JP6532651B2

JP6532651B2 - Rolling bearing with seal ring

Info

Publication number: JP6532651B2
Application number: JP2014080862A
Authority: JP
Inventors: 宏一矢嶋; 石田　勝; 勝石田
Original assignee: NSK Ltd; Uchiyama Manufacturing Corp
Current assignee: NSK Ltd; Uchiyama Manufacturing Corp
Priority date: 2014-04-10
Filing date: 2014-04-10
Publication date: 2019-06-19
Anticipated expiration: 2034-04-10
Also published as: JP2015200393A

Description

本発明は、二輪車用エンジン、変速機等、各種回転装置の回転支持部に組み込んだ状態で、回転軸等の回転部材を、ハウジング部等の固定部分に対して回転自在に支持する為に利用する、シールリング付転がり軸受の改良に関する。 The present invention is used to rotatably support a rotating member such as a rotating shaft with respect to a fixed portion such as a housing portion in a state of being incorporated in a rotating support portion of various rotating devices such as motorcycle engines and transmissions. The present invention relates to the improvement of a rolling bearing with a seal ring.

各種回転支持部に組み込む為の軸受として、玉軸受、ころ軸受、円すいころ軸受等の、単列又は複列の各種転がり軸受が広く使用されている。又、この様な転がり軸受として、軸方向端部開口をシールリングにより塞いだシールリング付転がり軸受も、例えば特許文献１に記載され、従来から広く知られている。図５〜６は、この特許文献１に記載された、従来構造のシールリング付転がり軸受の１例を示している。 As bearings for incorporating in various rotation support portions, various types of rolling bearings such as ball bearings, roller bearings and tapered roller bearings are widely used. Further, as such a rolling bearing, a rolling bearing with a seal ring in which an axial end opening is closed by a seal ring is described in, for example, Patent Document 1 and is widely known. FIGS. 5-6 show one example of the rolling bearing with a seal ring of the conventional structure described in this patent document.

シールリング付玉軸受１は、軸方向中央部内周面に深溝型の外輪軌道２を有する外輪３と、軸方向中央部外周面に深溝型の内輪軌道４を有する内輪５と、これら外輪軌道２と内輪軌道４との間に転動自在に設けられた、それぞれが転動体である玉６とを備えている。これら各玉６は、円周方向に互いに等間隔に配置された状態で、保持器７により転動自在に保持されている。又、前記各玉６を配置した、前記外輪３の内周面と前記内輪５の外周面との間に存在する内部空間８の軸方向両端開口部を、それぞれ円輪状のシールリング９により塞いでいる。 The seal ring ball bearing 1 includes an outer ring 3 having a deep groove type outer ring raceway 2 on the inner peripheral surface in the axial direction center, an inner ring 5 having a deep groove inner ring race 4 on the outer peripheral surface in the axial direction central portion And the inner ring raceway 4, provided with balls 6 each of which is a rolling element. Each of the balls 6 is rotatably held by the cage 7 in a state of being arranged at equal intervals in the circumferential direction. Further, opening portions at both axial ends of the internal space 8 existing between the inner peripheral surface of the outer ring 3 and the outer peripheral surface of the inner ring 5 in which the balls 6 are arranged are closed by seal rings 9 each having an annular shape. It is.

前記各シールリング９は、芯金１０と弾性材１１とを備える。このうちの芯金１０は、鋼板等の金属板に、打ち抜き、曲げ等のプレス加工を施す事により、断面クランク形で、全体を円輪状としている。又、前記弾性材１１は、ゴムの如きエラストマー等から成り、前記芯金１０を包埋した状態で円輪状に成形されて、この芯金１０により補強されている。又、前記弾性材１１のうちで、前記各シールリング９の径方向外端部には、弾性係止部１２が設けられている。これに対し、これら各シールリング９の径方向内端部には、前記芯金１０の内周縁部を覆う状態で、軸方向寸法の大きいブロック部１３が設けられている。又、このブロック部１３の軸方向内側面には、それぞれが軸方向に突出する第一シールリップ１４及び第二シールリップ１５が設けられている。
尚、本明細書及び特許請求の範囲で、軸方向に関して内とは、転がり軸受の中央に向かう方向を言い、外とは、転がり軸受の端部に向かう方向を言う。 Each seal ring 9 is provided with a core metal 10 and an elastic member 11. Among them, the core metal 10 has a cross-sectional crank shape and is formed into an annular shape as a whole by subjecting a metal plate such as a steel plate or the like to press processing such as punching and bending. Further, the elastic member 11 is made of an elastomer or the like such as rubber, and is formed into an annular shape in a state in which the core metal 10 is embedded, and is reinforced by the core metal 10. In addition, elastic locking portions 12 are provided at radially outer end portions of the seal rings 9 among the elastic members 11. On the other hand, a block portion 13 having a large axial dimension is provided at the radially inner end of each seal ring 9 so as to cover the inner peripheral edge of the cored bar 10. Further, on the axially inner side surface of the block portion 13, there are provided a first seal lip 14 and a second seal lip 15 which respectively project in the axial direction.
In the present specification and claims, the term "inwardly with respect to the axial direction" refers to the direction toward the center of the rolling bearing, and "outward" refers to the direction toward the end of the rolling bearing.

上述の様なシールリング９を装着する為に、前記外輪３の軸方向両端部内周面には、凹溝状の係止溝１６を全周に亙り形成している。又、前記内輪５の軸方向両端部外周面には、小径段部１７を全周に亙り形成している。そして、組立状態で、前記各シールリング９の外周縁部に設けた弾性係止部１２を、前記各係止溝１６にそれぞれ係止すると共に、同じく内周縁部に設けた前記第一、第二各シールリップ１４、１５の先端縁を、前記各小径段部１７の側壁面１８に全周に亙り摺接させている。 In order to mount the seal ring 9 as described above, a recessed groove-shaped locking groove 16 is formed over the entire circumference on the inner peripheral surface of both axial ends of the outer ring 3. Further, a small diameter step 17 is formed around the entire circumference on the outer peripheral surface of each end of the inner ring 5 in the axial direction. Then, in the assembled state, the elastic locking portions 12 provided on the outer peripheral edge portion of each seal ring 9 are respectively locked to the respective locking grooves 16 and the first and the second provided on the inner peripheral edge as well. The front end edges of the two seal lips 14 and 15 are in sliding contact with the side wall surface 18 of the small diameter step 17 all around.

ところで、例えばエンジン内部に使用される軸受には、通常０．１ＭＰａ程度の油圧が作用しているが、低温時等には、油圧が０．４ＭＰａ程度にまで上昇する場合がある。上述した様な構成を有する従来構造のシールリング付玉軸受１の場合、前記芯金１０の内周縁部を覆う状態で、軸方向に関する剛性の高いブロック部１３を設けている為、前記各シールリング９の軸方向外側面に作用する矢印方向の油圧が高くなった場合にも、前記ブロック部１３の弾性変形量を抑える事ができる。従って、外部空間に存在する油の油圧に対する強度（変形しにくさ）を意味する、前記シールリング９の耐圧性能を十分に確保できると共に、外部空間に存在する油が前記内部空間８に侵入する事を有効に防止できる。 For example, although a hydraulic pressure of about 0.1 MPa usually acts on a bearing used inside the engine, the hydraulic pressure may rise to about 0.4 MPa at a low temperature or the like. In the case of the seal ring equipped ball bearing 1 of the conventional structure having the configuration as described above, since the block portion 13 having high rigidity in the axial direction is provided in a state of covering the inner peripheral edge portion of the core metal 10 Even when the oil pressure in the arrow direction acting on the axially outer surface of the ring 9 is high, the amount of elastic deformation of the block portion 13 can be suppressed. Accordingly, the pressure resistance performance of the seal ring 9 can be sufficiently ensured, which means the strength (the difficulty of deformation) of the oil present in the external space against the hydraulic pressure, and the oil present in the external space intrudes into the internal space 8 You can prevent things effectively.

但し、上述した様な従来構造の場合には、前記ブロック部１３の軸方向に関する剛性が高い事に起因して、前記第一、第二各シールリップ１４、１５の先端縁と、前記各小径段部１７の側壁面１８との摺接部に作用する摩擦トルクが過大になる。この為、前記シールリング付玉軸受１の回転トルクが大きくなってしまう。又、外部空間に存在する油が前記内部空間８に侵入する事が確実に防止される為、この内部空間８の潤滑状態を良好に維持する事が難しくなる。 However, in the case of the conventional structure as described above, the tip edges of the first and second seal lips 14 and 15 and the small diameter are caused due to the high rigidity of the block portion 13 in the axial direction. The friction torque acting on the sliding contact portion with the side wall surface 18 of the step 17 becomes excessive. For this reason, the rotational torque of the seal ring attached ball bearing 1 is increased. Further, since oil present in the external space is reliably prevented from intruding into the internal space 8, it is difficult to maintain the lubricated state of the internal space 8 in a good condition.

特開２００５−１６３９００号公報JP, 2005-163900, A

本発明は、上述の様な事情に鑑み、回転トルクの低減を図れると共に、外部空間に存在する油を内部空間に適度に供給する事ができ、しかも、シールリングの耐圧性能を確保できる、シールリング付転がり軸受を実現すべく発明したものである。 SUMMARY OF THE INVENTION In view of the above-described circumstances, the present invention can reduce rotational torque, can appropriately supply oil present in the external space to the internal space, and can ensure the pressure resistance performance of the seal ring. It is invented to realize a ring-equipped rolling bearing.

本発明のシールリング付転がり軸受は、外輪と、内輪と、複数個の転動体と、シールリングとを備える。
このうちの外輪は、内周面に外輪軌道を有する。
前記内輪は、外周面に内輪軌道を有する。
前記各転動体は、例えば玉やころ（円筒ころ、円すいころを含む）又はニードル等であり、前記外輪軌道と前記内輪軌道との間に転動自在に設けられている。
前記シールリングは、前記外輪の内周面と前記内輪の外周面との間に存在して、前記各転動体を設置した内部空間の軸方向端部開口を塞ぐものであり、円環状の芯金と、この芯金により補強された弾性材とを備えている。
又、この弾性材のうちで、前記シールリングの径方向外端部に設けられた弾性係止部を、前記外輪の軸方向端部内周面に形成した係止溝に全周に亙って係止すると共に、前記芯金の内周縁部よりも径方向内方に突出する状態で設けられたシールリップの先端縁を、前記内輪の軸方向端部外周面に形成したシール溝の内側壁面に全周に亙り摺接させている。
又、本発明のシールリング付転がり軸受は、外部空間に存在する油を前記シールリップの先端縁と前記シール溝の内側壁面との間を通じて前記内部空間に供給するものである。 The rolling bearing with a seal ring of the present invention includes an outer ring, an inner ring, a plurality of rolling elements, and a seal ring.
Among these, the outer ring has an outer ring raceway on the inner circumferential surface.
The inner ring has an inner ring track on the outer peripheral surface.
Each of the rolling elements is, for example, a ball or a roller (including cylindrical rollers and tapered rollers) or a needle, and is provided so as to be freely rollable between the outer ring raceway and the inner ring raceway.
The sealing ring is present between the inner peripheral surface and the outer peripheral surface of the inner ring of the outer ring, the is intended for closing an axial end opening between the internal air which established the respective rolling elements, circles An annular core metal and an elastic material reinforced by the core metal are provided.
Further, among the elastic members, the elastic locking portion provided at the radially outer end of the seal ring is provided along the entire circumference of the locking groove formed on the inner peripheral surface of the axial end of the outer ring. An inner wall surface of a seal groove formed on an outer peripheral surface of an axial end portion of the inner ring in a tip end edge of a seal lip provided so as to engage and project radially inward from the inner peripheral edge portion of the metal core Contact all around.
The rolling bearing with a seal ring of the present invention supplies oil present in the external space to the internal space through the space between the tip end edge of the seal lip and the inner wall surface of the seal groove.

特に本発明の場合には、前記弾性係止部の軸方向内側面を、この弾性係止部の自由状態で、前記外輪の中心軸に直交する仮想平面に対し、前記係止溝の内側壁面と同方向に同じ角度だけ傾斜させている。
又、前記弾性材は、前記芯金の内周縁部よりも径方向内方に突出した部分のうち、前記シールリップよりも軸方向外側に外側リップを有している。そして、前記外側リップを、前記内輪の外周面のうちで前記シール溝よりも軸方向外側に外れた部分に近接対向させて、当該部分にラビリンスシールを形成している。
又、前記シールリップは、基端側から先端側に向かう程、前記シール溝の内側壁面に近づく方向に傾斜している。
又、前記シールリップのうち、前記シール溝の内側壁面に全周に亙って摺接した先端縁よりも径方向外方に存在する部分（径方向中間部）の軸方向内側面に、軸方向に突出した補助シールリップを設けており、この補助シールリップよりも径方向外方に存在する基端部にくびれ部を設けている。
そして、前記補助シールリップの先端縁と前記シール溝の内側壁面とを隙間を介して対向させ（当該部分にラビリンスシールを形成し）、前記シールリングの軸方向外側面が受ける油圧が高くなった場合に、前記くびれ部を起点に前記シールリップを曲げ変形させる事で、前記補助シールリップの先端縁を前記シール溝の内側壁面に摺接させる。
尚、補助シールリップの先端縁をシール溝の内側壁面に摺接させ始める油圧の大きさは、シールリング付転がり軸受の大きさや、シールリングを構成する芯金及び弾性材の材質等に応じて、設計的に定める事ができる。
又、シール溝及び係止溝の内側壁面とは、それぞれ軸方向外方に向いた側壁面を言う。 In the case of the present invention, in particular, the inner wall surface of the locking groove with respect to a virtual plane orthogonal to the central axis of the outer ring in the free state of the elastic locking portion. It is inclined by the same angle in the same direction.
Further, the elastic member has an outer lip axially outward of the seal lip in a portion projecting radially inward of the inner peripheral edge portion of the metal core. Then, the outer lip is made close to and opposed to a portion of the outer peripheral surface of the inner ring which is axially outside the seal groove, and a labyrinth seal is formed on the portion.
Further, the seal lip is inclined in a direction closer to the inner wall surface of the seal groove as it goes from the proximal end side to the distal end side.
In the seal lip, an axial inner side surface of a portion (radially intermediate portion) radially outward of a tip edge which is in sliding contact with the inner wall surface of the seal groove along the entire circumference. and an auxiliary sealing lip projecting direction, is provided a proximal end wall fin portion existing radially outward of the auxiliary sealing lip.
Then, the tip edge of the auxiliary seal lip and the inner wall surface of the seal groove are made to face each other via a gap (a labyrinth seal is formed in that portion), and the hydraulic pressure received by the axially outer surface of the seal ring is increased. In this case, the tip end edge of the auxiliary seal lip is brought into sliding contact with the inner wall surface of the seal groove by bending and deforming the seal lip starting from the constricted portion.
The magnitude of the hydraulic pressure to start bringing the tip edge of the auxiliary seal lip into sliding contact with the inner wall surface of the seal groove depends on the size of the rolling bearing with seal ring and the material of the core metal and elastic material constituting the seal ring. Can be determined by design.
Further, the sealing groove and the inner wall surface of the locking groove mean a side wall surface directed axially outward.

以上の様な構成を有する本発明のシールリング付転がり軸受によれば、回転トルクの低減を図れると共に、外部空間に存在する油を内部空間に適度に供給する事ができ、しかも、シールリングの耐圧性能を確保できる。
即ち、本発明の場合には、シールリップの基端部にくびれ部を設けている為、このシールリップの曲げ剛性を低くできて、リップ反力を小さくできる。この為、このシールリップの先端縁、及び、このシールリップの径方向中間部に設けられた補助シールリップの先端縁と、シール溝の内側壁面との摺接部に作用する摩擦トルクを低く抑える事ができる。又、前記補助シールリップの先端縁は、シールリングの軸方向外側面が受ける油圧が高くなり、内部空間に油が侵入し易くなった場合にのみ、前記シール溝の内側壁面に摺接し、それ以外の場合には、摺接させずに済む。従って、本発明のシールリング付転がり軸受によれば、回転トルクの低減を図れる。
又、本発明によれば、上述の様に、前記リップ反力を小さくできる為、前記内部空間に油を供給し易くできる。又、前記シールリングの軸方向外側面が受ける油圧が高くなるに従い、前記シールリップの先端縁に加えて、前記補助シールリップの先端縁を、前記シール溝の内側壁面に摺接させ、更に、これらシールリップ及び補助シールリップの締め代を徐々に大きくする事ができる。従って、本発明によれば、前記内部空間に供給される油が過剰になる事を有効に防止できて、この内部空間に適度に油を供給する事ができる。
更に、本発明の場合には、前記シールリングの軸方向外側面が受ける油圧が高くなった場合に、前記シールリップの先端縁だけでなく、この先端縁よりも基端側に設けられた前記補助シールリップの先端縁を、前記シール溝の内側壁面にそれぞれ摺接させる為、シールリングの耐圧性能を向上できる。しかも、本発明の場合には、弾性係止部の軸方向内側面を係止溝の内側壁面と同方向に同じ角度だけ傾斜させている為、この弾性係止部の軸方向内側面を前記係止溝の内側壁面に全周に亙り隙間なく押し付ける事で、前記シールリングの軸方向外側面に作用する油圧に対して、このシールリングが軸方向内方に押し込まれにくくする事ができる。従って、本発明によれば、このシールリングの耐圧性能を確保できる。 According to the rolling bearing with seal ring of the present invention having the above-described configuration, it is possible to reduce the rotational torque, and to appropriately supply the oil present in the external space to the internal space. Pressure resistant performance can be secured.
That is, in the case of the present invention, since the constricted portion is provided at the base end of the seal lip, the bending rigidity of the seal lip can be reduced and the lip reaction force can be reduced. For this reason, the friction torque acting on the sliding contact portion between the tip edge of the seal lip and the tip edge of the auxiliary seal lip provided in the radial direction intermediate portion of the seal lip and the inner wall surface of the seal groove is kept low. I can do things. Further, the tip edge of the auxiliary seal lip is in sliding contact with the inner wall surface of the seal groove only when the hydraulic pressure received by the axially outer surface of the seal ring is high and the oil easily intrudes into the internal space, In the case other than the above, the sliding contact can be avoided. Therefore, according to the rolling bearing with a seal ring of the present invention, the rotational torque can be reduced.
Further, according to the present invention, as described above, since the lip reaction force can be reduced, oil can be easily supplied to the internal space. In addition to the leading edge of the seal lip, the leading edge of the auxiliary seal lip is brought into sliding contact with the inner wall surface of the sealing groove as the hydraulic pressure received by the axially outer surface of the seal ring increases, The interference between the seal lip and the auxiliary seal lip can be gradually increased. Therefore, according to the present invention, it is possible to effectively prevent the oil supplied to the internal space from becoming excessive, and to supply the oil appropriately to the internal space.
Furthermore, in the case of the present invention, when the hydraulic pressure received by the axially outer side surface of the seal ring is high, the tip provided not only at the tip end edge of the seal lip but also at the proximal end side Since the tip end edge of the auxiliary seal lip is in sliding contact with the inner wall surface of the seal groove, the pressure resistance of the seal ring can be improved. Moreover, in the case of the present invention, since the axially inner side surface of the elastic locking portion is inclined by the same angle in the same direction as the inner wall surface of the locking groove, the axially inner side surface of the elastic locking portion is The seal ring can be made difficult to be pushed inward in the axial direction against the hydraulic pressure acting on the axially outer surface of the seal ring by pressing it all around the inner wall surface of the locking groove without any gap. Therefore, according to the present invention, the pressure resistance performance of this seal ring can be secured.

本発明の実施の形態の第１例のシールリング付玉軸受を示す部分断面図。BRIEF DESCRIPTION OF THE DRAWINGS The fragmentary sectional view which shows the ball bearing with a seal ring of the 1st example of embodiment of this invention. 同じく図１のＡ部に相当する拡大図であり、（Ａ）はシールリングの外側面に低い油圧が作用する状態を、（Ｂ）はシールリングの外側面に高い油圧が作用する状態をそれぞれ示す。Similarly, FIG. 1 is an enlarged view corresponding to part A of FIG. 1, in which (A) shows a state in which low oil pressure acts on the outer surface of the seal ring and (B) shows a state in which high oil pressure acts on the outer surface of the seal ring. Show. 同じくシールリングを取り出して示す断面図。Sectional drawing which similarly takes out a seal ring similarly. 本発明の実施の形態の第２例を示す、図３に相当する図。The figure corresponding to FIG. 3 which shows the 2nd example of embodiment of this invention. 従来構造の１例のシールリング付玉軸受を示す断面図。Sectional drawing which shows the ball bearing with a seal ring of one example of conventional structure. 同じくシールリングを取り出して示す断面図。Sectional drawing which similarly takes out a seal ring similarly.

［実施の形態の第１例］
本発明の実施の形態の第１例に就いて、図１〜３を参照しつつ説明する。本例のシールリング付玉軸受１ａは、軸方向中央部内周面に深溝型の外輪軌道２を有し、使用時にも回転しない静止輪である外輪３ａと、軸方向中央部外周面に深溝型の内輪軌道４を有し、使用時に回転する回転輪である内輪５ａと、これら外輪軌道２と内輪軌道４との間に転動自在に設けられた、それぞれが転動体である玉６と、これら各玉６を配置した、前記外輪３ａの内周面と前記内輪５ａの外周面との間に存在する内部空間８の軸方向両端開口部をそれぞれ塞ぐ、円輪状のシールリング９ａとを備えている。又、前記各玉６は、円周方向に互いに等間隔に配置された状態で、保持器７により転動自在に保持されている。 First Example of Embodiment
A first example of the embodiment of the present invention will be described with reference to FIGS. The seal ring ball bearing 1a of this example has a deep grooved outer ring raceway 2 on the inner peripheral surface in the axial direction center, and an outer ring 3a which is a stationary ring that does not rotate even in use; And an inner ring 5a, which is a rotating ring that rotates in use, and balls 6, each of which is a rolling element, rollably provided between the outer ring track 2 and the inner ring track 4; A ring-shaped seal ring 9a is provided, which has the balls 6 arranged, and which closes the openings at both axial ends of the internal space 8 existing between the inner peripheral surface of the outer ring 3a and the outer peripheral surface of the inner ring 5a. ing. The balls 6 are rotatably held by the cage 7 in a state where they are arranged at equal intervals in the circumferential direction.

前記外輪３ａの軸方向両端部内周面には、凹溝状の係止溝１６ａを、旋削加工により全周に亙り形成している。この係止溝１６ａの内側壁面１９は、この係止溝１６ａの旋削加工に伴って傾斜している。具体的には、この内側壁面１９は、前記外輪３ａの中心軸に直交する仮想平面に対して、径方向内方に向かう程軸方向内方に向かう方向に、角度α（例えば３〜１０度程度、図示の例では５度）だけ傾斜している。これに対し、前記内輪５ａの軸方向両端部外周面には、凹溝状のシール溝２０を、やはり旋削加工により全周に亙り形成している。 Recess-shaped engaging grooves 16a are formed around the entire circumference of the outer peripheral surface of each of the outer rings 3a in the axial direction by turning. The inner wall surface 19 of the locking groove 16a is inclined in accordance with the turning process of the locking groove 16a. Specifically, the inner wall surface 19 forms an angle α (for example, 3 to 10 degrees) with respect to a virtual plane orthogonal to the central axis of the outer ring 3a in a direction inward in the axial direction toward inward in the radial direction. The degree is inclined by 5 degrees in the example shown. On the other hand, on the outer peripheral surface at both axial end portions of the inner ring 5a, a seal groove 20 in the form of a recessed groove is formed around the entire circumference by turning as well.

又、前記シールリング９ａは、円環状の芯金１０ａと、この芯金１０ａにより補強されたゴムの如きエラストマー等から成る弾性材１１ａとを備える。この様なシールリング９ａは、図示しない金型のキャビティ内に前記芯金１０ａを配置した後、前記弾性材１１ａを構成する材料を、この芯金１０ａにモールド成形する事により形成される。この様な弾性材１１ａを構成する材料としては、ニトリルゴム、アクリルゴム、シリコンゴム、フッ素ゴム、エチレンプロピレン系ゴム等を採用できる他、塑性変形しにくい水素化ニトリルゴムを採用できる。 The seal ring 9a includes an annular core metal 10a and an elastic material 11a made of an elastomer such as rubber reinforced by the core metal 10a. Such a seal ring 9a is formed by molding the material constituting the elastic member 11a on the cored bar 10a after the cored bar 10a is disposed in a cavity of a mold (not shown). A nitrile rubber, an acrylic rubber, a silicone rubber, a fluororubber, an ethylene propylene type rubber etc. can be employ | adopted as a material which comprises such an elastic material 11a, The hydrogenation nitrile rubber which is hard to be plastically deformed can be adopted.

前記芯金１０ａは、軟鋼板等の金属板を曲げ形成する事により、断面略Ｌ字形で全体を円環状としたものであり、外周面を円筒面状とした円筒部２１と、この円筒部２１の軸方向外端縁（図１〜３の右端縁）から径方向内方に向けて直角に折れ曲がった円輪部２２とを備える。 The cored bar 10a is formed by bending a metal plate such as a mild steel plate so that the entire section is substantially L-shaped and has an annular shape as a whole, and the cylindrical portion 21 whose outer peripheral surface is a cylindrical surface, and this cylindrical portion An annular portion 22 bent at a right angle radially inward from an axially outer end edge (right end edge in FIGS. 1 to 3) 21.

前記弾性材１１ａは、前記シールリング９ａの径方向外端部に設けられた弾性係止部１２ａと、前記円輪部２２の軸方向外側面を全周に亙り覆った薄肉状の円輪覆い部２３と、前記シールリング９ａの径方向内端部に設けられたシール部２４とを備える。このうちの弾性係止部１２ａは、自由状態で、前記係止溝１６ａの幅寸法（軸方向寸法）よりも僅かに大きい幅寸法を有しており、前記芯金１０ａを構成する円筒部２１の外周面、及び、この円筒部２１の先端面（軸方向内端面）を覆っている。又、前記弾性係止部１２ａの軸方向内側面は、自由状態で、前記外輪３ａの中心軸に直交する仮想平面に対し、前記係止溝１６ａの内側壁面１９と同方向に同じ角度（角度α）だけ傾斜している。 The elastic member 11a is a thin circular ring covering all around the elastic locking portion 12a provided at the radial outer end of the seal ring 9a and the axial outer surface of the circular ring portion 22. A portion 23 and a seal portion 24 provided at the radially inner end of the seal ring 9a. Among them, the elastic locking portion 12a has a width dimension slightly larger than the width dimension (axial dimension) of the locking groove 16a in a free state, and the cylindrical portion 21 constituting the cored bar 10a. And the tip end surface (axially inner end surface) of the cylindrical portion 21. In addition, the axially inner side surface of the elastic locking portion 12a has the same angle (angle) in the same direction as the inner wall surface 19 of the locking groove 16a with respect to a virtual plane orthogonal to the central axis of the outer ring 3a in a free state. α) is inclined.

前記シール部２４は、シールリップ（主シールリップ）２５と、内側リップ（グリースリップ）２６と、外側リップ（ダストリップ）２７とを備える。このうちのシールリップ２５は、前記芯金１０ａを構成する円輪部２２の内周縁部よりも径方向内方に、且つ、軸方向内方に突出する状態で設けられており、その先端縁を、前記シール溝２０の内側壁面２８に全周に亙り摺接させている。又、前記シールリップ２５のうちで、前記先端縁よりも径方向外方に存在する径方向中間部の軸方向内側面に、軸方向内方に向けて突出した補助シールリップ２９が設けられている。又、前記シールリップ２５のうちで、この補助シールリップ２９が設けられた部分よりも径方向外方に存在する基端部に、軸方向に関する厚さ寸法が残部に比べて小さくなった、くびれ部３０が設けられている。又、前記内側リップ２６は、断面略三角形状で、前記シール部２４のうちで前記シールリップ２５よりも径方向外方に位置する部分に設けられている。又、前記内側リップ２６の先端縁は、前記内輪５ａの外周面のうちで、前記内輪軌道４と前記シール溝２０との間部分に近接対向しており、当該部分にラビリンスシールを形成している。又、前記外側リップ２７は、断面略矩形状で、前記円輪覆い部２３の内周縁部から径方向内方に延出する状態で設けられている。又、前記外側リップ２７の先端縁（内周縁）は、前記内輪５ａの外周面のうちで前記シール溝２０よりも軸方向外側に外れた部分に近接対向して、当該部分にラビリンスシールを形成している。 The seal portion 24 includes a seal lip (main seal lip) 25, an inner lip (grease lip) 26, and an outer lip (dust lip) 27. The seal lip 25 is provided so as to project radially inward and axially inward of the inner peripheral edge portion of the ring portion 22 constituting the core bar 10a, and the tip end edge of the seal lip 25 is provided. Is in sliding contact with the inner wall surface 28 of the seal groove 20 all around. In addition, an auxiliary seal lip 29 projecting inward in the axial direction is provided on the axially inner side surface of a radially intermediate portion of the seal lip 25 which is located radially outward of the tip edge. There is. Further, at the proximal end portion of the seal lip 25 which is located radially outward of the portion where the auxiliary seal lip 29 is provided, the thickness dimension in the axial direction is smaller than that of the remaining portion. A unit 30 is provided. The inner lip 26 has a substantially triangular cross section, and is provided at a portion of the seal portion 24 located radially outward of the seal lip 25. Further, the tip end edge of the inner lip 26 is close to and opposes a portion between the inner ring race 4 and the seal groove 20 in the outer peripheral surface of the inner ring 5a, and a labyrinth seal is formed in the portion There is. The outer lip 27 is substantially rectangular in cross section and extends radially inward from the inner peripheral edge of the annular ring cover 23. Further, the tip end edge (inner peripheral edge) of the outer lip 27 is closely opposed to a portion of the outer peripheral surface of the inner ring 5a that is axially outside the seal groove 20, and a labyrinth seal is formed in the portion doing.

上述の様な構成を有する前記シールリング９ａは、前記弾性係止部１２ａを、軸方向及び径方向に弾性変形させた状態で、前記係止溝１６ａに弾性的に係止する事により、前記外輪３ａに固定する。そして、この状態で、前記弾性係止部１２ａの軸方向内側面を、前記係止溝１６ａの内側壁面１９に対して全周に亙り隙間なく当接させると共に、前記シールリング９ａの内周縁部に設けられた前記シールリップ２５の先端縁を、前記シール溝２０の内側壁面２８に対して、締め代を持たせた状態で全周に亙り摺接させる。 The seal ring 9a having the above-described configuration elastically locks the locking groove 16a in a state where the elastic locking portion 12a is elastically deformed in the axial direction and the radial direction. It fixes to the outer ring 3a. Then, in this state, the axially inner surface of the elastic locking portion 12a is brought into contact with the inner wall surface 19 of the locking groove 16a all around without any gap, and the inner peripheral edge portion of the seal ring 9a The tip end edge of the seal lip 25 provided on the inner surface of the seal groove 20 is in sliding contact with the inner wall surface 28 of the seal groove 20 around the entire circumference in a state where an interference is given.

特に本例の場合には、前記補助シールリップ２９の先端縁と、前記シール溝２０の内側壁面２８との位置関係を、次の様に規制している。
即ち、前記シールリング９ａの組み付け状態で、前記補助シールリップ２９の先端縁と、前記シール溝２０の内側壁面２８との間には隙間３１を設けておく。そして、前記シールリング９ａの軸方向外側面に油圧が加わり、このシールリング９ａの径方向内方部分が、軸方向内方に向けて押し込まれる場合にも、図２の（Ａ）に示す様に、前記シールリング９ａの軸方向外側面が受ける油圧が低く、押し込まれ量が小さい状態では、前記補助シールリップ２９の先端縁と前記シール溝２０の内側壁面２８とを、隙間３１を介して対向させる。これにより、これら補助シールリップ２９の先端縁とシール溝２０の内側壁面２８との間にラビリンスシールを形成する。これに対し、図２の（Ｂ）に示す様に、前記シールリング９ａの軸方向外側面が受ける油圧が高くなり、押し込まれ量が大きくなった状態では、前記補助シールリップ２９の先端縁を前記シール溝２０の内側壁面２８に全周に亙り摺接させる。本例の場合には、この補助シールリップ２９の先端縁を前記シール溝２０の内側壁面２８に摺接させ始める油圧の大きさを、シールリング付玉軸受１ａの大きさや、前記シールリング９ａを構成する芯金１０ａ及び弾性材１１ａの材質、くびれ部３０の厚さ等に応じて、設計的に定めている。従って、外部空間の油圧が狙いとする値に達した瞬間から、前記補助シールリップ２９の先端縁を、前記シール溝２０の内側壁面２８に摺接させ始める事ができる。又、前記係止溝１６ａを旋削加工により形成する為、この係止溝１６ａの内側壁面１９には傾斜が付いてしまうが、前記弾性係止部１２ａの軸方向内側面の傾斜角度を、この内側壁面１９の傾斜角度に合わせている為、前記シールリング９ａを前記外輪３ａに固定した際に、これら弾性係止部１２ａの軸方向内側面と係止溝１６ａの内側壁面１９との間には隙間が生じずに済む。従って、前記シールリング９ａの軸方向外側面に加わる油圧と、このシールリング９ａの径方向内方部分が軸方向内方に押し込まれる量との関係の誤差を少なくする事ができる。 In particular, in the case of this example, the positional relationship between the tip end edge of the auxiliary seal lip 29 and the inner wall surface 28 of the seal groove 20 is regulated as follows.
That is, in the assembled state of the seal ring 9 a, a clearance 31 is provided between the tip end edge of the auxiliary seal lip 29 and the inner wall surface 28 of the seal groove 20. As shown in FIG. 2A, even when a hydraulic pressure is applied to the axially outer surface of the seal ring 9a and the radially inward portion of the seal ring 9a is pushed axially inward. In the state where the hydraulic pressure received by the axial outer surface of the seal ring 9a is low and the amount of depression is small, the tip edge of the auxiliary seal lip 29 and the inner wall surface 28 of the seal groove 20 are separated by a gap 31. Let them face each other. As a result, a labyrinth seal is formed between the leading edge of the auxiliary seal lip 29 and the inner wall surface 28 of the seal groove 20. On the other hand, as shown in FIG. 2B, when the hydraulic pressure received by the outer surface in the axial direction of the seal ring 9a is high and the amount of pushing is large, the tip edge of the auxiliary seal lip 29 is The entire inner peripheral wall surface 28 of the seal groove 20 is in sliding contact with the entire periphery. In the case of this example, the magnitude of the hydraulic pressure to start the sliding contact of the tip edge of the auxiliary seal lip 29 with the inner wall surface 28 of the seal groove 20, the size of the seal ring ball bearing 1a and the seal ring 9a. The design is determined according to the material of the cored bar 10a and the elastic member 11a to be formed, the thickness of the constricted portion 30, and the like. Therefore, the tip edge of the auxiliary seal lip 29 can be brought into sliding contact with the inner wall surface 28 of the seal groove 20 from the moment when the oil pressure in the external space reaches the target value. Further, since the locking groove 16a is formed by turning, the inner wall surface 19 of the locking groove 16a is inclined, but the inclination angle of the inner surface of the elastic locking portion 12a in the axial direction is Since the seal ring 9a is fixed to the outer ring 3a, it is between the axially inner side surface of the elastic locking portions 12a and the inner wall surface 19 of the locking groove 16a because the inclination angle of the inner wall surface 19 is adjusted. No gaps occur. Accordingly, it is possible to reduce an error in the relationship between the hydraulic pressure applied to the axially outer surface of the seal ring 9a and the amount by which the radially inward portion of the seal ring 9a is pushed axially inward.

上述の様な構成を有する本例のシールリング付玉軸受１ａによれば、回転トルクの低減を図れると共に、外部空間に存在する油を内部空間に適度に供給する事ができ、しかも、シールリング９ａの耐圧性能を確保できる。
即ち、本例の場合には、前記シールリップ２５の基端部にくびれ部３０を設けている為、このシールリップ２５の曲げ剛性を低くできて、リップ反力を小さくできる。この為、このシールリップ２５の先端縁、及び、このシールリップ２５の径方向中間部に設けられた補助シールリップ２９の先端縁と、前記シール溝２０の内側壁面２８との摺接部に作用する摩擦トルクを低く抑える事ができる。又、本例の場合、前記補助シールリップ２９の先端縁は、前記シールリング９ａの軸方向外側面が受ける油圧が高くなり、内部空間８に油が侵入し易くなった場合にのみ、前記シール溝２０の内側壁面２８に摺接し、それ以外の場合には、摺接させずに済む。従って、本例のシールリング付玉軸受１ａによれば、回転トルクの低減を図れる。 According to the seal ring attached ball bearing 1a of the present example having the above-described configuration, it is possible to reduce the rotational torque, and to appropriately supply the oil present in the external space to the internal space. The pressure resistance performance of 9a can be secured.
That is, in the case of the present embodiment, since the constricted portion 30 is provided at the base end of the seal lip 25, the bending rigidity of the seal lip 25 can be reduced and the lip reaction force can be reduced. For this reason, the tip edge of the seal lip 25 and the tip edge of the auxiliary seal lip 29 provided at the radial direction intermediate portion of the seal lip 25 act on the sliding contact portion with the inner wall surface 28 of the seal groove 20. Friction torque can be kept low. Further, in the case of the present embodiment, the tip edge of the auxiliary seal lip 29 is the seal only when the hydraulic pressure received by the outer surface in the axial direction of the seal ring 9a becomes high and the oil easily intrudes into the internal space 8. It is in sliding contact with the inner wall surface 28 of the groove 20, and in the other cases, it is not necessary to make the sliding contact. Therefore, according to the seal ring attached ball bearing 1a of this embodiment, the rotational torque can be reduced.

又、前記リップ反力を小さくできる為、前記内部空間８に油を供給し易くできる。又、前記シールリング９ａの軸方向外側面が受ける油圧が高くなるに従い、前記シールリップ２５の先端縁に加えて、前記補助シールリップ２９の先端縁を、前記シール溝２０の内側壁面２８に摺接させ、更に、これらシールリップ２５及び補助シールリップ２９の締め代を徐々に大きくする事ができる。従って、前記内部空間８に供給される油が過剰になる事を有効に防止できて、この内部空間８に適度に油を供給する事ができる。 Further, since the lip reaction force can be reduced, the oil can be easily supplied to the internal space 8. Further, as the hydraulic pressure received by the axial outer surface of the seal ring 9a becomes higher, the tip edge of the auxiliary seal lip 29 is slid on the inner wall surface 28 of the seal groove 20 in addition to the tip edge of the seal lip 25. In addition, contact between the seal lip 25 and the auxiliary seal lip 29 can be gradually increased. Therefore, excessive supply of oil to the internal space 8 can be effectively prevented, and the internal space 8 can be appropriately supplied with oil.

更に、本例の場合には、前記シールリング９ａの軸方向外側面が受ける油圧が高くなった場合に、前記シールリップ２５の先端縁だけでなく、この先端縁よりも基端側に設けられた前記補助シールリップ２９の先端縁を、前記シール溝２０の内側壁面２８にそれぞれ摺接させる為、前記シールリング９ａの耐圧性能を向上できる。しかも、本例の場合には、前記弾性係止部１２ａの軸方向内側面を前記係止溝１６ａの内側壁面１９と同方向に同じ角度だけ傾斜させている為、前記弾性係止部１２ａの軸方向内側面を前記係止溝１６ａの内側壁面１９に全周に亙り隙間なく押し付ける事で、前記シールリング９ａの軸方向外側面に作用する油圧に対して、このシールリング９ａが軸方向内方に押し込まれにくくする事ができる。従って、このシールリング９ａの耐圧性能を確保できる。 Furthermore, in the case of this example, when the hydraulic pressure received by the axially outer side surface of the seal ring 9a becomes high, it is provided not only at the tip edge of the seal lip 25 but also on the proximal side of this tip edge. Since the tip end edge of the auxiliary seal lip 29 is brought into sliding contact with the inner wall surface 28 of the seal groove 20, the pressure resistance of the seal ring 9a can be improved. Moreover, in the case of the present example, since the axially inner surface of the elastic locking portion 12a is inclined by the same angle in the same direction as the inner wall surface 19 of the locking groove 16a, the elastic locking portion 12a By pressing the inner surface in the axial direction to the inner wall surface 19 of the locking groove 16a all around the periphery without any gap, the seal ring 9a is axially inward with respect to the hydraulic pressure acting on the outer surface in the axial direction of the seal ring 9a. It can be made hard to be pushed in by people. Therefore, the pressure resistance performance of the seal ring 9a can be secured.

［実施の形態の第２例］
本発明の実施の形態の第２例に就いて、図４を参照しつつ説明する。本例の場合には、芯金１０ｂとして、前記実施の形態の第１例で使用したものよりも板厚が小さいものを使用する代わりに、前記芯金１０ｂを構成する円輪部２２ａの径方向内端部に、径方向内方に向かう程軸方向内方に向かう方向に傾斜した折れ曲がり部３２を形成している。そして、この折れ曲がり部３２を覆う状態で、シール部２４を設けている。 Second Example of Embodiment
A second example of the embodiment of the present invention will be described with reference to FIG. In the case of this example, the diameter of the circular ring portion 22a constituting the cored bar 10b is used instead of using a cored bar 10b having a smaller plate thickness than that used in the first example of the embodiment. A bent portion 32 is formed at the inner end portion in the direction so as to be inclined inward in the axial direction as it goes inward in the radial direction. And the seal part 24 is provided in the state which covers this bending part 32. As shown in FIG.

上述の様な構成を有する本例の場合には、前記円輪部２２ａの径方向内端部に、前記折れ曲がり部３２を形成している為、前記芯金１０ｂの剛性を向上させる事ができる。この為、この芯金１０ｂを構成する金属板の板厚を小さくした場合にも、シールリング９ｂの耐圧性能を確保できる。
その他の構成及び作用効果に就いては、前記実施の形態の第１例の場合と同様である。 In the case of the present example having the above-described configuration, since the bent portion 32 is formed at the radially inner end of the annular portion 22a, the rigidity of the metal core 10b can be improved. . Therefore, the pressure resistance performance of the seal ring 9b can be secured even when the thickness of the metal plate constituting the core metal 10b is reduced.
The other configurations and effects are similar to those of the first example of the embodiment.

本発明のシールリング付転がり軸受は、転動体を単列に配置した構造に限らず、複列（２列或いはそれ以上）に配置した構造を採用しても良い。又、転動体としては、玉に限らず、ころ、ニードル等、従来から知られている各種のものを採用できる。 The rolling bearing having a seal ring according to the present invention is not limited to a structure in which rolling elements are arranged in a single row, but may be a structure in which rolling elements are arranged in a double row (two rows or more). Moreover, as a rolling element, not only a ball but various things conventionally known, such as a roller and a needle, are employable.

１、１ａシールリング付玉軸受
２外輪軌道
３、３ａ外輪
４内輪軌道
５、５ａ内輪
６玉
７保持器
８内部空間
９、９ａ、９ｂシールリング
１０、１０ａ、１０ｂ芯金
１１、１１ａ弾性材
１２、１２ａ弾性係止部
１３ブロック部
１４第一シールリップ
１５第二シールリップ
１６、１６ａ係止溝
１７小径段部
１８側壁面
１９内側壁面
２０シール溝
２１円筒部
２２、２２ａ円輪部
２３円輪覆い部
２４シール部
２５シールリップ（主シールリップ）
２６内側リップ（グリースリップ）
２７外側リップ（ダストリップ）
２８内側壁面
２９補助シールリップ
３０くびれ部
３１隙間
３２折れ曲がり部
1, 1a Ball bearing with seal ring 2 Outer ring track 3, 3a Outer ring 4 inner ring track 5, 5a inner ring 6 ball 7 cage 8 internal space 9, 9a, 9b seal ring 10, 10a, 10b metal core 11, 11a elastic material 12 , 12a elastic locking portion 13 block portion 14 first seal lip 15 second seal lip 16, 16a locking groove 17 small diameter step portion 18 side wall surface 19 inner wall surface 20 sealing groove 21 cylindrical portion 22 22a annular ring portion 23 annular ring Cover 24 Seal 25 Seal lip (main seal lip)
26 Inner lip (grease lip)
27 Outer lip (dust lip)
28 inner wall surface 29 auxiliary seal lip 30 constricted portion 31 gap 32 bent portion

Claims

An outer ring having an outer ring raceway on an inner peripheral surface, an inner ring having an inner ring raceway on an outer peripheral surface, a plurality of rolling elements rollably provided between the outer ring raceway and the inner ring raceway, and an inner periphery of the outer ring A ring-shaped seal ring which is present between the surface and the outer peripheral surface of the inner ring and closes an axial end opening of the internal space in which the rolling elements are installed;
The seal ring has an annular core and an elastic member reinforced by the core. Among the elastic members, the elastic ring provided at the radially outer end of the seal ring is provided. The stop portion is provided so as to be locked over the entire circumference in a lock groove formed on the inner peripheral surface of the axial end portion of the outer ring and in a state projecting radially inward of the inner peripheral edge portion of the cored bar The tip edge of the seal lip is in sliding contact with the inner wall surface of the seal groove formed on the outer peripheral surface of the axial end of the inner ring around the entire circumference ,
A rolling bearing with a seal ring, which supplies oil present in an external space to the internal space through between a leading edge of the seal lip and an inner wall surface of the seal groove ,
The axially inner surface of the elastic locking portion is inclined at the same angle in the same direction as the inner wall surface of the locking groove with respect to a virtual plane perpendicular to the central axis of the outer ring in the free state of the elastic locking portion Yes,
The elastic member has an outer lip axially outward of the seal lip among portions projecting radially inward of the inner peripheral edge portion of the core, and the outer lip is a portion of the inner ring A labyrinth seal is formed on the outer peripheral surface close to and facing a portion of the outer peripheral surface that is axially outside the seal groove,
The seal lip is inclined in a direction closer to the inner wall surface of the seal groove from the proximal end toward the distal end.
An axially projecting auxiliary seal lip is provided on the axially inner side surface of a portion of the seal lip that is radially outward of the tip edge in sliding contact with the inner wall surface of the seal groove along the entire circumference. together provided, and proximal end wall fin portion is provided that is present radially outward from the auxiliary sealing lip,
The tip edge of the auxiliary seal lip and the inner wall surface of the seal groove are opposed to each other via a gap, and when the hydraulic pressure received by the axially outer surface of the seal ring is high, the narrow portion is used as a starting point. A rolling bearing with a seal ring characterized in that a tip edge of the auxiliary seal lip is brought into sliding contact with an inner wall surface of the seal groove by bending and deforming the seal lip.