JP3144409B2 - Rolling bearing device - Google Patents
Rolling bearing deviceInfo
- Publication number
- JP3144409B2 JP3144409B2 JP04634199A JP4634199A JP3144409B2 JP 3144409 B2 JP3144409 B2 JP 3144409B2 JP 04634199 A JP04634199 A JP 04634199A JP 4634199 A JP4634199 A JP 4634199A JP 3144409 B2 JP3144409 B2 JP 3144409B2
- Authority
- JP
- Japan
- Prior art keywords
- ball
- ball bearings
- bearing
- rolling bearing
- bearing device
- 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.)
- Expired - Fee Related
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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
-
- 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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
- F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact 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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/545—Systems comprising at least one rolling bearing for radial load in combination with at least one rolling bearing for axial load
-
- 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
-
- 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
- F16C2360/00—Engines or pumps
- F16C2360/43—Screw compressors
Description
【０００１】[0001]
【発明の属する技術分野】この発明に係る転がり軸受装
置は、例えばスクリューコンプレッサの回転軸を回転自
在に支持する為に利用する。BACKGROUND OF THE INVENTION A rolling bearing device according to the present invention is used, for example, to rotatably support a rotary shaft of a screw compressor.
【０００２】[0002]
【従来の技術】スクリューコンプレッサの回転軸等、高
速で回転する軸を支承する為、図４に示す様な転がり軸
受装置が、従来から使用されている。この軸受装置は、
スクリューコンプレッサを構成するロータ１を固定した
回転軸２の外周面と、ハウジング３の内周面との間に設
けられる。尚、図４で４は、ラジアル方向の負荷Ｆr を
支承する為のころ軸受で、本発明の対象ではない。2. Description of the Related Art Rolling bearing devices as shown in FIG. 4 are conventionally used to support a high-speed rotating shaft such as a rotary shaft of a screw compressor. This bearing device
The screw compressor is provided between an outer peripheral surface of a rotating shaft 2 to which a rotor 1 constituting the screw compressor is fixed and an inner peripheral surface of a housing 3. Incidentally, 4 in FIG. 4 is a roller bearing for supporting a load F r radial, not the subject of the present invention.
【０００３】本発明の対象である軸受装置は、上記回転
軸２の軸方向（図４の左右方向）荷重を支承する為のも
ので、１対のアンギュラ型の玉軸受５、６を組み合わせ
る事により構成される。両玉軸受５、６の接触角α（後
述する図５参照）の方向は、互いに逆方向（本例では所
謂正面組合せ）としている。この為、上記回転軸２が図
４の左方に変位しようとする時は、同図で左方の玉軸受
５が軸方向荷重を支承し、同じく右方に変位しようとす
る時は、右方の玉軸受６が軸方向荷重を支承して、回転
軸２及びロータ１が、ハウジング３に対し変位する事を
防止する。但し、本発明の対象となる軸受装置により支
持する上記回転軸２の使用時には、上記ロータ１の回転
に伴なって、この回転軸２に、ほぼ一定方向（図では右
から左方向へ）の軸方向荷重Ｆa が加わる。尚、図４で
７、８は間座、９は抑え金である。A bearing device to which the present invention is applied is for supporting a load in the axial direction (the left-right direction in FIG. 4) of the rotary shaft 2 and is constituted by combining a pair of angular type ball bearings 5 and 6. It consists of. The directions of the contact angles α (see FIG. 5 described later) of the two ball bearings 5 and 6 are opposite to each other (a so-called front combination in this example). For this reason, when the rotary shaft 2 is to be displaced to the left in FIG. 4, the left ball bearing 5 in FIG. The other ball bearing 6 supports the axial load, and prevents the rotating shaft 2 and the rotor 1 from being displaced with respect to the housing 3. However, when the rotating shaft 2 supported by the bearing device to which the present invention is applied is used, the rotating shaft 2 rotates in a substantially constant direction (from right to left in the figure) as the rotor 1 rotates. An axial load Fa is applied. In FIG. 4, reference numerals 7 and 8 denote spacers and reference numeral 9 denotes a presser.
【０００４】[0004]
【発明が解決しようとする課題】ところで、上述の様に
１対のアンギュラ型の玉軸受５、６を互いの位置関係が
変らない（定位置）様に組み合わせて成る転がり軸受装
置は、回転軸２が高速（例えば１００万dmn 以上）で回
転した場合には、必ずしも十分な軸受寿命を得られない
事がある。As described above, a rolling bearing device comprising a pair of angular ball bearings 5 and 6 combined in such a manner that their positional relationship does not change (fixed position) is achieved by a rotating shaft. 2 when rotating at high speed (e.g., more than 1 million d m n), it may not always provide sufficient bearing life.
【０００５】図５は、高速回転で生じる遠心力に基づい
て、軸受に加わる力を説明する為の図である。この図５
に示す様に、上記回転軸２を高速で回転させた場合、内
輪１０及び外輪１３と共に各玉軸受５、６を構成する、
玉１１、１２に加わる遠心力に基づいて、各玉軸受５、
６の外輪１３、１３の内周面に、荷重Ｆc1が加わる。そ
して、各玉軸受５、６を構成する玉１１、１２は、この
遠心力に基づいて外輪軌道１４、１４に、Ｑin1 の力
で、接触角αの方向に押し付けられる。そして、各玉軸
受５、６を構成する玉１１、１２は、この力Ｑin1 の軸
方向の分力Ｆain1で各外輪軌道１４、１４に、アキシャ
ル方向に亙り押し付けられる。そして、この分力により
Ｆain1＋Ｆain1に相当する内部アキシャル荷重が、組み
合わされた各玉軸受５、６に発生し、上記外輪軌道１
４、１４と玉１１、１２との接触面圧を増大させて、各
玉軸受５、６の疲れ寿命を低下させてしまう。FIG. 5 is a diagram for explaining the force applied to the bearing based on the centrifugal force generated at high speed rotation. This figure 5
As shown in FIG. 5, when the rotating shaft 2 is rotated at a high speed, the ball bearings 5 and 6 are configured together with the inner ring 10 and the outer ring 13.
Based on the centrifugal force applied to the balls 11, 12, each ball bearing 5,
A load Fc1 is applied to the inner peripheral surfaces of the outer rings 13 and 13 of FIG. The balls 11, 12 constituting the respective ball bearings 5, 6 are pressed against the outer raceways 14, 14 by the force of Q in1 in the direction of the contact angle α based on the centrifugal force. The balls 11 and 12 constituting the respective ball bearings 5 and 6, each outer ring raceways 14, 14 in the axial direction of the component force F AIN1 of force Q in1, pressed against over the axial direction. Due to this component force, an internal axial load corresponding to Fain1 + Fain1 is generated in each of the combined ball bearings 5 and 6, and the outer raceway 1
The contact surface pressure between the ball bearings 4 and 14 and the balls 11 and 12 is increased, and the fatigue life of the ball bearings 5 and 6 is reduced.
【０００６】上述の様な原因による寿命低下を防止すべ
く、各玉軸受５、６を構成する玉１１、１２を、軽量な
セラミック材により造ったり、或は玉１１、１２として
小径なものを使用し、遠心力に基づいて生じる荷重Ｆc1
を小さくする試みもなされている。ところが、玉１１、
１２を、縦弾性係数の大きなセラミック材により造る
と、特に外部荷重（例えば上記軸方向荷重Ｆa ）を支承
する側の玉軸受５に於いて、玉１１が外輪軌道１４に押
し付けられ、この外輪軌道１４と玉１１との接触面圧が
軸受鋼製の玉を使用した場合よりも増大して玉軸受５の
疲れ寿命が低下し、組合せ玉軸受５、６全体の疲れ寿命
が低下してしまう。又、玉１１、１２として小径のもの
を使用すると、各玉軸受５、６の負荷容量（基本動定格
荷重）が小さくなり、やはり疲れ寿命が低下してしま
う。本発明の転がり軸受装置は、上述の様な事情に鑑み
て発明したものである。In order to prevent shortening of the service life due to the above-mentioned causes, the balls 11 and 12 constituting each of the ball bearings 5 and 6 may be made of a lightweight ceramic material, or small balls 11 and 12 may be used. Use, load Fc1 generated based on centrifugal force
Attempts have been made to reduce this. However, ball 11,
12, when made by a large ceramic material modulus, especially at the ball bearing 5 on the side for supporting external load (e.g. the axial load F a), the ball 11 is pressed against the outer ring raceway 14, the outer ring The contact surface pressure between the raceway 14 and the ball 11 increases as compared with the case where a ball made of bearing steel is used, so that the fatigue life of the ball bearing 5 decreases, and the fatigue life of the combined ball bearings 5 and 6 as a whole decreases. . Also, if the balls 11 and 12 have a small diameter, the load capacity (basic dynamic load rating) of each of the ball bearings 5 and 6 is reduced, and the fatigue life is also reduced. The rolling bearing device of the present invention has been invented in view of the above situation.
【０００７】[0007]
【課題を解決するための手段】本発明の転がり軸受装置
は何れも、前述した従来の転がり軸受装置と同様に、軸
の外周面とハウジングの内周面との間に、少なくとも１
対のアンギュラ型の玉軸受を、互いの接触角の方向を異
ならせて設け、使用時に上記軸とハウジングとの間に、
外部からほぼ一定方向に加わる軸方向荷重を、上記１対
の玉軸受の内の一方の玉軸受により支承する。In each of the rolling bearing devices of the present invention, at least one rolling bearing device is provided between the outer peripheral surface of the shaft and the inner peripheral surface of the housing, similarly to the aforementioned conventional rolling bearing device.
A pair of angular type ball bearings are provided with different directions of the contact angle with each other, and when used, between the shaft and the housing,
An axial load applied from the outside in a substantially constant direction is supported by one of the pair of ball bearings.
【０００８】特に、本発明の転がり軸受装置のうち、請
求項１に記載したものに於いては、上記一方の玉軸受
（負荷側）を構成する玉の径よりも、他方の玉軸受（反
負荷側）を構成する玉の径を小さくしている。又、請求
項２に記載した転がり軸受装置に於いては、上記一方の
玉軸受（負荷側）を構成する玉を軸受鋼製とし、他方の
玉軸受（反負荷側）を構成する玉をセラミック製として
いる。In particular, in the rolling bearing device according to the present invention, in the rolling bearing device according to the present invention, the diameter of the one ball bearing (load side) is larger than the diameter of the other ball bearing (anti-ball bearing). The diameter of the ball constituting the load side) is reduced. Further, in the rolling bearing device according to the second aspect, the ball forming the one ball bearing (load side) is made of bearing steel, and the ball forming the other ball bearing (non-load side) is formed of ceramic. It is made.
【０００９】[0009]
【作用】上述の様に構成される本発明の転がり軸受装置
は何れも、使用時に外部から加わる軸方向荷重を支承す
る、一方の玉軸受の負荷容量として大きいものを使用
し、又、使用時にこの軸方向荷重を支承しない他方の玉
軸受は、遠心力に基づく内部アキシャル荷重の増大を抑
える構成とする。この為、１対のアンギュラ型の玉軸受
を組み合わせて成る転がり軸受装置全体としての、転が
り疲れ寿命の低下を抑える事が出来る。Each of the rolling bearing devices of the present invention configured as described above uses a large ball bearing as one of the ball bearings that supports an axial load applied from the outside during use. The other ball bearing that does not support the axial load is configured to suppress an increase in internal axial load due to centrifugal force. For this reason, it is possible to suppress a reduction in the rolling fatigue life of the entire rolling bearing device formed by combining a pair of angular ball bearings.
【００１０】[0010]
【発明の実施の形態】図１〜２は、請求項１に対応す
る、本発明の実施の形態の第１例を示している。前述の
図４〜５に示した従来装置と同等部分には同一符号を付
して重複する説明を省略し、以下、本発明の特徴部分に
就いて説明する。使用時に外部から回転軸２に加わる軸
方向荷重Ｆa を支承する負荷側（図１〜２の左側）に設
けた、一方の玉軸受５ａを構成する玉１１ａの径を、前
記従来の転がり軸受装置の玉軸受５、６（図４〜５）を
構成する玉１１、１２の径と同様に大きくしている。こ
れに対して、使用時に上記軸方向荷重Ｆa を支承しない
反負荷側（図１〜２の右側）に設けられた、他方の玉軸
受６ａを構成する玉１２ａの径を、これよりも小さくし
ている。1 and 2 show a first embodiment of the present invention corresponding to claim 1. FIG. The same parts as those of the conventional apparatus shown in FIGS. 4 and 5 are denoted by the same reference numerals, and the description thereof will not be repeated. The following describes only the features of the present invention. Provided on the load side for supporting the axial load F a acting on the rotary shaft 2 from the outside (left side in FIG. 1-2), in use, the diameter of the balls 11a which constitutes the one of the ball bearings 5a, the conventional rolling bearing The diameter of the balls 11 and 12 constituting the ball bearings 5 and 6 (FIGS. 4 and 5) of the device is increased as well. In contrast, the anti-load side without bearing the axial load F a at the time of use provided (right side in FIG. 1-2), the diameter of the balls 12a constituting the other of the ball bearing 6a, smaller than this are doing.
【００１１】上述の様に、負荷側である一方の玉軸受５
ａを構成する玉１１ａの径を大きく、反負荷側である他
方の玉軸受６ａを構成する玉１２ａの径を小さくする事
により、上記負荷側である一方の玉軸受５ａの負荷容量
を十分に確保出来る。この場合に於いて、遠心力に基づ
いてこの一方の玉軸受５ａに作用する軸方向分力は、Ｆ
ain1となる。又、反負荷側である他方の玉軸受６ａに加
わる軸方向分力はＦain3となる。この場合に於いて、こ
の他方の玉軸受６ａを構成する玉１２ａの径は小さく、
従ってこの玉１２ａに作用する遠心力も小さい為、上記
他方の玉軸受６ａに加わる軸方向分力Ｆain3は、前記従
来装置の玉軸受６に作用する軸方向分力Ｆain1よりも小
さく（Ｆain3＜Ｆain1）なる。この為、組み合わせられ
た玉軸受に発生する、遠心力に基づく内部アキシャル荷
重は、Ｆain1＋Ｆain3となり、前記従来装置に生じる内
部アキシャル荷重Ｆain1＋Ｆain1よりも小さくなる。As described above, one of the ball bearings 5 on the load side
a by increasing the diameter of the ball 11a constituting the ball bearing 5a and decreasing the diameter of the ball 12a constituting the other ball bearing 6a on the non-load side, thereby sufficiently increasing the load capacity of the ball bearing 5a on the load side. Can be secured. In this case, the axial component acting on one of the ball bearings 5a based on the centrifugal force is F
ain1 . The axial component force applied to the other ball bearing 6a on the non-load side is Fain3 . In this case, the diameter of the ball 12a constituting the other ball bearing 6a is small,
Therefore, since the centrifugal force acting on the ball 12a is also small, the axial component force Fain3 applied to the other ball bearing 6a is smaller than the axial component force Fain1 acting on the ball bearing 6 of the conventional device ( Fain3). <F ain1 ). Therefore, generated combined ball bearing, an internal axial load based on the centrifugal force, F ain1 + F ain3, and becomes smaller than the internal axial load F ain1 + F ain1 generated in the conventional apparatus.
【００１２】この結果、上記各玉軸受５ａ、６ａを構成
する玉１１ａ、１２ａと外輪軌道１４、１４との接触面
圧が低下する。そして、各玉軸受５ａ、６ａの転がり疲
れ寿命が低下する事が抑えられ、１対のアンギュラ型の
玉軸受５ａ、６ａを組み合わせて成る転がり軸受装置の
寿命低下を抑える事が出来る。As a result, the contact surface pressure between the balls 11a, 12a constituting the respective ball bearings 5a, 6a and the outer raceways 14, 14 decreases. The rolling fatigue life of each of the ball bearings 5a and 6a is prevented from being shortened, and the life of the rolling bearing device formed by combining the pair of angular ball bearings 5a and 6a can be suppressed.
【００１３】次に、図３は、請求項２に対応する、本発
明の実施の形態の第２例を示している。使用時に外部か
ら回転軸２に加わる軸方向荷重Ｆa を支承する負荷側
（図３の左側）に設けられた、一方の玉軸受５ｂを構成
する玉１１を、前記従来の転がり軸受装置の玉軸受５、
６（図４〜５）を構成する玉１１、１２と同様に、軸受
鋼により造り、使用時に上記軸方向荷重Ｆa を支承しな
い反負荷側（図３の右側）に設けられた、他方の玉軸受
６ｂを構成する玉１２ｂを、軸受鋼よりも軽量なセラミ
ックにより造っている。FIG. 3 shows a second embodiment of the present invention corresponding to claim 2. Provided on the load side for supporting the axial load F a acting on the rotary shaft 2 from the outside (left side in FIG. 3) in use, the balls 11 constituting one of the ball bearing 5b, the ball of a conventional rolling bearing device Bearing 5,
6 Like the balls 11 and 12 constituting the (FIGS. 4-5), making the bearing steel, provided on the anti-load side without bearing the axial load F a at the time of use (the right side in FIG. 3), the other The ball 12b constituting the ball bearing 6b is made of ceramic which is lighter than bearing steel.
【００１４】上述の様に、一方の玉軸受５ｂを構成する
玉１１を軸受鋼により造る事で、この負荷側である一方
の玉軸受５ｂの負荷容量を十分に確保出来る。この場合
に於いて、遠心力に基づいてこの一方の玉軸受５ｂに作
用する軸方向分力は、Ｆain1となる。又、反負荷側であ
る他方の玉軸受６ｂに加わる軸方向分力は、Ｆain4とな
る。この場合に於いて、この他方の玉軸受６ｂを構成す
る玉１２ｂは軽量で、従ってこの玉１２ｂに作用する遠
心力も小さい為、上記他方の玉軸受６ｂに加わる軸方向
分力Ｆain4は、前述した従来装置の他方の玉軸受６に作
用する軸方向分力Ｆain1よりも小さく（Ｆain4＜
Ｆain1）なる。この為、組み合わせられた玉軸受に発生
する、遠心力に基づく内部アキシャル荷重は、Ｆain1＋
Ｆain4となり、前記従来装置に生じる内部アキシャル荷
重Ｆain1＋Ｆain1よりも小さくなる。As described above, by forming the balls 11 constituting the one ball bearing 5b from bearing steel, the load capacity of the one ball bearing 5b on the load side can be sufficiently ensured. In this case, the axial component acting on the one ball bearing 5b based on the centrifugal force is Fain1 . The axial component force applied to the other ball bearing 6b on the non-load side is Fain4 . In this case, the ball 12b constituting the other ball bearing 6b is light in weight, and therefore the centrifugal force acting on the ball 12b is small. Therefore, the axial component force Fain4 applied to the other ball bearing 6b is as described above. Is smaller than the axial component force Fain1 acting on the other ball bearing 6 of the conventional device ( Fain4 <
F ain1 ). For this reason, the internal axial load based on the centrifugal force generated in the combined ball bearing is F ain1 +
F AIN4, and becomes smaller than the internal axial load F ain1 + F ain1 generated in the conventional apparatus.
【００１５】この結果、上記各玉軸受５ｂ、６ｂを構成
する玉１１、１２ｂと外輪軌道１４、１４との接触面圧
が低下する。そして、各玉軸受５ｂ、６ｂの転がり疲れ
寿命が低下する事が抑えられ、１対のアンギュラ型の玉
軸受５ｂ、６ｂを組み合わせて成る転がり軸受装置の寿
命低下を抑える事が出来る。例えば、本発明者が、各玉
軸受５ｂ、６ｂを構成する玉１１、１２ｂの材質を変え
た場合に於ける、各玉軸受５ｂ、６ｂの転がり疲れ寿命
を計算した結果を、下記の表１に示す。尚、各玉軸受５
ｂ、６ｂとして、内径２５mm、外径６２mm、幅１７mmの
アンギュラ型玉軸受（７３０５型）を２個、製作時の測
定アキシャル隙間が０．０３０mmとなる様にして、正面
組み合わせ（各図に示した様な組み合わせ）で組み合わ
せ、６７kgf の軸方向荷重を受けつつ、回転数２３００
０r.p.m.で回転する回転軸に装着した場合の条件で計算
した。又、これら各玉軸受５ｂ、６ｂの接触角は何れも
３０度とした。As a result, the contact surface pressure between the balls 11, 12b constituting the ball bearings 5b, 6b and the outer raceways 14, 14 is reduced. Then, a reduction in the rolling fatigue life of each of the ball bearings 5b, 6b is suppressed, and a reduction in the life of the rolling bearing device formed by combining the pair of angular ball bearings 5b, 6b can be suppressed. For example, the present inventor calculated the rolling fatigue life of each ball bearing 5b, 6b when the material of the balls 11, 12b constituting each ball bearing 5b, 6b was changed. Shown in In addition, each ball bearing 5
As b and 6b, two angular ball bearings (type 7305) having an inner diameter of 25 mm, an outer diameter of 62 mm, and a width of 17 mm are combined so that the axial gap measured at the time of manufacture is 0.030 mm. 2300 rpm while receiving a 67 kgf axial load.
The calculation was performed under the condition that the device was mounted on a rotating shaft rotating at 0 rpm. The contact angle of each of the ball bearings 5b and 6b was 30 degrees.
【００１６】[0016]
【表１】 [Table 1]
【００１７】この計算結果から明らかな通り、本発明の
転がり軸受装置は、従来の転がり軸受装置に比べて大幅
に寿命が長くなる。尚、本発明は、１対のアンギュラ型
玉軸受を正面組み合わせで組み合わせた転がり軸受装置
に限らず、３個以上の玉軸受を組み合わせた場合でも、
或は背面組み合わせにより組み合わせた転がり軸受装置
でも、適用可能である。又、組み合わされた玉軸受同士
の間に間座を介在させる構造の場合でも適用可能であ
る。又、請求項１、２は各々単独でも効果があるが、二
つの請求項を組み合わせる事により、更に大きな効果を
得られる。更には、１対のアンギュラ型玉軸受の接触角
を互いに異ならせる構造を組み合わせる事もできる。即
ち、遠心力に基づく内部アキシアル荷重の増大は、接触
角が大きい程著しくなる。そこで、軸方向荷重を受けな
い他方の玉軸受の接触角を小さくして、内部アキシアル
荷重の増大を抑える。これに対して、上記軸方向荷重を
受ける一方の玉軸受の接触角は大きくして、この一方の
玉軸受の負荷容量を確保する。As is apparent from the calculation results, the rolling bearing device of the present invention has a significantly longer life than the conventional rolling bearing device. In addition, the present invention is not limited to a rolling bearing device in which a pair of angular type ball bearings are combined in a frontal combination, even when three or more ball bearings are combined.
Alternatively, the present invention can be applied to a rolling bearing device combined by a combination of rear surfaces. Further, the present invention is also applicable to a structure in which a spacer is interposed between the combined ball bearings. Although the first and second aspects are each effective independently, a greater effect can be obtained by combining the two aspects. Further, a structure in which the contact angles of a pair of angular ball bearings are different from each other can be combined. That is, the increase in the internal axial load due to the centrifugal force becomes more significant as the contact angle increases. Therefore, the contact angle of the other ball bearing that does not receive the axial load is reduced to suppress an increase in the internal axial load. On the other hand, the contact angle of one of the ball bearings receiving the axial load is increased to secure the load capacity of the one ball bearing.
【００１８】[0018]
【発明の効果】本発明は、以上に述べた通り構成され作
用する為、外部アキシャル荷重に対する負荷容量を十分
に確保しつつ、内部アキシャル荷重の低減を図って、転
がり軸受装置の耐久性向上を図れる。Since the present invention is constructed and operated as described above, the internal axial load is reduced while the load capacity against the external axial load is sufficiently secured, and the durability of the rolling bearing device is improved. I can do it.
【図１】本発明の実施の形態の第１例を示す断面図。FIG. 1 is a sectional view showing a first example of an embodiment of the present invention.
【図２】同じく要部断面図。FIG. 2 is a sectional view of an essential part of the same.
【図３】本発明の実施の形態の第２例を示す要部断面
図。FIG. 3 is an essential part cross-sectional view showing a second example of the embodiment of the present invention.
【図４】従来装置を示す断面図。FIG. 4 is a sectional view showing a conventional device.
【図５】同じく要部断面図。FIG. 5 is a sectional view of an essential part of the same.
１ ロータ ２ 回転軸 ３ ハウジング ４ ころ軸受 ５、５ａ、５ｂ 玉軸受 ６、６ａ、６ｂ 玉軸受 ７、８ 間座 ９ 抑え金 １０ 内輪 １１、１１ａ 玉 １２、１２ａ、１２ｂ 玉 １３ 外輪 １４ 外輪軌道 DESCRIPTION OF SYMBOLS 1 Rotor 2 Rotary shaft 3 Housing 4 Roller bearing 5, 5a, 5b Ball bearing 6, 6a, 6b Ball bearing 7, 8 Spacer 9 Retainer 10 Inner ring 11, 11a Ball 12, 12a, 12b Ball 13 Outer ring 14 Outer ring raceway
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F16C 19/56 F16C 19/18 F16C 33/58 ──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int. Cl. 7 , DB name) F16C 19/56 F16C 19/18 F16C 33/58
Claims (2)
に、少なくとも１対のアンギュラ型の玉軸受を、互いの
接触角の方向を異ならせて設け、使用時に上記軸とハウ
ジングとの間に、外部からほぼ一定方向に加わる軸方向
荷重を、上記１対の玉軸受の内の一方の玉軸受により支
承する転がり軸受装置に於いて、この一方の玉軸受を構
成する玉の径よりも、他方の玉軸受を構成する玉の径を
小さくした事を特徴とする転がり軸受装置。At least one pair of angular ball bearings is provided between an outer peripheral surface of a shaft and an inner peripheral surface of a housing so that directions of contact angles thereof are different from each other. In a rolling bearing device in which an axial load applied from the outside in a substantially constant direction is supported by one of the pair of ball bearings, the diameter of a ball forming one of the ball bearings A rolling bearing device characterized in that the diameter of a ball constituting the other ball bearing is reduced.
に、少なくとも１対のアンギュラ型の玉軸受を、互いの
接触角の方向を異ならせて設け、使用時に上記軸とハウ
ジングとの間に、外部からほぼ一定方向に加わる軸方向
荷重を、上記１対の玉軸受の内の一方の玉軸受により支
承する転がり軸受装置に於いて、この一方の玉軸受を構
成する玉を軸受鋼製とし、他方の玉軸受を構成する玉を
セラミック製とした事を特徴とする転がり軸受装置。2. At least one pair of angular type ball bearings are provided between an outer peripheral surface of a shaft and an inner peripheral surface of a housing so that directions of contact angles thereof are different from each other. In a rolling bearing device in which an axial load applied from the outside in a substantially constant direction is supported by one of the pair of ball bearings, a ball forming one of the ball bearings is mounted. A rolling bearing device characterized in that it is made of steel and the balls constituting the other ball bearing are made of ceramic.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04634199A JP3144409B2 (en) | 1999-02-24 | 1999-02-24 | Rolling bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04634199A JP3144409B2 (en) | 1999-02-24 | 1999-02-24 | Rolling bearing device |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP04078811A Division JP3144033B2 (en) | 1992-03-02 | 1992-03-02 | Rolling bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11280758A JPH11280758A (en) | 1999-10-15 |
| JP3144409B2 true JP3144409B2 (en) | 2001-03-12 |
Family
ID=12744448
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP04634199A Expired - Fee Related JP3144409B2 (en) | 1999-02-24 | 1999-02-24 | Rolling bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3144409B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20130264495A1 (en) * | 2011-01-31 | 2013-10-10 | Ushio Denki Kabushiki Kaisha | Ultraviolet irradiation device for implants |
-
1999
- 1999-02-24 JP JP04634199A patent/JP3144409B2/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20130264495A1 (en) * | 2011-01-31 | 2013-10-10 | Ushio Denki Kabushiki Kaisha | Ultraviolet irradiation device for implants |
| US8729501B2 (en) * | 2011-01-31 | 2014-05-20 | Ushio Denki Kabushiki Kaisha | Ultraviolet irradiation device for implants |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH11280758A (en) | 1999-10-15 |
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