JPS6111563Y2 - - Google Patents
Info
- Publication number
- JPS6111563Y2 JPS6111563Y2 JP1980084495U JP8449580U JPS6111563Y2 JP S6111563 Y2 JPS6111563 Y2 JP S6111563Y2 JP 1980084495 U JP1980084495 U JP 1980084495U JP 8449580 U JP8449580 U JP 8449580U JP S6111563 Y2 JPS6111563 Y2 JP S6111563Y2
- Authority
- JP
- Japan
- Prior art keywords
- lip
- spline
- seal
- tapered inner
- inner peripheral
- 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
Links
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 claims description 8
- 239000010687 lubricating oil Substances 0.000 claims description 6
- 230000002093 peripheral effect Effects 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 claims 5
- 239000000853 adhesive Substances 0.000 description 2
- 230000001070 adhesive effect Effects 0.000 description 2
- 238000004026 adhesive bonding Methods 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- JEIPFZHSYJVQDO-UHFFFAOYSA-N iron(III) oxide Inorganic materials O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Landscapes
- Gasket Seals (AREA)
Description
【考案の詳細な説明】
本考案は、主として舶用減速逆転機と機関との
スプライン結合部において使用される潤滑油の密
封装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a lubricating oil sealing device mainly used in a spline connection between a marine speed reducer and an engine.
通常、舶用機関においては、エンジンのフライ
ホイールにダンパーデイスク式の軸継手を固着
し、この軸継手のスプラインハブを、減速逆転機
より突出する入力軸にスプライン係合して、エン
ジンから減速逆転機への動力伝達を行なうように
なつている。この場合、スプラインハブと入力軸
との結合部は潮風にさらされた状態にあり、この
ため該スプライン結合部に錆を発生し、耐久性を
損う虞れがある。 Normally, in a marine engine, a damper disk type shaft joint is fixed to the flywheel of the engine, and the spline hub of this shaft joint is spline-engaged with the input shaft that protrudes from the reduction/reversing gear, so that the engine is connected to the reducing/reversing gear. It is designed to transmit power to. In this case, the joint between the spline hub and the input shaft is exposed to sea breeze, which may cause rust to occur in the spline joint, which may impair its durability.
そこで、この様な不具合を防止するため、従来
においては、第１図の如く、入力軸１ａにスプラ
イン係合したハブ２ａの端部に、弾性体シール３
ａを接着剤等を用いて嵌着し、弾性体シール３ａ
先端の突条４ａを、入力軸１ａの傾斜面５ａに当
接して、弾性体シール３ａの弾性変形によつて、
スプライン結合部の潤滑油を密封したものが使用
されている。しかしながら、このような構造によ
ると、高速回転時の遠心力によつてシール３ａが
外方へ拡開して潤滑油が飛散し、また、接着等の
工程が必要となるため組立が面倒となる欠点があ
つた。 Therefore, in order to prevent such problems, conventionally, as shown in FIG.
a using an adhesive or the like to seal the elastic body 3a.
By bringing the protrusion 4a at the tip into contact with the inclined surface 5a of the input shaft 1a, and by elastic deformation of the elastic seal 3a,
The spline joints are sealed with lubricating oil. However, with such a structure, the seal 3a expands outward due to centrifugal force during high-speed rotation, causing lubricating oil to scatter, and assembly is troublesome because processes such as gluing are required. There were flaws.
また、このような欠点を解消するものとして、
入力軸に外嵌したシールをスプリング等にて押圧
支持するもの（実願昭52−35996参照）が考えら
れているが、かくては部品点数が増大してコスト
高となり、かつ軸方向寸法も長くなる欠点があ
る。あるいは、実公昭37−16950号公報のよう
に、ハブ側に凹部を形成するとともに、この凹部
へ、ゴムリング先端のリツプを間隙をおいて挿入
し、回転時の遠心力によつてこのリツプが前記凹
部内周面に接触させ、これによつてシールを施す
ものがある。しかし、この場合においても、回転
していない時は上記の如く間隙があるため、熱に
よつて流動化した潤滑油がこの間隙から漏れ出た
り或いは埃が侵入する虞れがあり、完全な密封と
は言えないという欠点がある。 In addition, in order to eliminate such drawbacks,
It has been considered to press and support a seal fitted externally on the input shaft with a spring or the like (see Utility Model Application No. 52-35996), but this increases the number of parts, increases cost, and increases the axial dimension. It has the disadvantage of being long. Alternatively, as in Japanese Utility Model Publication No. 37-16950, a recess is formed on the hub side, and the lip at the tip of the rubber ring is inserted into the recess with a gap, so that the lip is removed by centrifugal force during rotation. Some seals are brought into contact with the inner circumferential surface of the recess, thereby providing a seal. However, even in this case, when it is not rotating, there is a gap as mentioned above, so there is a risk that lubricating oil fluidized by heat may leak from this gap or dust may enter, and it is impossible to completely seal it. The drawback is that it cannot be said that
本考案は、上記従来の欠点に鑑みてなされたも
ので、スプリング等特別の支持部材を用いてコス
ト高にすることなく、潤滑油の完全密封を行なう
ことを目的としてなされたものであり、その構成
を一実施例を示す図面に基づいて説明すると以下
の通りである。 The present invention was developed in view of the above-mentioned drawbacks of the conventional technology, and was developed with the aim of completely sealing lubricating oil without increasing costs by using special support members such as springs. The configuration will be described below based on the drawings showing one embodiment.
第２図において、１はエンジンのフライホイー
ル、２は該フライホイール１の外方より後方に突
出する機関側のマウンテイングフランジ、３は、
減速逆転機構を内装するケースであつて、このケ
ース３は、前部側外周にフランジ４を有し、この
フランジ４がマウンテイングフランジ２にボルト
２０にて固着されている。 In FIG. 2, 1 is an engine flywheel, 2 is an engine-side mounting flange that protrudes rearward from the outside of the flywheel 1, and 3 is a
This case 3 has a flange 4 on the outer periphery of the front side, and the flange 4 is fixed to the mounting flange 2 with bolts 20.
５は、ケース３に軸架した入力軸、６は同じく
出力軸であり、これらに取付けた歯車７，７等に
よつて減速・逆転が行なわれるが、入力軸５は、
その前端部近傍にスリーブ型の軸受台８が外嵌さ
れており、この軸受台８部において、ケース壁の
軸受部９に軸受１０を介して支承され、ケース３
より前方へ突出するこの入力軸５の前端外周には
スプライン１１が形成されている。 Reference numeral 5 indicates an input shaft mounted on the case 3, and reference numeral 6 indicates an output shaft. Deceleration and reversal are performed by gears 7, 7, etc. attached to these.
A sleeve-shaped bearing pedestal 8 is externally fitted near the front end portion of the bearing pedestal 8, and in this bearing pedestal 8 portion, the case wall is supported via a bearing 10 by a bearing portion 9 of the case wall.
A spline 11 is formed on the outer periphery of the front end of this input shaft 5 which protrudes further forward.
一方、１２は、円周方向のスプリング１３を介
して動力伝達を行なうダンパー式軸継手であり、
この軸継手１２外周のデイスク１４がフライホイ
ール１側面にボルト固着されるとともに、内周側
のスプラインハブ１５が、上記入力軸５前端のス
プライン１１部に係合され、このようにしてフラ
イホイール１から入力軸５へ動力伝達を行なうよ
うになつている。 On the other hand, 12 is a damper type shaft joint that transmits power via a circumferential spring 13,
The disk 14 on the outer periphery of the shaft joint 12 is bolted to the side surface of the flywheel 1, and the spline hub 15 on the inner periphery side is engaged with the spline 11 at the front end of the input shaft 5. In this way, the flywheel 1 Power is transmitted from the input shaft 5 to the input shaft 5.
しかして、本考案に係るシール１６は、上記軸
受台８とスプラインハブ１５との間に介装される
が、その構造は第３図及び第４図に示す通りであ
る。 The seal 16 according to the present invention is interposed between the bearing pedestal 8 and the spline hub 15, and its structure is as shown in FIGS. 3 and 4.
そこで、これについて説明すると、シール１６
はゴム等の弾性体により環状に形成されて入力軸
５に外嵌されるが、このシール１６に対応して、
軸受台８の端面には環状溝１７が形成され、該シ
ール１６の一端がこの環状溝１７に嵌入して取付
けられるとともに、シール１６の他端には、その
外周部より環状リツプ１８が軸方向に突出され、
その外周面は先端へ向つて小径となるテーパ状に
形成されている。一方、このリツプ１８に対向す
るスプラインハブ１５の端部内周には、上記リツ
プ１８外周に対応して、外側即ち端面側に向つて
大径となるテーパ形内周面１９が形成されてお
り、前記のリツプ１８をこのテーパ形内周面１９
に挿入し、次いで第４図の如く、軸受台８によつ
てシール１６を軸方向へ移動させて、リツプ１８
を押込むと、このリツプ１８が内方へ弾性変形し
てテーパ形内周面１９との接触面圧が増大して密
着し、このシール１６内のスプライン１１部に封
入されたグリース等の潤滑剤が完全にシールされ
た状態となるものである。なお、このようなシー
ル１６の押込みは、前記ケース３の取付けの際、
フランジ４の取付ボルト２０をマウンテイングフ
ランジ２に締付けると同時に行なわれる。 So, to explain this, seal 16
is formed into an annular shape from an elastic body such as rubber and is fitted onto the input shaft 5. Corresponding to this seal 16,
An annular groove 17 is formed in the end surface of the bearing pedestal 8, and one end of the seal 16 is fitted into this annular groove 17 and attached, and an annular lip 18 is attached to the other end of the seal 16 from its outer circumference in the axial direction. is projected to,
Its outer circumferential surface is formed into a tapered shape that becomes smaller in diameter toward the tip. On the other hand, on the inner periphery of the end of the spline hub 15 facing this lip 18, a tapered inner periphery 19 is formed, corresponding to the outer periphery of the lip 18, and the diameter becomes larger toward the outside, that is, toward the end surface. The lip 18 is connected to this tapered inner peripheral surface 19.
As shown in FIG.
When the lip 18 is pushed in, the lip 18 elastically deforms inward, increasing the contact pressure with the tapered inner circumferential surface 19 and making a close contact with the spline 11 of the seal 16. The agent is completely sealed. Note that pushing the seal 16 in this way is necessary when installing the case 3.
This is done simultaneously with tightening the mounting bolts 20 of the flange 4 to the mounting flange 2.
本考案は上記のような構成であり、このように
本考案においては、シールに突設したリツプをス
プラインハブのテーパ形内周面に接触嵌入させて
いるから、第１図の従来の如く遠心力によつて開
くということがなく、むしろ遠心力によつて接触
面が益々増大することから密封が完全となり、ま
た、このシールはスプラインハブと軸受台とによ
つて確実に支持されているから、従来の如く接着
剤やスプリング等を用いる必要がなく、したがつ
て部品コストや組立工数を増加させることがなく
底コストで行なえる利点がある。しかも、本考案
では、スプラインハブのテーパ形内周面へシール
のリツプを接触嵌入することにより、このリツプ
が弾性変形して該テーパ形内周面に密着するか
ら、回転していない時においても完全なシールが
得られ、しかも、リツプの外径を前記テーパ形内
周面の最大外径部よりも小さくしておけば、該リ
ツプは押し込むだけで上記テーパ形内周面に沿つ
て弾性変形し密着するため、組み込みが容易であ
るという効果が得られる。 The present invention has the above-mentioned configuration, and in this way, the lip protruding from the seal is fitted into contact with the tapered inner peripheral surface of the spline hub. It does not open due to force, but rather the contact surface increases due to centrifugal force, so the seal is perfect, and this seal is reliably supported by the spline hub and bearing pedestal. There is no need to use adhesives, springs, etc. as in the conventional method, and therefore there is an advantage that the cost can be reduced without increasing the cost of parts or the number of assembly steps. Moreover, in the present invention, by fitting the lip of the seal into contact with the tapered inner circumferential surface of the spline hub, this lip is elastically deformed and comes into close contact with the tapered inner circumferential surface, even when not rotating. If a perfect seal is obtained and the outer diameter of the lip is smaller than the maximum outer diameter of the tapered inner circumferential surface, the lip will be elastically deformed along the tapered inner circumferential surface just by being pushed. Since they are in close contact with each other, it is easy to assemble them.
第１図は従来例を示すダンパー継手取付部の縦
断面図、第２図は本考案実施例を示すダンパー継
手部の縦断面図、第３図及び第４図は同じく本考
案シール取付部の拡大縦断面図である。
５……入力軸、８……軸受台、１１……スプラ
イン、１５……スプラインハブ、１６……弾性体
シール、１８……リツプ、１９……テーパ形内周
面。
Fig. 1 is a vertical sectional view of a damper joint mounting part showing a conventional example, Fig. 2 is a longitudinal sectional view of a damper joint part showing an embodiment of the present invention, and Figs. 3 and 4 are similar to the seal mounting part of the present invention. It is an enlarged longitudinal cross-sectional view. 5... Input shaft, 8... Bearing stand, 11... Spline, 15... Spline hub, 16... Elastic seal, 18... Lip, 19... Tapered inner peripheral surface.
Claims (1)
該伝動軸を支承するとともに、同じく伝動軸に
は、動力伝達用のスプラインハブをスプライン係
合した動力伝達構造において、前記軸受台の端面
に筒状弾性体シールを嵌着し、この弾性体シール
の他端に設けたリツプを前記スプラインハブ側に
突出せしめるともに、同じくスプラインハブの端
部には、前記軸受台側に向つて大径となるテーパ
形内周面を形成し、このテーパ形内周面に前記リ
ツプを接触嵌入せしめて該リツプを内方へ弾性変
形させ、この変形による弾性による弾性によつて
前記テーパ形内周面へリツプを密着させたことを
特徴とするスプライン結合部の潤滑油密封装置。 In a power transmission structure in which a bearing pedestal is externally fitted onto a transmission shaft, the transmission shaft is supported via this bearing pedestal, and a spline hub for power transmission is spline-engaged with the transmission shaft. A cylindrical elastic seal is fitted to the end face, and a lip provided at the other end of the elastic seal protrudes toward the spline hub. A tapered inner peripheral surface is formed, and the lip is fitted into contact with the tapered inner peripheral surface to elastically deform the lip inwardly, and the elasticity caused by this deformation causes the tapered inner peripheral surface to A lubricating oil sealing device for spline joints characterized by a surface lip that is in close contact with the surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980084495U JPS6111563Y2 (en) | 1980-06-16 | 1980-06-16 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980084495U JPS6111563Y2 (en) | 1980-06-16 | 1980-06-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS578945U JPS578945U (en) | 1982-01-18 |
| JPS6111563Y2 true JPS6111563Y2 (en) | 1986-04-11 |
Family
ID=29446786
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1980084495U Expired JPS6111563Y2 (en) | 1980-06-16 | 1980-06-16 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6111563Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004347118A (en) * | 2003-05-21 | 2004-12-09 | Scania Cv Ab | Splined connection |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5273456B2 (en) * | 2008-10-09 | 2013-08-28 | 住友重機械工業株式会社 | Mounting structure of speed reducer to counterpart machine |
| DE102022131550A1 (en) | 2022-11-29 | 2024-05-29 | Bayerische Motoren Werke Aktiengesellschaft | Rotation-dependent sealing of a shaft connection |
-
1980
- 1980-06-16 JP JP1980084495U patent/JPS6111563Y2/ja not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004347118A (en) * | 2003-05-21 | 2004-12-09 | Scania Cv Ab | Splined connection |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS578945U (en) | 1982-01-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US3741361A (en) | Clutch release bearing | |
| US4551115A (en) | Driveshaft coupling with elastomer damper | |
| JPH07317914A (en) | Coupling oil seal | |
| JPS5937434U (en) | Sealing device for synchronous rotating universal joints | |
| GB2072305A (en) | Wheel coupling | |
| KR20210008734A (en) | Hub built-in type constant velocity joint apparatus | |
| JPH01303377A (en) | Unit of seal joint | |
| JPS6111563Y2 (en) | ||
| US4536038A (en) | Wheel hub assembly for a motor vehicle | |
| KR20080064715A (en) | A sealing arrangement between a constant velocity joint and a hub bearing unit of a motor vehicle wheel | |
| JPH03288041A (en) | Propeller shaft | |
| JP2572621Y2 (en) | Constant velocity joint boots for propeller shafts of automobiles | |
| JPH0118892Y2 (en) | ||
| JPH07167249A (en) | Fluid type torque converter with bridge clutch | |
| JP2016153285A (en) | Connection structure | |
| US5401106A (en) | Bearing assembly with inner race bearing support means | |
| JP3191013U (en) | Oil seal | |
| GB2046873A (en) | Vibration damper for rotating shafts | |
| JP2009228727A (en) | Dust preventing device for joint | |
| US4121841A (en) | Drive shaft seal for compressor housing | |
| GB2151719A (en) | A sealing assembly for a bearing | |
| JPH063201Y2 (en) | Oil leakage prevention structure from the differential carrier | |
| JP3008177U (en) | Self-excited vibration prevention mechanism of mechanical seal | |
| JP2007138977A (en) | End cover installing structure for telescopic shaft | |
| JPS6316900Y2 (en) |