JPS58187656A - Oil seal - Google Patents

Abstract

PURPOSE:To minimize rotational resistance, by providing a communication bore in an annular lip that communicates on the lubricating oil side with a hollow section thereby imparting to the hollow section the negative pressure that will be resulting from the flow of the lubricating oil due to the centrifugal force caused by rotation of a rotating shaft to be sealed. CONSTITUTION:When a rotating shaft 2 is in rotation, and lubricating oil is forced to flow due to the centrifugal force of the rotating shaft 2 along the slant 5b with an angle beta as shown by an arrow (b) so that a negative pressure state is created at a corner 11, the pressure in the hollow section 17 in communication with the negatively pressured corner 11 becomes negative. Then, the annular lip section 5 receives a force radially outward of the rotating shaft in accordance with its pressure difference, and since a second waist part 16 is thin to have a diaphragm function, the second waist port 16 is bent outward in accordance with the pressure difference between the pressures outside and inside the hollow section 17, which overcomes the strain in the annular lip section 5 so that a very fine gap is formed between a contact section 5c and the outer circumference of the rotating shaft 2. Accordingly, the frictional resistance between the annular lip 5 and the rotating shaft 2 can be reduced.

Description

【発明の詳細な説明】 この発明は、回転軸の外周部の液密１行うオイルシール
に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an oil seal that provides liquid tightness to the outer periphery of a rotating shaft.

第１図に従来のオイルシール【断面図で示■。Figure 1 shows a conventional oil seal [shown in cross section].

ｌはケーシング、２は１転軸、Ｂはオイルシールで、第
１図においてケーシングｌ内のオイルシール８の右方に
潤滑油を収容しており、オイルシール８の左方がエア側
である。このオイルシール８は、前記ケーシングｌに固
定される環状基部４と、ケーシングｌに支持された回転
軸ｚ＆：接触ｒる環状リップ部６と、同転軸２の長ざ方
向に延在して環状Ｍ都４と環状リップｓ６とを弾性的に
連結Ｔる塘状紐部６とを有している。環状基品番、環状
リップ都５、環状腰部６６まゴムより成り、環状基Ｆ！
ＡＳ４は會属鯛の補強環７によって補強されている。前
記環状リップ都５の内周側は、エア側に同転軸２外周と
角度α【なＴ傾斜面６ａ％＃滑油負１に回転軸２外周と
αより大なる角度βをな工傾斜（２）６ｂｔ−有して接
触部６ｃか尖った形状をなしており、回転軸１＆：略梅
接触Ｔる。環状リップ部６の外周側には半円状ＩＩＩＴ
面の凹部８が形成され、この凹部８にコイルばねを環状
にしたスプリングｏｒｔ＊装している。ｌＯはダストリ
ップである。l is a casing, 2 is a rotating shaft, and B is an oil seal. In Fig. 1, lubricating oil is stored on the right side of the oil seal 8 in the casing l, and the left side of the oil seal 8 is the air side. . The oil seal 8 includes an annular base portion 4 fixed to the casing l, an annular lip portion 6 that contacts the rotating shaft z supported by the casing l, and an annular lip portion 6 extending in the longitudinal direction of the rotating shaft 2. It has a tang-like string portion 6 that elastically connects the annular M cap 4 and the annular lip s6. Cyclic base part number, cyclic lip cap 5, cyclic waist 66, made of rubber, cyclic base F!
The AS4 is reinforced by a reinforcing ring 7 of a related sea bream. The inner peripheral side of the annular lip 5 is inclined at an angle β larger than α with the outer periphery of the rotary shaft 2 on the air side with the outer periphery of the rotary shaft 2 at an angle α (2) The contact portion 6c has a pointed shape with 6bt, and the rotating shaft 1&: substantially contacts T. On the outer circumferential side of the annular lip portion 6, there is a semicircular IIIT.
A recess 8 is formed in the surface, and a coiled spring ort* is installed in this recess 8. lO is a dust lip.

この従来のオイルシール８の作用ｔ−貌明Ｔると、環状
リップ都６には、回転細雪と環状リップ部すによる締め
代及びその締め代によって変形された環状腰部６０弾性
による締め付は力と、スプリング９の締め付は力とによ
ってＰなる細め付は方１Ｔなわち緊迫力が作用し、環状
リップｇ６の接触部６Ｃか回転軸２に押し付けられて液
密作用【果たしてしする。When this conventional oil seal 8 works, the annular lip cap 6 has a tightening margin caused by the rotating thin snow and the annular lip portion, and an annular waist portion 60 deformed by the tightening margin. The tightening of the spring 9 is caused by a force P, that is, a tension force acts, and the contact portion 6C of the annular lip g6 is pressed against the rotating shaft 2, resulting in a liquid-tight effect.

また、回転軸２０回転時に番ゴ、潤滑油か回転軸２によ
る遠心力Ｔｒ−受けて傾斜（１６ｂに沿って図中矢印（
イ）の如く飛散流動■る。このため、同転−２外周と接
触部５Ｃとが数丁隅部１１か負圧状軟となると共に、前
記流動ｒｔ９！けて接触部５Ｃが押し上げらｔｌ−この
接触部５Ｃは回転軸３外周から極く微小な間隙【もって
離隔Ｔる。一方、接触部６Ｃのエア側においては、回転
軸Ｓの回転による遠心力により空気が傾斜１１０６５１
に沿って流動Ｔるが、傾斜面６ａの角度ａが傾斜面６ｂ
の角度βより小さいため空気の流動は前記潤滑油の流動
に比して抑１＃ｌＪぎれてい心。このため、接触部６Ｃ
（２２潤滑油麹とエア側との間には上記二つの流動によ
る圧力差が生じ、潤滑油側の方がエア側より低圧状態と
なｏｏこの結果、前記接触部５Ｃと回転軸２外周との間
に微小間隙か形成されても＄４？＃油は上記圧力差によ
りシールされることとなる。上記のようなタイプのオイ
ルシールは回転軸２の回転時には回転軸２と非接触状紗
となるため、同転軸２０回転抵抗を生じてしＩうような
ことはなく優れた特性を有■るものである。Also, when the rotating shaft 20 rotates, the lubricating oil or the centrifugal force Tr caused by the rotating shaft 2 causes it to tilt (along arrow 16b in the figure).
The scattering flow is as shown in a). Therefore, the outer periphery of the rotation-2 and the contact portion 5C become under negative pressure at the corner 11, and the flow rt9! When the contact portion 5C is pushed up, the contact portion 5C is separated from the outer periphery of the rotating shaft 3 by an extremely small gap T. On the other hand, on the air side of the contact portion 6C, the air is tilted 110651 due to the centrifugal force caused by the rotation of the rotating shaft S.
The flow T is along the slope 6a, but the angle a of the slope 6a is the slope 6b.
Since the angle β is smaller than the angle β, the flow of air is suppressed compared to the flow of the lubricating oil. For this reason, the contact portion 6C
(22 A pressure difference occurs between the lubricating oil koji and the air side due to the above two flows, and the lubricating oil side is in a lower pressure state than the air side. As a result, the contact portion 5C and the outer periphery of the rotating shaft 2 Even if a minute gap is formed between them, the oil will be sealed due to the above pressure difference.The above type of oil seal will not contact the rotating shaft 2 when the rotating shaft 2 rotates. Therefore, it has excellent characteristics without causing rotational resistance of the co-rotating shaft 20.

しかしながら、Ｆ記のようなオイルシールの液密性に彩
管Ｔる要因がある。■なわち、０回転軸の加工精度によ
る偏心振れ、■オイルシールの加工精度による同心度の
社い、■オイルシールのケーシング取付時の細心の狂い
等である。こｎら鰭要因は総じてオイルシールの追従性
急化【もたらし、上記した従来のオイルシールにおいて
は回転軸２停止時の接触不良によるオイル漏れ、および
回転軸Ｂ４転時の微小間隙が過大となることによるオイ
ル漏れを生じる不具合をもたら■。このたメ、従来のオ
イルシールにあってＣゴ、追従性急化【解消Ｔるために
、必要な細め代（＠コ図ピ）に不した）および、スプリ
ング９により細め付は力により十分な緊迫力を与えて、
オイルシールの回転軸２への追従性１得ている。しかし
ながら、このオイルシールの追従性と前記非接触による
シール作用とは相反Ｔる性質にあり、オイルシールの追
従性ｔ”得るために、あまりオイルシールに緊迫力【与
えてしまうと、回転軸の回転時にあっても、オイルシー
ルは回転軸２外肩と接触伏動となってしまい、回転軸２
に回転抵抗【与えてし！うばかりか、オイルシールの接
触部ａＣも摩耗してしまうという問題点があった。また
、Ｗｈ２図（ロ）に示Ｔ新品セット時に比べて第２図（
／→に示Ｔ摩耗時には、傾斜面６ｂ側の角度βが小さく
なってし！い、前記潤滑油の流動による負圧を十分に得
られなくなってしまう。このため、従来においては、環
状腰部６の長ざを長くして接触部６Ｃの摩耗による角度
βの減少【少しでも防いでいるが、これとて、油滑油の
圧力′ｆｔｗ４状ｊｌｌＩ都６から受けてオイルシール
の緊迫力を増長させてし！つという不具合【生じてしま
うものであった。以上のように従来のオイルシールにあ
っては、回転軸の回転抵抗を減少己せるためのオイルシ
ールの非接触を図らんとしても、微妙な設定条件が要求
されるため、十分な目的過酸を威丁ことかでさなかった
。However, there are factors that affect the liquid tightness of the oil seal as shown in F. (2) Eccentric runout due to the machining accuracy of the 0-rotation axis, (2) Concentricity due to the machining accuracy of the oil seal, and (2) Inaccuracies in the care taken when installing the oil seal casing. These fin factors generally result in a sharper compliance of the oil seal.In the conventional oil seal mentioned above, oil leaks due to poor contact when rotating shaft 2 stops, and the minute gap becomes excessive when rotating shaft B4 rotates. This can lead to problems such as oil leakage. For this reason, in the conventional oil seal, Cgo, followability becomes rapid (in order to eliminate T, the necessary thinning allowance (@ko figure pi) was not made), and the thinning with spring 9 is made by sufficient force. Gives tension,
The ability of the oil seal to follow the rotating shaft 2 is 1. However, the conformability of this oil seal and the above-mentioned non-contact sealing action are contradictory, and in order to obtain the conformability t'' of the oil seal, if too much tension is applied to the oil seal, the rotation shaft Even when rotating, the oil seal comes into contact with the outer shoulder of the rotating shaft 2, causing the oil seal to come into contact with the outer shoulder of the rotating shaft 2.
[Give rotational resistance to it!] In addition, there was a problem in that the contact portion aC of the oil seal also wore out. In addition, compared to the new set of T shown in Figure 2 (B), the difference is shown in Figure 2 (2).
/→ When T wears out, the angle β on the inclined surface 6b side becomes smaller! Otherwise, it becomes impossible to obtain a sufficient negative pressure due to the flow of the lubricating oil. For this reason, in the past, the length of the annular waist portion 6 was increased to prevent the angle β from decreasing due to wear of the contact portion 6C. Take it and increase the tension of the oil seal! One problem [occurred]. As mentioned above, with conventional oil seals, delicate setting conditions are required even if the oil seal does not make contact in order to reduce the rotational resistance of the rotating shaft. I didn't call it Iding.

この発明は上記背景のもとに提案されたもので１液密効
果を充分維持しながら、しかも回転軸の回転に伴なって
、業迫力【減少させて（ロ）転方向抵抗トルクか小とな
るオイルシールを得ることな目的とＴるものである。This invention was proposed based on the above background. 1. While sufficiently maintaining the liquid-tight effect, it also reduces the force of rotation as the rotating shaft rotates, thereby reducing the turning direction resistance torque. The purpose is to obtain an oil seal with a high quality.

以Ｆこの発明の実施例を第３図以下に従って説明Ｔる。Hereinafter, embodiments of the present invention will be described with reference to FIG. 3 and subsequent figures.

なお、１ｌＩ１図と共通Ｔる部分には同じ記号を付して
説明【省略Ｔる。Note that the same symbols are given to the parts common to those in Figure 1lI1 and explained [omitted].

１１１０実施例のオイルシールの自由状態（非装着時）
【示Ｔ＠３図、装着時【示Ｔ第参図において、このオイ
ルシール１８は、環状基部４と回転軸２に内周で接触■
る環状リップ部６とを環状リップ部６の圓転輪長８方向
両側に設けた第１可撓性環状験部（以Ｆ第ｌ腰部と略Ｔ
）１５および第１可撓性環状験ｇ（以Ｆ第１姦部と略Ｔ
）ｌｆｌｔ−介して接続して、環状基部会と環状リップ
酩らとの間に中空部１ｅｔ−形成し％環状リップ孔６＆
−調滑油側と前記中空部１７と【連通させる連通孔１８
を設けている。この実施例の連通孔１８は、潤滑油ａ（
第３図、第参図において右方）の傾斜面ａｂにはぼ直角
に設けられていて、回転軸の一転に伴う圧力変化【正確
に検出できるようにしている。Free state of oil seal of 1110 example (when not installed)
[Illustrated in Figure 3, when installed] In Figure T, this oil seal 18 contacts the annular base 4 and the rotating shaft 2 at the inner circumference.
A first flexible annular portion (hereinafter referred to as the F-th waist portion and approximately T
) 15 and the first flexible annular part g (hereinafter referred to as the first flexible part)
) lflt- connected through the annular lip hole 1et- to form a hollow part 1et- between the annular base part and the annular lip hole 6 &
- Communication hole 18 for communicating between the lubricating oil side and the hollow portion 17
has been established. The communication hole 18 of this embodiment has lubricating oil a (
It is provided almost at right angles to the inclined surface ab (right side in FIG. 3, reference figure), so that pressure changes caused by one turn of the rotation axis can be accurately detected.

また、連通孔１８の中空１１１？への出口はスプリング
９のＦ面位置としているか、こｎは連通孔１８の形成が
容易だからである。前記亀コ紐ａ１６は、ダイヤフラム
として機能させるため、容易にたるみ、あるいは折れ曲
がることができるように薄くしており、前記第１腰酩１
５は、亀コ腰部１６より厚くして、環状リップ部１４の
傾斜面６ａ、６ｂの角度ａ、β【安定して決め易いよう
にしている。Also, the hollow 111 of the communication hole 18? The outlet of the spring 9 is located at the F side of the spring 9 because it is easy to form the communication hole 18. The turtle string a16 is made thin so that it can easily slacken or bend in order to function as a diaphragm.
5 is made thicker than the tortoise waist portion 16 so that the angles a and β of the inclined surfaces 6a and 6b of the annular lip portion 14 can be determined stably and easily.

なお、輛コ＆Ｉ都１６は、壁部１９ｔ−介して環状基部
４に接続ざｎでいるか、この壁部１９は接着剤により環
状基部会に接着（矢印（ハ）部）されている。It should be noted that the carriage 16 is connected to the annular base 4 through a wall 19t, or the wall 19 is bonded to the annular base 4 with an adhesive (arrow (c)).

また、スプリング９を緩装Ｔる凹部８における連通孔１
８の位置には連通【良くＴるための溝８ａ１Ｗｉけてい
る。Also, the communication hole 1 in the recess 8 in which the spring 9 is loosely installed.
At position 8, there is a groove 8a1 for communication.

上述のオイルシール１８の作用について説明Ｔる口 （ロ）転軸２か静止している時をま、空気で満た２れた
中空部１７内の圧力は静止した潤滑油の圧力と釣り会っ
ており、環状リップ部５に作用Ｔる緊迫力はそれらの圧
力に影響されず、主としてスプリング９による緊迫力に
よって環状リップ都６の接触＆６Ｃか回転軸２に押し付
けらｎて、液密作用を果たＴ。Explanation of the action of the oil seal 18 mentioned above: When the rotating shaft 2 is stationary, the pressure in the hollow part 17 filled with air balances the pressure of the stationary lubricating oil. Therefore, the tension force acting on the annular lip portion 5 is not affected by these pressures, and the tension force mainly due to the spring 9 causes the annular lip portion 6 to come into contact with the rotating shaft 2 and press against the rotating shaft 2, thereby achieving a liquid-tight action. T.

回転軸８が回転している時は、潤滑油は回転軸２の遠心
力により大きな角度βの傾斜面６ｂに沿って矢印に）の
如く飛散して流ｎて隅ｉｌｌか負圧状態になり、また環
状リップ都５のエア側の隅部１ｇでは、空気は小ざな角
度αの傾斜面６ａ＆：沿って矢印（ホ）の如く流れるの
であまり負圧状態とならず、したかつて両隣１１１１．
ＩＢの圧力差の関係からＮ＃油がエア側に流出■るのを
防ぐことかでき＾。When the rotating shaft 8 is rotating, the lubricating oil is scattered as shown by the arrow () along the inclined surface 6b having a large angle β due to the centrifugal force of the rotating shaft 2, and a negative pressure is created in the corner. Also, at the corner 1g of the annular lip 5 on the air side, the air flows along the inclined surface 6a &: of the small angle α as shown by the arrow (e), so there is not much negative pressure.
Due to the pressure difference between IB, it is possible to prevent N# oil from flowing to the air side.

そして、潤滑油側の隅１ｆｌＳｌｌが上述のとおり負圧
となるので、この負圧の隅ｓｔｉに連通孔１８か介して
通じている中空部１７の気圧は負圧となる◎■なわち、
中空ｉ１？内の気圧は外部の圧力より低くなり、環状リ
ップ都６には、その圧力差に応じて回転軸半径方向外方
向に力【受け、そして、第−ｌ１ｉｌ！！部１６か博く
ダイヤフラム機能を有Ｔるので、中空部１７の内外の圧
力差に応じて島コｈｅＢ１６が外方向に撓み環状リップ
Ｗ６６に生じる緊迫力＆：チｊち勝って接触部５Ｃと回
転軸Ｓ外崗さの間に極く微小な間隙を形成Ｔる。したか
って環状リップ都すと回転軸２との摩擦抵抗か減少し一
同転軸８に対Ｔる１転方向抵抗トルクが減少Ｔる。Then, since the corner 1flSll on the lubricating oil side becomes a negative pressure as described above, the air pressure in the hollow part 17 that communicates with this negative pressure corner sti via the communication hole 18 becomes a negative pressure.
Hollow i1? The internal pressure becomes lower than the external pressure, and the annular lip 6 receives a force in the radial direction of the rotating shaft outward in accordance with the pressure difference. ! Since the portion 16 has a wide diaphragm function, the island heB16 bends outward in response to the pressure difference between the inside and outside of the hollow portion 17, and the tension force generated on the annular lip W66 overcomes the contact portion 5C. An extremely small gap is formed between the outer and outer sides of the rotating shaft S. Therefore, when the annular lip is closed, the frictional resistance with the rotating shaft 2 decreases, and the resistance torque in one rotation direction against the rotating shaft 8 decreases.

なお、回転時＆：はＸ迫力がなくても、前述した如き遠
心力の作用による隅部１１の負圧化現象によって液密作
用は充分に維持Ｈｎる。Incidentally, during rotation, even if there is no X force, the liquid-tight effect is sufficiently maintained due to the negative pressure phenomenon in the corner 11 due to the action of centrifugal force as described above.

また、従来のオイルシールの場合、環状リップ部６の購
耗対策もあって傾斜ｌ０６ａの角度ａ【ｌ！ＩＬ′〜コ
Ｏ０、傾斜面６ｂの角度Ｉｒｅｓ♂〜６Ｉに設定してい
るが、本発明の如く回転軸３の一転途度の増加につれて
緊迫力か減少■るものでは、環状リップ部５と回転軸２
との間の摩擦か減少し、環状リップ部５の接触部５Ｃの
摩耗も減少■るので、環状リップ都５の接触部５Ｃをよ
り鋭角にＴることかできる。■なわち角度β【より大き
くとることかできる。角度βを大さくとることによって
、潤滑油の＃Ｉ斜面５ｂに沿う流れが速くなって隅部１
１の負圧がより大となり、潤滑油流出防止の作用を一層
効果的なものとＴることかでき６０＠！図は第２の実施
例【示Ｔもので、このオイルシールｇｚは、環状リップ
都５の接触部ａＣｔ−幅広く形成して、回転軸Ｂに対し
て面接触【Ｔるようにし、この接触部６Ｃに全周にわた
る周溝２４を形成し、こり周溝３４に連通孔１８を臨ま
せている。また、接触部６Ｃの幅か広く傾斜面５ａ。In addition, in the case of the conventional oil seal, the angle a[l! Although the angle of the inclined surface 6b is set to IL'~koO0 and the angle Ires♂~6I of the inclined surface 6b, in the case where the tension force decreases as the degree of rotation of the rotating shaft 3 increases, as in the present invention, the annular lip portion 5 and Rotating axis 2
Since the friction between the annular lip portion 5 and the contact portion 5C of the annular lip portion 5 is reduced, the contact portion 5C of the annular lip portion 5 can be made at a more acute angle. ■That is, the angle β [can be made larger. By increasing the angle β, the flow of lubricating oil along the #I slope 5b becomes faster, and the corner 1
The negative pressure of 1 becomes larger, making the lubricating oil leakage prevention effect even more effective.60＠! The figure shows a second embodiment [T], and this oil seal gz is formed so that the contact portion aCt of the annular lip cap 5 is wide and in surface contact [T] with the rotating shaft B, and this contact portion A circumferential groove 24 extending over the entire circumference is formed in 6C, and the communication hole 18 is made to face the circumferential groove 34. Further, the width of the contact portion 6C is wide and the inclined surface 5a is wide.

６ｂの角度α、βか安定し易いため、第ｌ紐部１６は環
状リップ都５が横転しないように連結Ｔる程度の薄ざで
よい。その他の部分について６ゴ、１８３図、島参図の
オイルシールｌＢと同様なので同じ記号）付して説明【
省略する。Since the angles α and β of 6b are easily stabilized, the first string portion 16 may be thin enough to connect to prevent the annular lip capital 5 from overturning. The other parts are the same as the oil seal 1B in Figure 6, Figure 183, and Shimanazan, so they are explained with the same symbol) [
Omitted.

この実施例の作用ｒｔ＠、四Ｔ６゜ −転軸Ｓか静止している時、環状リップ７１６の接触１
％６ｃは１スプリング９による緊迫力によって（ロ）転
軸２に押し付けらｎ１液密作＃１ｔ−果た工。The effect of this embodiment rt@, 4T6° - when the rolling axis S is stationary, the contact 1 of the annular lip 716
%6c is pressed against (b) rotating shaft 2 by the tension force of 1 spring 9, n1 liquid-tight work #1t-work.

この場合、幅の広い接触部６Ｃと回転軸２との聞は、ラ
ビリンスパツキンとしての作用をなＴので液密効果が高
い。In this case, the space between the wide contact portion 6C and the rotating shaft 2 acts as a labyrinth packing, so that the liquid-tight effect is high.

回転軸Ｂが回転している時には、環状リップ酩５の潤滑
油側の隅ａｌｌが遠心力によって謝【述の如く負圧にな
る。そして、輪の広い接触部５Ｃと回転軸２外周との闇
がラビリンスパツキンとしての作用をなＴＵ）で、接触
部６Ｃの申開にある周溝８４内の圧力は１Ｍａｌｌの負
圧よりは小ざいがや番ゴリ負圧状龜となっている。周溝
２４内が負圧であるから中空部１７内が負圧となる０し
たがって抱ｌの実施例の場合と同様に環状リップ部５に
生じる緊迫力に打ち勝って微小間［）形成し、摩擦抵抗
を減少させ、回転軸２に対Ｔる回転方向抵抗トルク【減
少３せる作用が生じる。When the rotating shaft B is rotating, all corners of the annular lip 5 on the lubricating oil side become under negative pressure due to centrifugal force as described above. Then, the darkness between the wide ring contact part 5C and the outer periphery of the rotating shaft 2 acts as a labyrinth packing (TU), and the pressure in the circumferential groove 84 at the opening of the contact part 6C is smaller than the negative pressure of 1Mall. It is a negative pressure type chamber. Since the inside of the circumferential groove 24 is under negative pressure, the inside of the hollow part 17 is under negative pressure. Therefore, as in the case of the embodiment shown in FIG. The effect of reducing the resistance and reducing the rotational direction resistance torque relative to the rotating shaft 2 occurs.

また回転軸Ｓの回転か停止した際には、エア伽から中φ
ｍｌ？への空気の導入か容易に行わｒＬるので、停止の
際の中空部１７内の気圧の回復か速やかであり、したか
って環状リップ都６の復帰性は良好である。In addition, when the rotation of the rotating shaft S stops, the middle φ
ml? Since air can be easily introduced into the hollow part 17, the atmospheric pressure in the hollow part 17 can be quickly recovered when the engine is stopped, and therefore the annular lip cap 6 can be easily restored.

なお、第コ実施例において、第１の実施例と同様に連通
孔を潤滑油側の＃１斜面６ｂにほぼ直角に設けることも
できる。In the fourth embodiment, the communication hole can be provided at a substantially right angle to the #1 slope 6b on the lubricating oil side, as in the first embodiment.

第６図は＠３の実施例をボＴもので、例えば第２の実施
例のオイルシールにおいて（第１の実施例の場合も同様
に適用できるか、第２の実施例の場合で説明Ｔる）、環
状リップ都５の潤滑油側に鍔部８６を設けたものであ６
゜ こり！ｊ！施例においては、環状リップＦＡ！、６の＃
滑油側の傾斜面５ｂに沿って流れる潤滑油か鍔部Ｂ６の
内周面１ａ６Ｊｌに当ってこｒＬを押し上けるので、環
状リップ部６に生じる緊迫力を減少させる作用ｔ−なし
・中空［１？および連通孔１８による作用と相まって緊
迫力減少の効果か晶まる。また不発明は従来のオイルシ
ールのような環状腰部６を有しないためｓａｍ圧により
オイルシールの緊迫力が増大してしソうごともない。Fig. 6 shows the embodiment @3, for example, in the oil seal of the second embodiment (I will explain whether it can be applied in the same way to the case of the first embodiment or not, in the case of the second embodiment). ), a flange 86 is provided on the lubricating oil side of the annular lip 5 .
゜Kori! j! In the example, the annular lip FA! , # of 6
The lubricating oil flowing along the inclined surface 5b on the lubricating oil side hits the inner circumferential surface 1a6Jl of the flange B6 and pushes up this rL, so the effect of reducing the tension force generated on the annular lip 6 is absent/hollow [ 1? Coupled with the effect of the communication hole 18, the effect of reducing the tension force is crystallized. Furthermore, since the oil seal of the present invention does not have an annular waist portion 6 like a conventional oil seal, the tension force of the oil seal does not increase due to sam pressure.

以上の実施例は環状リップ部が単一のものであるか１第
７図に不■ように環状リップ部５【コ個所に持つダブル
リップ型のオイルシールｚ８に適用Ｔることかできる。The above embodiments can be applied to a double-lip type oil seal z8 having a single annular lip portion or having an annular lip portion 5 at the location shown in FIG.

また−、ｙｉｓｔ図にボＴように傾斜面６ｂに連通孔１
８に通じる切欠１ａ？ｉｉ−設けると、潤滑油の流動に
よるジェット効果により中空ｓｉ　？ｔ′より効果的に
負圧伏１に導くことかできる〇 なお、本発明のオイルシールは内燃機＠【始め、■べて
の機械部品の回転軸部に適用しつるものである。Also, as shown in the yist diagram, the communication hole 1 is provided on the inclined surface 6b.
Notch 1a leading to 8? ii-If provided, the jet effect caused by the flow of lubricating oil will create a hollow si? The oil seal of the present invention can be applied to the rotating shafts of all mechanical parts of internal combustion engines.

以上説明したように本発明において目、環状基部と環状
リップ部と′ｆｒ−環状リツブすの両匈の可撓性環状腰
部【介して接続して中空部を形成し、環状リップｈ＆：
＃滑油仙と中空部と【連通させる連通孔を設けているの
で、回転軸の（ロ）転時に番ゴ、遠心力による潤滑油の
流動に伴って生じる負圧が中空部内に及び、中空部の内
外の圧力差により環状リップ恥に作用■る緊迫力に打ち
勝つことかできる。したかつて、環状リップ都と回転軸
との摩擦抵抗を小さくＴｏことかでさ、回転軸に対■る
同転方向抵抗トルクを減少させることかでさ、機械効率
の向上に大さく真献Ｔる。また、環状リップ都Ｑｉｌｌ
ｉ耗防止の効果も大きく、オイルシールの耐久性が同上
Ｔる１１種々の効果を得ることかでざる。As explained above, in the present invention, the annular base, the annular lip, and the flexible annular waist part of both the annular ribs are connected to form a hollow part, and the annular lip h&:
#Since a communication hole is provided to communicate between the lubricant and the hollow part, the negative pressure generated by the flow of lubricating oil due to centrifugal force reaches the hollow part when the rotating shaft rotates (B) and the hollow part. It is possible to overcome the strain acting on the annular lip due to the pressure difference between the inside and outside of the lip. In the past, it has been a great contribution to improving machine efficiency by reducing the frictional resistance between the annular lip and the rotating shaft, and by reducing the synchronous resistance torque against the rotating shaft. Ru. Also, the annular lip capital Qill
It is also highly effective in preventing wear and improves the durability of the oil seal.

【図面の簡単な説明】[Brief explanation of drawings]

第１図は従来のオイルシールの断面図、第２図（イ）、
（ロ）、（ハ）は第１図のオイルシールの各１様を不Ｔ
要部断面図、第３図以Ｆは本発明の実施例を示Ｔもので
、第３図は＠／の実施例の要す断面図、１ａ参図６１第
３図のオイルシールの装着時の断面図、′ａ％Ｓ図６ゴ
１１８コの実施例【示■要部断面図１第６図は第３の実
施例【ン１ζ丁要酩断面図、第７図は箪ダの実施例【示
ＴＩＬ！都断面図、ＩｐＩｇ図４：を第３の実施例を示
Ｔ填状すップ品断面図である。 ｌ・・・・・・ケーシング、２・・・・・・回転軸、４
・・・・・・環状基部、ト・・・・・環状リップ都、６
ａ、６ｂ・・・・・・傾斜面、６Ｃ・・・・・・接触部
、１１，１ｇ・・・・・・隅部、１Ｂ。 ａｓ、ａｓ・・・・・・オイルシール、１６・・・・・
・＠　／　ｉｒＪ　７１８性腺部、１６・・・・・・褐
コ司撓性飯都、ｌ？・・・・・・中空ｇ、ｔｓ・・・・
・・連通孔。 出馳人　本田技研工業株式会社 ；　・、 代理人　弁畑土　志　賀　正　武１．　　トノ 第５図 第６図 第８図Figure 1 is a cross-sectional view of a conventional oil seal, Figure 2 (a),
(B) and (C) are for each type of oil seal shown in Figure 1.
Cross-sectional views of essential parts, Figures 3 to F show embodiments of the present invention. Figure 3 is a cross-sectional view of the embodiment of @/, 1a, Figure 61, when the oil seal shown in Figure 3 is installed. Figure 6 is a sectional view of the third embodiment, and Figure 7 is a cross-sectional view of the main parts. Example [Show TIL! FIG. 4 is a cross-sectional view of a T-shaped cup product showing a third embodiment. l...Casing, 2...Rotating shaft, 4
・・・・・・Annular base, ・・・Annular lip capital, 6
a, 6b... Slope, 6C... Contact portion, 11, 1g... Corner, 1B. as, as...Oil seal, 16...
・@/irJ 718 gonadal part, 16... Brown Koji flexible Iito, l? ...Hollow g, ts...
・Communication hole. Presenter Honda Motor Co., Ltd.; Agent Masatake Shiga Benhata 1. Tonneau Figure 5 Figure 6 Figure 8

Claims (1)

【特許請求の範囲】 ｃ＋＋　　６−滑油ご収容したケーシングに固定される
環状基部と端部かケーシングに支持２れた回転軸に内周
で接触■る環状リップ都とｒｔｌＩＡ状リップ部の回転
軸長ざ方向内Ｉｔの可撓性環状ＩｌｉｉＩｗ６【介して
接続して環状基部と環状リップ部との闇に環状の中空部
を形成し、ｌｔＩ紀填状リップ部に調ｍ油側と前記中空
部と【連通させる連通孔を設けたこと【特徴と■るオイ
ルシール。 ＋２１　１＋＋記環状リップ部の内周の回転軸との接触
部【幅広く形成し、前記環状リップ酩が同転軸にＩｌｋ
＋接触Ｔるようにした特ｉｆＦ１ｍ求の範囲纂１項記載
のオイルシール。[Claims] c++ 6- Rotation of an annular lip fixed to a casing containing lubricating oil and an annular lip whose inner periphery contacts a rotating shaft supported by the casing or a rotating shaft supported by the casing. The annular base and the annular lip are connected through a flexible annular IliIw6 in the axial length direction to form an annular hollow in the gap between the annular base and the annular lip, and the oil side and the hollow are connected to the annular lip. The oil seal features a communication hole that communicates with the part. +21 1++ Contact portion of the inner circumference of the annular lip portion with the rotating shaft
+An oil seal as described in item 1 of the range summary for the specific ifF1m, which is designed to have contact T.