図ることが可能となる。   According to the rolling bearing 1 according to the first embodiment described above, the cage outer diameter 5D is guided to the inner peripheral surface 6 of the outer ring 3 during the bearing operation. The guide area of the cage 5 is reduced by the annular grease reservoir recesses 7 and 7 provided at one end and the other end in the axial direction of the guide surface of the cage outer diameter 5D. 7, the grease Gr as a lubricant is collected, so that the grease Gr can easily reach the guide surface. In other words, the grease Gr present on the guide surface is blocked by the grease Gr itself stored in the grease reservoir recesses 7 and 7, and is difficult to be scattered from the end of the guide surface having the outer diameter of the cage 5D to the bearing side. Therefore, poor lubrication such as wear and seizure of the guide surface can be prevented, and generation of cage noise can be suppressed. The grease reservoir recess 7 provided in the cage 5 can suppress the scattering of the grease Gr without providing a seal or shield, so that the bearing structure can be simplified and the manufacturing cost can be reduced compared to a bearing having a shield or the like. Is possible.

特に、保持器外径５Ｄの案内面のうち軸方向一端部および他端部に、環状のグリース溜り凹部７，７を設けたので、保持器５の剛性強度が低くなり過ぎず、軸受運転時に保持器５に作用する遠心力に起因して当該保持器５が不所望に変形することを防止することができる。また、外輪内径面に凹部を加工する従来技術よりも工数低減が可能となり、製造コストの低減を図ることが可能となる。   In particular, since the annular grease retaining recesses 7 and 7 are provided at one end and the other end in the axial direction of the guide surface having the outer diameter of the cage 5D, the rigidity strength of the cage 5 does not become too low, and the bearing is in operation. It is possible to prevent the cage 5 from being undesirably deformed due to the centrifugal force acting on the cage 5. Further, the number of man-hours can be reduced as compared with the conventional technique in which the concave portion is processed in the inner surface of the outer ring, and the manufacturing cost can be reduced.

また保持器５は樹脂製であるので、工作機械主軸等を支持するアンギュラ玉軸受のように高速回転（ピッチ円直径ｄｍに回転速度ｎを乗じたいわゆるｄｍｎ値が、例えば１４０万）しても、保持器５の軽量性および樹脂材料の有する自己潤滑性により、潤滑不良となるおそれを低減することができる。   Further, since the cage 5 is made of resin, it can be rotated at a high speed (the pitch circle diameter dm multiplied by the rotational speed n is a so-called dmn value of, for example, 1.4 million) like an angular ball bearing that supports the machine tool main shaft and the like. The risk of poor lubrication can be reduced by the light weight of the cage 5 and the self-lubricating property of the resin material.

次に、この発明の第２の実施形態を図５〜図７と共に説明する。以下の説明においては、第１の実施形態で説明している事項に対応している部分には同一の参照符を付し、重複する説明を略する場合がある。構成の一部のみを説明している場合、構成の他の部分は、先行して説明している形態と同様とする。実施の各形態で具体的に説明している部分の組合せばかりではなく、特に組合せに支障が生じなければ、実施の形態同士を部分的に組合せることも可能である。   Next, a second embodiment of the present invention will be described with reference to FIGS. In the following description, portions corresponding to the matters described in the first embodiment are denoted by the same reference numerals, and overlapping descriptions may be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in the preceding section. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

この第２の実施形態に係る転がり軸受１Ａも、グリース潤滑で使用されるアンギュラ玉軸受に適用される。この転がり軸受１Ａの保持器１１は、保持器５と同様に、リング状で全周において肉厚（後述するリング幅）が一定となるように形成されている。この保持器１１の幅方向中央に、玉４を転動可能に保持する円筒孔状のポケット１１ａが形成されている。該ポケット１１ａは円周方向一定間隔おきに複数配設されている（図７参照）。この保持器１１は、樹脂材料からなり、且つ外輪３の内周面６に案内されるものである。保持器外径１１Ｄの案内面のうち軸方向一端部および他端部に、環状のグリース溜り凹部としての傾斜部７Ｂ，７Ｂが設けられている。各傾斜部７Ｂは、保持器端部１２に向かう程半径方向内方に傾斜するように形成されている。傾斜部７Ｂのうち保持器端部１２との第１交差部Ｐ１から保持器外径１１Ｄまでの半径方向寸法ｄ２は、例えば、保持器リング幅ＲＨの１／２の寸法に規定されている。傾斜部７Ｂのうち保持器外径１１Ｄとの第２交差部Ｐ２から保持器端部１２までの幅方向寸法ｈ２は、例えば、当該保持器１１の柱幅Ｗｈ１の１／２よりも若干大きくなるように規定されている。ただし、このような半径方向寸法ｄ２、幅方向寸法ｈ２に限定されるものではない。また、第１および第２交差部Ｐ１，Ｐ２は、尖りなきように形成されている。   The rolling bearing 1A according to the second embodiment is also applied to an angular ball bearing used for grease lubrication. The cage 11 of the rolling bearing 1A is formed in a ring shape so that the wall thickness (ring width described later) is constant over the entire circumference, like the cage 5. At the center in the width direction of the cage 11, a cylindrical hole-shaped pocket 11a that holds the ball 4 in a rollable manner is formed. A plurality of pockets 11a are arranged at regular intervals in the circumferential direction (see FIG. 7). The cage 11 is made of a resin material and is guided to the inner peripheral surface 6 of the outer ring 3. Inclined portions 7B and 7B as annular grease retaining recesses are provided at one end and the other end in the axial direction of the guide surface of the cage outer diameter 11D. Each inclined portion 7B is formed so as to be inclined inward in the radial direction toward the cage end 12. A radial dimension d2 from the first intersecting portion P1 with the cage end 12 of the inclined portion 7B to the cage outer diameter 11D is defined as, for example, a dimension of ½ of the cage ring width RH. Of the inclined portion 7B, the width direction dimension h2 from the second intersection P2 with the cage outer diameter 11D to the cage end 12 is slightly larger than, for example, 1/2 of the column width Wh1 of the cage 11. It is prescribed as follows. However, it is not limited to such a radial direction dimension d2 and a width direction dimension h2. The first and second intersecting portions P1 and P2 are formed so as not to be sharp.

以上説明した第２の実施形態に係る転がり軸受１Ａによると、保持器外径１１Ｄの案内面のうち軸方向一端部および他端部に、環状のグリース溜り凹部としての傾斜部７Ｂを設けたので、保持器１１の剛性強度を、第１の実施形態に係る転がり軸受１の保持器５よりも剛性強度をさらに高め、軸受運転時に保持器１１に作用する遠心力に起因して当該保持器１１が不所望に変形することを確実に防止することができる。また、傾斜部７Ｂのうち保持器外径１１Ｄとの第２交差部Ｐ２は、尖りがないように形成されているので、案内面の摩耗や焼き付き等の潤滑不良を防止することができる。その他第１の実施形態と同様の効果を奏する。   According to the rolling bearing 1A according to the second embodiment described above, the inclined portion 7B as the annular grease reservoir recess is provided at one end and the other end in the axial direction of the guide surface of the cage outer diameter 11D. The rigidity of the cage 11 is further increased than that of the cage 5 of the rolling bearing 1 according to the first embodiment, and the cage 11 is caused by the centrifugal force acting on the cage 11 during the bearing operation. Can be reliably prevented from being deformed undesirably. Moreover, since the 2nd intersection part P2 with the cage | basket outer diameter 11D is formed so that there may be no sharpness among the inclination parts 7B, lubrication failures, such as abrasion of a guide surface and a seizure, can be prevented. Other effects similar to those of the first embodiment are obtained.

本発明の他の実施形態として、段差部は、複数の段差をなす階段形状にしてもよい。この場合の保持器は、第１の実施形態の保持器よりもやや剛性強度を高めることができる。傾斜部は、第１交差部から第２交差部まで直線的に繋がっていなくてもよい。第１交差部から第２交差部まで次第に傾斜角度が大きくなる（又は小さくなる）ような曲線的な傾斜部であってもよい。この場合であっても、第２の実施形態と同様の効果を奏する。また第１の実施形態の段差部と、第２の実施形態の傾斜部とが複合的に組み合わされた形態であっても良い。その他本発明の趣旨を逸脱しない範囲において、種々の変更を行うことが可能である。   As another embodiment of the present invention, the stepped portion may have a staircase shape having a plurality of steps. In this case, the cage can have a slightly higher rigidity than the cage of the first embodiment. The inclined portion may not be linearly connected from the first intersection to the second intersection. It may be a curved inclined portion where the inclination angle gradually increases (or decreases) from the first intersecting portion to the second intersecting portion. Even in this case, the same effects as those of the second embodiment can be obtained. Moreover, the form which the step part of 1st Embodiment and the inclination part of 2nd Embodiment combined together may be sufficient. Other various modifications can be made without departing from the spirit of the present invention.

本発明の第１の実施形態に係る転がり軸受の断面図である。It is sectional drawing of the rolling bearing which concerns on the 1st Embodiment of this invention. 図１における保持器等の要部拡大図である。It is a principal part enlarged view of the holder | retainer etc. in FIG. 同保持器の断面図である。It is sectional drawing of the holder | retainer. 同保持器の一部破断した平面図である。It is the top view which fractured | ruptured the retainer partially. 本発明の第２の実施形態に係る転がり軸受の断面図である。It is sectional drawing of the rolling bearing which concerns on the 2nd Embodiment of this invention. 同転がり軸受の保持器の断面図である。It is sectional drawing of the holder | retainer of the rolling bearing. 同保持器の一部破断した平面図である。It is the top view which fractured | ruptured the retainer partially. 従来の外輪案内型の転がり軸受の断面図である。It is sectional drawing of the conventional outer ring guide type rolling bearing. 従来技術に係り、外輪内径面に凹部が形成された転がり軸受の断面図である。It is sectional drawing of the rolling bearing in which the recessed part was formed in the outer ring internal diameter surface according to a prior art. 従来技術に係り、保持器の外径面に断面凹形状の貯油周溝を設けた転がり軸受の断面図である。It is sectional drawing of the rolling bearing which concerns on the prior art and provided the oil storage circumferential groove of the cross-sectional concave shape in the outer-diameter surface of the holder | retainer. 同保持器の変形前後を表す断面図である。It is sectional drawing showing the deformation | transformation before and behind of the same holder | retainer.

符号の説明Explanation of symbols

１，１Ａ…転がり軸受
２…内輪
３…外輪
４…玉
５…保持器
５Ｄ…保持器外径
６…内周面
７…グリース溜り凹部
７Ａ…段差部
ｄ１…段差寸法
１１…保持器 DESCRIPTION OF SYMBOLS 1,1A ... Rolling bearing 2 ... Inner ring 3 ... Outer ring 4 ... Ball 5 ... Cage 5D ... Cage outer diameter 6 ... Inner peripheral surface 7 ... Grease reservoir recessed part 7A ... Step part d1 ... Step size 11 ... Cage

Claims (4)

内輪と外輪との間に、保持器に保持された玉を介在させた転がり軸受において、
前記保持器は、外輪の内周面に案内されるものであり、且つ、この内周面に案内される保持器外径の案内面のうち端部に、環状のグリース溜り凹部を設けたことを特徴とする転がり軸受。 In a rolling bearing in which a ball held by a cage is interposed between an inner ring and an outer ring,
The cage is guided by the inner peripheral surface of the outer ring, and an annular grease reservoir recess is provided at the end of the guide surface of the outer diameter of the cage guided by the inner peripheral surface. Rolling bearing characterized by 請求項１において、
前記保持器の環状のグリース溜り凹部は、保持器外径に対し、半径方向内方に段差を有する段差部であることを特徴とする転がり軸受。 In claim 1,
The rolling grease bearing according to claim 1, wherein the annular grease retaining recess of the cage is a stepped portion having a step inward in the radial direction with respect to the outer diameter of the cage. 請求項２において、
前記保持器のうち、保持器外径から段差部の外周面までの段差寸法を、保持器外径から保持器内径までの半径方向寸法の１／２以下に規定したことを特徴とする転がり軸受。 In claim 2,
Of the cages, a rolling bearing characterized in that a step size from the outer diameter of the cage to the outer peripheral surface of the stepped portion is defined to be ½ or less of a radial dimension from the outer diameter of the cage to the inner diameter of the cage. . 請求項１〜請求項３のいずれか１項において、
前記保持器は樹脂製であることを特徴とする転がり軸受。 In any one of Claims 1-3,
The rolling bearing is characterized in that the cage is made of resin.
JP2006337203A 2006-12-14 2006-12-14 Roller bearing Pending JP2008151181A (en)

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Cited By (9)

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JP2008240806A (en) * 2007-03-26 2008-10-09 Jtekt Corp Ball bearing
WO2013002036A1 (en) * 2011-06-27 2013-01-03 Ntn株式会社 Synthetic resin ball bearing cage and ball bearing
JP2013113394A (en) * 2011-11-30 2013-06-10 Nsk Ltd Rolling bearing
JP2016507712A (en) * 2013-02-14 2016-03-10 ニュー ハンプシャー ボール ベアリングス，インコーポレイテッド Angular contact ball bearings
CN106536954A (en) * 2014-07-16 2017-03-22 株式会社捷太格特 Ball bearing
EP3173644A4 (en) * 2014-07-22 2018-06-27 NTN Corporation Ball bearing for spindle with built-in motor
JP2019074096A (en) * 2017-10-12 2019-05-16 Ntn株式会社 Rolling bearing
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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008240806A (en) * 2007-03-26 2008-10-09 Jtekt Corp Ball bearing
WO2013002036A1 (en) * 2011-06-27 2013-01-03 Ntn株式会社 Synthetic resin ball bearing cage and ball bearing
US9022662B2 (en) 2011-06-27 2015-05-05 Ntn Corporation Retainer made of synthetic resin for use in ball bearing and ball bearing
JP2013113394A (en) * 2011-11-30 2013-06-10 Nsk Ltd Rolling bearing
JP2016507712A (en) * 2013-02-14 2016-03-10 ニュー ハンプシャー ボール ベアリングス，インコーポレイテッド Angular contact ball bearings
EP2956684A4 (en) * 2013-02-14 2016-11-30 New Hampshire Ball Bearings Angular contact ball bearing
CN106536954A (en) * 2014-07-16 2017-03-22 株式会社捷太格特 Ball bearing
EP3173644A4 (en) * 2014-07-22 2018-06-27 NTN Corporation Ball bearing for spindle with built-in motor
US10197092B2 (en) 2014-07-22 2019-02-05 Ntn Corporation Ball bearing for spindle with built-in motor
JP2019074096A (en) * 2017-10-12 2019-05-16 Ntn株式会社 Rolling bearing
JP7152849B2 (en) 2017-10-12 2022-10-13 Ntn株式会社 rolling bearing
WO2021199873A1 (en) * 2020-03-30 2021-10-07 Ntn株式会社 Roller bearing
CN111677761A (en) * 2020-06-28 2020-09-18 瓦房店轴承集团国家轴承工程技术研究中心有限公司 Turntable bearing with L-shaped retainer

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