JP2003028165A - Roller bearing device - Google Patents
Roller bearing deviceInfo
- Publication number
- JP2003028165A JP2003028165A JP2001216141A JP2001216141A JP2003028165A JP 2003028165 A JP2003028165 A JP 2003028165A JP 2001216141 A JP2001216141 A JP 2001216141A JP 2001216141 A JP2001216141 A JP 2001216141A JP 2003028165 A JP2003028165 A JP 2003028165A
- Authority
- JP
- Japan
- Prior art keywords
- outer ring
- cage
- bearing device
- roller bearing
- roller
- 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- Withdrawn
Links
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
- 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
- F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
- F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock 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
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/70—Diameters; Radii
- F16C2240/80—Pitch circle diameters [PCD]
- F16C2240/82—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD
- F16C2240/84—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD with full complement of balls or rollers, i.e. sum of clearances less than diameter of one rolling element
-
- 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/02—General use or purpose, i.e. no use, purpose, special adaptation or modification indicated or a wide variety of uses mentioned
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
【０００１】
【発明の属する技術分野】本発明は、軸受装置に関し、
特に、転動体としてころを用いた転がり軸受装置に関す
る。
【０００２】
【従来の技術】転動体としてころを用いたころ軸受装置
は、玉軸受装置に比べて大荷重に耐え得るため、そのよ
うな大荷重を受ける用途に用いられることが多い。しか
るに、大荷重を受けながら回転体を支持する場合に、こ
ろが受ける力も大きくなるので、比較的剛性の高い保持
器によって、ころの挙動を抑えるようにしていることが
多い。
【０００３】
【発明が解決しようとする課題】図４は、従来技術によ
るころ軸受装置の軸線方向断面図であり、図５は、図４
の構成をV-V線で切断して矢印方向に見た図である。図
において、ころ軸受装置１００は、外輪１０１と、内輪
１０２と、外輪１０１と内輪１０２との間に転動自在に
配置された円すいころ１０３と、円すいころ１０３を保
持する保持器１０４とを有している。保持器１０４は、
リング状部１０４ｂと、リング状部１０４ｂから軸線方
向且つ半径方向に延在する複数の柱部１０４ａとを有し
ている。
【０００４】ここで、かかる保持器１０４は、図５に示
すように、円すいころ１０３の周方向両側に、柱部１０
４ａの案内面１０４ｃを当接させることで支持され、外
輪１０１と内輪１０２との間において、フローティング
状態で配置されている。そのため、かかる従来の円すい
ころ軸受では次のような問題が生じている。
【０００５】まず、外輪１０１の内周面と保持器１０４
の外周面との間のすきまＳが小さいと、軸受装置回転時
の保持器１０４の振れ回りなどにより、保持器１０４の
外周面と外輪１０１の内周面（軌道面）が当接し、硬度
の低い保持器１０４の当接部では著しい摩耗を生じる恐
れがある。
【０００６】このような当接による摩耗を防ぐため、保
持器１０４の振れ回り量などを考慮しても当接しないす
きまＳｍｉｎを確保する必要がある。しかしながら、す
きまＳｍｉｎを確保すると、外輪１０１の内径に対し
て、保持器１０４の外径を、図５に示すように限られた
範囲以上に大きくできず（ＣＲｍａｘ以下）、それに伴
って保持器１０４の柱部１０４ａの周方向幅Ｗ１は狭く
なり、ころ１０３から大きな力を受ける厳しい使用条件
では、柱部１０４ａの強度を十分に得られない恐れがあ
る。
【０００７】図６は、上述の問題点を解消できると考え
られるころ軸受装置１１０の軸線方向断面図であり、図
７は、図６の構成をVII-VII線で切断して矢印方向に見
た図である。かかるころ軸受装置においては、保持器１
１４の柱部１１４ａが、外輪１１１の内周面（軌道面）
に当接し、それにより案内されるような構造となってい
る。このような構成によれば、保持器１１４の外径が増
大するので、それに伴い柱部１１４ａの周方向幅Ｗ２を
Ｗ１より大きくすることができ、保持器１１４の強度を
増大させることができる。
【０００８】しかしながら、図６，７の構造を採用する
と、保持器１１４の強度は確保できるが、以下に述べる
ような新たな問題が生じる。図８は、図６の構成の拡大
図であり、図９は、図７の構成の拡大図である。ころ軸
受装置１１０の動作時に、図９に示すように、ころ１１
３が保持器１１４の柱部１１４ａを押す、あるいは保持
器１１４の柱部１１４ａがころ１１３を押すことによ
り、柱部１１４ａが力を受ける。すなわち、図５の従来
技術の保持器１０４と比較すると、窓押し角（一つのこ
ろに当接する柱部の案内面のなす角度）Ｌ２が広くなる
ことから、保持器１１４を半径方向に押し広げる力Ｆ１
（ころ１１３からの反力Ｆに対し、Ｆ・ｃｏｓθ：θ＝
９０−（Ｌ２／２））も大きくなり、柱部１１４ａの中
央部は、図８の実線（点線は力を受ける前）で示すよう
に変形する。すると、互いに当接し合う外輪１１１の内
周面と保持器１１４との外周面の摩擦が増大し、当接部
の摩耗を促進し、引きずりトルクの増大を引き起こす可
能性がある。
【０００９】そこで本発明は、かかる問題点を解決すべ
く、保持器の強度を確保しつつも、摩耗が少なく且つ引
きずりトルクの増大を招かないころ軸受装置を提供する
ことを目的とする。
【００１０】
【課題を解決するための手段】本発明のころ軸受装置
は、外輪と、内輪と、前記外輪と前記内輪との間に転動
自在に配置された複数のころと、前記ころを保持する保
持器とを有するころ軸受装置において、前記保持器の外
周面は、前記外輪の内周面に当接する案内面と、前記案
内面より半径方向内方に位置する内方面とからなり、前
記内方面は、前記柱部が前記ころから力を受けて変形し
ても、前記外輪に当接しない非当接状態を維持するよう
になっている。
【００１１】
【作用】本発明のころ軸受装置によれば、外輪と、内輪
と、前記外輪と前記内輪との間に転動自在に配置された
複数のころと、前記ころを保持する保持器とを有するこ
ろ軸受装置において、前記保持器の外周面は、前記外輪
の内周面に当接する案内面と、前記案内面より半径方向
内方に位置する内方面とからなり、前記内方面は、前記
柱部が前記ころから力を受けて変形しても、前記外輪に
当接しない非当接状態を維持するようになっているの
で、前記柱部が変形して前記外輪に当接する場合に比べ
て、摩耗量を抑制し、且つ引きずりトルクの抑制を行え
るようになっている。
【００１２】
【発明の実施の形態】以下、図面を参照して本発明の実
施の形態について詳細に説明する。図１は、第１の実施
の形態にかかるころ軸受装置１０の軸線方向断面図であ
る。図１において、ころ軸受装置１０は、外輪１１と、
内輪１２と、外輪１１と内輪１２との間に転動自在に配
置された円すいころ１３と、円すいころ１３を保持する
保持器１４とを有している。保持器１４は、小径のリン
グ状部１４ｂと大径のリング状部１４ｃと、リング状部
１４ｂ、１４ｃを軸線方向に連結してなる複数の柱部１
４ａとを有している。
【００１３】本実施の形態においては、小径のリング状
部１４ｂに対する柱部１４ａの接合部の外周面が、外輪
１１の内周面に当接する案内面１４ｄとなっている。
又、大径のリング状部１４ｃの外周面が、外輪１１の内
周面に当接する案内面１４ｅとなっている。案内面１４
ｄ、１４ｅの間において一段半径方向内方に位置する内
方面１４ｆは、外輪１１の内周面に対してスキマＣ（＜
Ｓｍｉｎ）で離隔している。かかるスキマＣは、ころ軸
受装置１０の動作時に、柱部１４ａがころ１３から、最
大の荷重を受けて変形した場合でも、内方面１４ｆは外
輪１１に当接しないような値となっている。
【００１４】本実施の形態によれば、案内面１４ｄ、１
４ｅが外輪１１の内周面に案内される程度に保持器１４
の内径を拡大でき、それにより柱部１４ａの周方向幅
（図７のＷ２参照）を拡大し、保持器１４の強度を確保
できる。一方、ころ軸受装置の動作時に、柱部１４ａが
ころ１３から力を受けて変形したとしても、柱部１４ａ
の中央の内方面１４ｆは、外輪１１の内周面（軌道面）
に当接しないので、摩耗の抑制と引きずりトルクの抑制
を達成することができる。
【００１５】図２は、第２の実施の形態にかかるころ軸
受装置２０の軸線方向断面図である。第２の実施の形態
に関しては、図１のころ軸受装置に対して、保持器の形
状が異なるのみであるので、同様な構成に関しては、同
一符号を付して説明を省略する。図１の保持器１４に対
して、本実施の形態の保持器２４は、案内面２４ｄ、２
４ｅの領域が減少しており、その分だけ外輪１１の内周
面に対してスキマＣで離隔している内方面２４ｆの領域
が拡大している。本実施の形態においても、上述した実
施の形態と同様な作用効果が奏される。
【００１６】図３は、第３の実施の形態にかかるころ軸
受装置３０の軸線方向断面図である。第３の実施の形態
に関しては、図１のころ軸受装置に対して、外輪及び保
持器の形状が異なるのみであるので、同様な構成に関し
ては、同一符号を付して説明を省略する。
【００１７】図３において、外輪３１は、図３の右方に
延長されて、その内周に軸線に平行な外輪案内面３１ａ
を形成している。一方、保持器３４における大径のリン
グ状部３４ｃの外周面は、外輪案内面３１ａに対向して
案内される保持器案内面３４ｅとなっている。本実施の
形態では、柱部３４ａ及び小径のリング状部３４ｂの外
周面は、外輪３１に当接していないので、内方面３４ｆ
は、案内面３４ｃからリング状部３４ｂにかけての範囲
となる。本実施の形態においても、上述した実施の形態
と同様な作用効果が奏される他、保持器３４は、軸線に
平行な外輪３１の内周面で案内されるため、ころ軸受装
置３０の動作時に、軸線方向に移動しにくいという利点
がある。
【００１８】以上、本発明を実施の形態を参照して説明
してきたが、本発明は上記実施の形態に限定して解釈さ
れるべきではなく、適宜変更・改良が可能であることは
もちろんである。例えば、本発明は円すいころに限ら
ず、円筒ころ、鼓形ころなど、他のころを用いた軸受装
置にも適用できる。
【００１９】
【発明の効果】本発明のころ軸受装置によれば、外輪
と、内輪と、前記外輪と前記内輪との間に転動自在に配
置された複数のころと、前記ころを保持する保持器とを
有するころ軸受装置において、前記保持器の外周面は、
前記外輪の内周面に当接する案内面と、前記案内面より
半径方向内方に位置する内方面とからなり、前記内方面
は、前記柱部が前記ころから力を受けて変形しても、前
記外輪に当接しない非当接状態を維持するようになって
いるので、前記柱部が変形して前記外輪に当接する場合
に比べて、摩耗量を抑制し、且つ引きずりトルクの抑制
を行えるようになっている。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device.
In particular, the present invention relates to a rolling bearing device using rollers as rolling elements. 2. Description of the Related Art A roller bearing device using rollers as rolling elements can withstand a large load as compared with a ball bearing device, and is often used for applications that receive such a large load. However, when a rotating body is supported while receiving a large load, the force received by the roller also increases, and therefore, the behavior of the roller is often suppressed by a relatively rigid cage. FIG. 4 is a sectional view in the axial direction of a roller bearing device according to the prior art, and FIG.
It is the figure which cut | disconnected this structure with the VV line and looked at the arrow direction. In the figure, a roller bearing device 100 includes an outer ring 101, an inner ring 102, a tapered roller 103 disposed so as to be able to roll between the outer ring 101 and the inner ring 102, and a cage 104 that holds the tapered roller 103. doing. The cage 104 is
The ring-shaped portion 104b has a plurality of column portions 104a extending in the axial direction and in the radial direction from the ring-shaped portion 104b. Here, as shown in FIG. 5, the retainer 104 is provided with column portions 10 on both sides of the tapered roller 103 in the circumferential direction.
4a is supported by contacting the guide surface 104c, and is arranged in a floating state between the outer ring 101 and the inner ring 102. Therefore, the following problems occur in such conventional tapered roller bearings. First, the inner peripheral surface of the outer ring 101 and the cage 104.
If the clearance S between the outer peripheral surface and the outer peripheral surface of the retainer 104 is small, the outer peripheral surface of the retainer 104 abuts on the inner peripheral surface (track surface) of the outer ring 101 due to the swinging of the retainer 104 during rotation of the bearing device. There is a risk of significant wear at the lower cage 104 abutment. In order to prevent wear due to such contact, it is necessary to secure a clearance Smin that does not contact even if the amount of swing of the cage 104 is taken into consideration. However, if the clearance Smin is ensured, the outer diameter of the cage 104 cannot be increased beyond the limited range as shown in FIG. 5 with respect to the inner diameter of the outer ring 101 (CRmax or less). The circumferential width W1 of the column portion 104a becomes narrow, and there is a possibility that the strength of the column portion 104a cannot be sufficiently obtained under severe use conditions that receive a large force from the roller 103. FIG. 6 is a sectional view in the axial direction of the roller bearing device 110 which is considered to be able to solve the above-mentioned problems. FIG. 7 is a sectional view of the structure of FIG. It is a figure. In such a roller bearing device, the cage 1
14 pillar portions 114a are the inner peripheral surface (track surface) of the outer ring 111.
The structure is such that it is in contact with and guided by it. According to such a configuration, the outer diameter of the cage 114 increases, and accordingly, the circumferential width W2 of the column portion 114a can be made larger than W1, and the strength of the cage 114 can be increased. However, if the structure shown in FIGS. 6 and 7 is adopted, the strength of the cage 114 can be ensured, but the following new problem arises. 8 is an enlarged view of the configuration of FIG. 6, and FIG. 9 is an enlarged view of the configuration of FIG. During operation of the roller bearing device 110, as shown in FIG.
3 pushes the pillar 114a of the cage 114, or the pillar 114a of the cage 114 pushes the roller 113, whereby the pillar 114a receives a force. That is, as compared with the prior art cage 104 of FIG. 5, the window pushing angle (angle formed by the guide surface of the column portion in contact with one roller) L2 is widened, so that the cage 114 is pushed in the radial direction. Force F1
(For the reaction force F from the roller 113, F · cos θ: θ =
90- (L2 / 2)) is also increased, and the central portion of the pillar portion 114a is deformed as shown by the solid line in FIG. 8 (the dotted line is before receiving force). Then, the friction between the inner peripheral surface of the outer ring 111 and the outer peripheral surface of the cage 114 that are in contact with each other increases, which may promote wear of the contact portion and cause an increase in drag torque. SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a roller bearing device that can reduce the wear and that does not increase drag torque while ensuring the strength of the cage. [0010] A roller bearing device according to the present invention comprises an outer ring, an inner ring, a plurality of rollers rotatably arranged between the outer ring and the inner ring, and the roller. In the roller bearing device having a retainer for holding, the outer peripheral surface of the retainer is composed of a guide surface that is in contact with the inner peripheral surface of the outer ring and an inner surface that is located radially inward from the guide surface, The inner surface maintains a non-contact state in which the pillar portion does not contact the outer ring even when the column portion is deformed by receiving a force from the roller. According to the roller bearing device of the present invention, an outer ring, an inner ring, a plurality of rollers arranged to roll between the outer ring and the inner ring, and a cage for holding the rollers. The outer peripheral surface of the cage includes a guide surface that contacts the inner peripheral surface of the outer ring, and an inner surface that is located radially inward from the guide surface, and the inner surface is Even if the column portion is deformed by receiving a force from the roller, the non-contact state is maintained so as not to contact the outer ring, so that the column portion deforms and contacts the outer ring. Compared to the above, the amount of wear is suppressed, and the drag torque can be suppressed. DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is an axial cross-sectional view of a roller bearing device 10 according to a first embodiment. In FIG. 1, a roller bearing device 10 includes an outer ring 11 and
An inner ring 12, a tapered roller 13 disposed between the outer ring 11 and the inner ring 12, and a cage 14 for holding the tapered roller 13 are provided. The cage 14 includes a plurality of pillar portions 1 formed by connecting a small-diameter ring-shaped portion 14b, a large-diameter ring-shaped portion 14c, and the ring-shaped portions 14b and 14c in the axial direction.
4a. In the present embodiment, the outer peripheral surface of the joint portion of the column portion 14a with respect to the small-diameter ring-shaped portion 14b is a guide surface 14d that contacts the inner peripheral surface of the outer ring 11.
In addition, the outer peripheral surface of the large-diameter ring-shaped portion 14 c is a guide surface 14 e that contacts the inner peripheral surface of the outer ring 11. Guide plane 14
The inner surface 14f positioned inward in the first radial direction between d and 14e has a clearance C (<
Smin). The clearance C has such a value that the inner surface 14 f does not come into contact with the outer ring 11 even when the column portion 14 a is deformed by receiving the maximum load from the roller 13 during the operation of the roller bearing device 10. According to the present embodiment, the guide surfaces 14d, 1
The cage 14 is moved to such an extent that 4e is guided to the inner peripheral surface of the outer ring 11.
The inner diameter of the retainer 14 can be increased, whereby the circumferential width of the column portion 14a (see W2 in FIG. 7) can be increased, and the strength of the retainer 14 can be ensured. On the other hand, even when the column portion 14a is deformed by receiving a force from the roller 13 during the operation of the roller bearing device, the column portion 14a.
The inner inner surface 14f of the outer ring 11 is an inner peripheral surface (track surface) of the outer ring 11.
Therefore, it is possible to achieve suppression of wear and suppression of drag torque. FIG. 2 is a sectional view in the axial direction of the roller bearing device 20 according to the second embodiment. Regarding the second embodiment, since only the shape of the cage is different from that of the roller bearing device of FIG. The cage 24 of the present embodiment is different from the cage 14 of FIG.
The region 4e is reduced, and the region of the inner surface 24f that is separated by the clearance C from the inner peripheral surface of the outer ring 11 is enlarged accordingly. Also in the present embodiment, the same operational effects as those of the above-described embodiments are exhibited. FIG. 3 is an axial sectional view of a roller bearing device 30 according to a third embodiment. Regarding the third embodiment, since only the shapes of the outer ring and the cage are different from those of the roller bearing device of FIG. In FIG. 3, an outer ring 31 is extended to the right in FIG. 3, and an outer ring guide surface 31a parallel to the axis on the inner periphery thereof.
Is forming. On the other hand, the outer peripheral surface of the large-diameter ring-shaped portion 34c in the cage 34 is a cage guide surface 34e that is guided to face the outer ring guide surface 31a. In the present embodiment, the outer peripheral surfaces of the column portion 34a and the small-diameter ring-shaped portion 34b are not in contact with the outer ring 31, and therefore the inner surface 34f.
Is a range from the guide surface 34c to the ring-shaped portion 34b. Also in the present embodiment, the same operational effects as those of the above-described embodiment can be obtained, and the cage 34 is guided on the inner peripheral surface of the outer ring 31 parallel to the axis, so that the operation of the roller bearing device 30 is performed. Sometimes it has the advantage that it is difficult to move in the axial direction. The present invention has been described above with reference to the embodiments. However, the present invention should not be construed as being limited to the above-described embodiments, and can be modified or improved as appropriate. is there. For example, the present invention is not limited to a tapered roller but can be applied to a bearing device using other rollers such as a cylindrical roller and a drum roller. According to the roller bearing device of the present invention, an outer ring, an inner ring, a plurality of rollers arranged to roll between the outer ring and the inner ring, and the roller are held. In the roller bearing device having a cage, the outer circumferential surface of the cage is
The guide surface is in contact with the inner peripheral surface of the outer ring, and the inner surface is located radially inward of the guide surface. Since the non-contact state that does not contact the outer ring is maintained, the amount of wear is suppressed and the drag torque is suppressed as compared with the case where the column portion deforms and contacts the outer ring. It can be done.
【図面の簡単な説明】
【図１】第１の実施の形態にかかるころ軸受装置１０の
軸線方向断面図である。
【図２】第２の実施の形態にかかるころ軸受装置２０の
軸線方向断面図である。
【図３】第３の実施の形態にかかるころ軸受装置３０の
軸線方向断面図である。
【図４】従来技術によるころ軸受装置の軸線方向断面図
である。
【図５】図４の構成をV-V線で切断して矢印方向に見た
図である。
【図６】保持器の強度を向上できると考えられるころ軸
受装置の軸線方向断面図である。
【図７】図６の構成をVII-VII線で切断して矢印方向に
見た図である。
【図８】図６のころ軸受装置の拡大図である。
【図９】図７のころ軸受装置の拡大図である。
【符号の説明】
１０、２０，３０ ころ軸受装置
１１，３１ 外輪
１２ 内輪
１３ 円すいころ
１４，２４，３４ 保持器
１４ａ、２４ａ、３４ａ 柱部
１４ｃ、１４ｄ、２４ｃ、２４ｄ、３４ｃ 案内面
１４ｆ、２４ｆ、３４ｆ 内方面BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an axial sectional view of a roller bearing device 10 according to a first embodiment. FIG. 2 is an axial sectional view of a roller bearing device 20 according to a second embodiment. FIG. 3 is an axial sectional view of a roller bearing device 30 according to a third embodiment. FIG. 4 is a sectional view in the axial direction of a roller bearing device according to the prior art. 5 is a view of the configuration of FIG. 4 taken along the line VV and viewed in the direction of the arrow. FIG. 6 is an axial sectional view of a roller bearing device that is considered to be able to improve the strength of the cage. 7 is a view of the configuration of FIG. 6 taken along line VII-VII and viewed in the direction of the arrow. 8 is an enlarged view of the roller bearing device of FIG. 6. FIG. 9 is an enlarged view of the roller bearing device of FIG. DESCRIPTION OF SYMBOLS 10, 20, 30 Roller bearing device 11, 31 Outer ring 12 Inner ring 13 Tapered rollers 14, 24, 34 Cages 14a, 24a, 34a Pillar portions 14c, 14d, 24c, 24d, 34c Guide surfaces 14f, 24f , 34f Inward direction
Claims (1)
の間に転動自在に配置された複数のころと、前記ころを
保持する保持器とを有するころ軸受装置において、 前記保持器の外周面は、前記外輪の内周面に当接する案
内面と、前記案内面より半径方向内方に位置する内方面
とからなり、前記内方面は、前記柱部が前記ころから力
を受けて変形しても、前記外輪に当接しない非当接状態
を維持するようになっているころ軸受装置。1. A roller bearing having an outer ring, an inner ring, a plurality of rollers rotatably disposed between the outer ring and the inner ring, and a cage for holding the roller. In the apparatus, an outer peripheral surface of the cage includes a guide surface that abuts on an inner peripheral surface of the outer ring, and an inner surface that is located radially inward from the guide surface, and the inner surface includes the column portion. A roller bearing device configured to maintain a non-contact state that does not contact the outer ring even when deformed by receiving a force from the roller.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001216141A JP2003028165A (en) | 2001-07-17 | 2001-07-17 | Roller bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001216141A JP2003028165A (en) | 2001-07-17 | 2001-07-17 | Roller bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003028165A true JP2003028165A (en) | 2003-01-29 |
Family
ID=19050654
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001216141A Withdrawn JP2003028165A (en) | 2001-07-17 | 2001-07-17 | Roller bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003028165A (en) |
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| WO2005054697A1 (en) * | 2003-12-02 | 2005-06-16 | Ntn Corporation | Tapered roller bearing |
| WO2005111446A1 (en) | 2004-05-13 | 2005-11-24 | Ntn Corporation | Tapered roller bearing |
| EP1605175A2 (en) * | 2004-06-11 | 2005-12-14 | Ab Skf | Cylindrical roller bearing with window-shaped cage |
| EP1614917A2 (en) | 2004-07-05 | 2006-01-11 | Ntn Corporation | Tapered roller bearing |
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2001
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| JP2005188738A (en) * | 2003-12-02 | 2005-07-14 | Ntn Corp | Tapered roller bearing |
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| WO2005054697A1 (en) * | 2003-12-02 | 2005-06-16 | Ntn Corporation | Tapered roller bearing |
| EP1698789A1 (en) * | 2003-12-02 | 2006-09-06 | Ntn Corporation | Tapered roller bearing |
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| EP1605175A2 (en) * | 2004-06-11 | 2005-12-14 | Ab Skf | Cylindrical roller bearing with window-shaped cage |
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| EP1614917A3 (en) * | 2004-07-05 | 2010-12-22 | NTN Corporation | Tapered roller bearing |
| JP2006022823A (en) * | 2004-07-05 | 2006-01-26 | Ntn Corp | Tapered roller bearing for transmission |
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| CN107110216A (en) * | 2014-10-29 | 2017-08-29 | 株式会社捷太格特 | Tapered roller bearing |
| US10215233B2 (en) | 2014-10-29 | 2019-02-26 | Jtekt Corporation | Taper roller bearing |
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| JP2016089846A (en) * | 2014-10-29 | 2016-05-23 | 株式会社ジェイテクト | Conical roller bearing |
| US10408266B2 (en) | 2014-10-29 | 2019-09-10 | Jtekt Corporation | Cage for taper roller bearing and taper roller bearing |
| CN107110216B (en) * | 2014-10-29 | 2020-01-03 | 株式会社捷太格特 | Tapered roller bearing |
| US10539184B2 (en) | 2014-10-29 | 2020-01-21 | Jtekt Corporation | Taper roller bearing |
| CN106851696A (en) * | 2017-04-07 | 2017-06-13 | 深圳市普渡科技有限公司 | A kind of scheduling system of the UWB multi-tag many base stations synchronous based on Wireless clock |
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| CN111801504B (en) * | 2018-03-07 | 2022-04-29 | 住友重机械工业株式会社 | Radial oblique roller bearing |
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Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20080717 |
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