JPH034824Y2 - - Google Patents
Info
- Publication number
- JPH034824Y2 JPH034824Y2 JP17646285U JP17646285U JPH034824Y2 JP H034824 Y2 JPH034824 Y2 JP H034824Y2 JP 17646285 U JP17646285 U JP 17646285U JP 17646285 U JP17646285 U JP 17646285U JP H034824 Y2 JPH034824 Y2 JP H034824Y2
- Authority
- JP
- Japan
- Prior art keywords
- seal
- flange
- inner ring
- outer diameter
- cylindrical portion
- 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
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims 1
- 239000002184 metal Substances 0.000 description 11
- 238000007789 sealing Methods 0.000 description 8
- 238000005452 bending Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 1
- 238000006116 polymerization reaction Methods 0.000 description 1
- 229920003051 synthetic elastomer Polymers 0.000 description 1
- 239000005061 synthetic rubber Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7889—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to an inner race and extending toward the outer race
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7803—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings
- F16C33/7813—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members suited for particular types of rolling bearings for tapered roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
- F16C33/783—Details of the sealing or parts thereof, e.g. geometry, material of the mounting region
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
- F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
Description
〔産業上の利用分野〕
この考案は、自動車或いは一般産業機械に使用
される円すいころ軸受のシールに関するものであ
る。
[Industrial Application Field] This invention relates to a seal for a tapered roller bearing used in automobiles or general industrial machinery.
従来、自動車の歯車減速装置等に使用される円
すいころ軸受用シールとして、第３図乃至第６図
に示すような構造のものがある。
この種のシールは、芯金を軸受内輪の大鍔外径
に嵌合させ、外径側に環状の弾性シール部材を固
着し、又そのシール部材は外輪の大径側端面及び
軸受箱内径に夫々摺接するシールリツプを有して
いる。
第３図のシールは例えば実公昭38−4404号に記
載されているもので、円すいころ軸受１の内輪２
の大鍔外径２ａに嵌合され、且つ内輪２の大鍔側
端面２ｂに密着位置決め固定される。
このシールは円筒部５ａと、その端部から内径
側に延びたフランジ部５ｂとからなる断面略Ｌ字
状の芯金５及び、芯金５の外方に固着され、軸方
向に延び外輪３の大径側端面３ａに摺接するアキ
シアルリップ６ａと、径方向外方に延び軸受箱内
径に摺接するラジアルリツプ６ｂとを一体に有す
るシール部材６からなつている。
このシール４を軸受１に装着する場合、シール
芯金５の円筒部５ａを内輪２の大鍔外径５ａに圧
入し、そのシメシロにてシール４の抜け止めを行
なつている。
しかし、大鍔外径２ａや円筒部５ａの寸法バラ
ツキ或いは形状誤差等により、第４図に示すよう
に円筒部５ａはラツパ状に変形し、実質的に大鍔
外径２ａとのシメシロは減少して、シール４の抜
けの問題が発生する。
又、円筒部５ａの変形θに追従し、シール部材
６も変形θして、予め外輪３の大径側端面３ａと
の間で設定されているシメシロは崩れ、スキマＣ
が生じる事があり、シール性能を著しく低下させ
る。
このようなシール芯金５の変形θを防止するた
めには、従来大鍔外径２ａを研削加工して、その
寸法を厳しく管理する以外になかつた。
又これらの問題点を解決する為に、第５図に示
すシールが提案されている（米国特許第4043620
号）。このシールは内輪２の大鍔側端面２ｂに当
接し、シール４の位置決めを行なうフランジ部７
ｂと大鍔外径２ａに嵌合される円筒部７ａに続
き、この円筒部７ａの剛性増大の為の折り返し部
７ｃからなるシール芯金７と、外輪３の大径側端
面３ａに摺接するアキシアルリツプ６ａと軸受箱
の内径に摺接するラジアルリツプ６ｂを夫々一体
に有するシール部材６とで構成されている。
従つて、折り返し部７ｃの存在の為、圧入時の
芯金変形は解消する。ところが、第６図１部は折
曲部で、実質的にはシメシロがなく、有効ハメア
イ長さは角部７ｂを除いたｍ部のみとなり、減少
してしまう。
又角部７ｂと内輪２との干渉を避ける為には角
部７ｂを大きく盗むか、或いは内輪大鍔の面取り
を大きくせざるを得なく、この種のシールに於い
ては有効ハメアイ長さの減少によりシール装着は
強圧入になり、作業性の点で問題が有つた。
Conventionally, there are seals for tapered roller bearings used in gear reduction devices of automobiles, etc., which have structures as shown in FIGS. 3 to 6. In this type of seal, a core metal is fitted to the outer diameter of the large flange of the bearing inner ring, and an annular elastic seal member is fixed to the outer diameter side, and the seal member is attached to the large diameter end face of the outer ring and the inner diameter of the bearing box. Each has a seal lip that makes sliding contact. The seal shown in Fig. 3 is, for example, the one described in Utility Model Publication No. 38-4404, and is the seal shown in the inner ring 2 of the tapered roller bearing 1.
It is fitted into the large flange outer diameter 2a of the inner ring 2, and is tightly positioned and fixed to the large flange side end surface 2b of the inner ring 2. This seal is fixed to a core metal 5 having a substantially L-shaped cross section and consisting of a cylindrical portion 5a and a flange portion 5b extending radially inward from the end thereof, and to the outside of the core metal 5, extending in the axial direction to the outer ring 5. The seal member 6 integrally includes an axial lip 6a that slides on the large-diameter end surface 3a of the bearing box, and a radial lip 6b that extends radially outward and slides on the inner diameter of the bearing box. When the seal 4 is mounted on the bearing 1, the cylindrical portion 5a of the seal core metal 5 is press-fitted into the outer diameter 5a of the large flange of the inner ring 2, and the seal 4 is prevented from coming off by the interference. However, due to dimensional variations or shape errors in the large flange outer diameter 2a and the cylindrical portion 5a, the cylindrical portion 5a deforms into a rough shape as shown in Fig. 4, and the interference with the large flange outer diameter 2a is substantially reduced. As a result, the problem of the seal 4 coming off occurs. Further, following the deformation θ of the cylindrical portion 5a, the sealing member 6 also deforms θ, and the interference previously set between the outer ring 3 and the large-diameter end surface 3a collapses, and the gap C
may occur, significantly reducing sealing performance. In order to prevent such deformation θ of the seal core metal 5, conventionally the only option was to grind the outer diameter of the large flange 2a and strictly control its dimensions. In order to solve these problems, a seal shown in Fig. 5 has been proposed (U.S. Pat. No. 4,043,620).
issue). This seal comes into contact with the large flange side end surface 2b of the inner ring 2, and the flange portion 7 serves to position the seal 4.
Continuing from the cylindrical portion 7a fitted to the outer diameter 2a of the large flange b, the sealing core 7 consisting of a folded portion 7c for increasing the rigidity of the cylindrical portion 7a slides into contact with the large diameter side end surface 3a of the outer ring 3. The seal member 6 includes an axial lip 6a and a radial lip 6b that slides into contact with the inner diameter of the bearing box. Therefore, due to the presence of the folded portion 7c, deformation of the core metal during press-fitting is eliminated. However, the part 1 in FIG. 6 is a bent part, and there is virtually no seam, and the effective fit length is reduced to only part m excluding the corner part 7b. In addition, in order to avoid interference between the corner 7b and the inner ring 2, it is necessary to make the corner 7b large or to make the chamfer of the inner ring large flange large, and in this type of seal, the effective fit length is Due to the reduction, seal installation required forceful press-fitting, which caused problems in terms of workability.
上記従来の問題点を解決するため、本考案のシ
ールは、内輪２の大鍔外径２ａに嵌合される円筒
部８ａと、シール４を軸受１に装着する時の位置
決め用フランジ部８ｂと、このフランジ部８ｂと
円筒部８ａを連結する折曲重合部８ｃとからなる
シール芯金８、及び外輪３の大径側端面３ａに摺
接するアキシアルリツプ６ａと軸受箱内径に摺接
するラジアルリツプ６ｂを夫々一体に有するシー
ル部材６で構成されている。
In order to solve the above-mentioned conventional problems, the seal of the present invention has a cylindrical portion 8a that fits into the outer diameter 2a of the large collar of the inner ring 2, and a flange portion 8b for positioning when the seal 4 is mounted on the bearing 1. , a seal core bar 8 consisting of a bent overlapping portion 8c connecting the flange portion 8b and the cylindrical portion 8a, an axial lip 6a that slides on the large diameter side end surface 3a of the outer ring 3, and a radial lip 6b that slides on the inner diameter of the bearing box. The sealing members 6 each have an integral part.
以下、この考案による円すいころ軸受用シール
の一実施例を第１図及び第２図を参照して説明す
る。
この実施例のシールは、内輪２の大鍔外径２ａ
に嵌合される円筒部８ａと、この円筒部８ａから
外径方向に折曲され、更にシール４の位置決めフ
ランジ部８ｂに連なる折曲重合部８ｃからなるシ
ール芯金８と、外輪３の大径端面３ａに摺接し、
軸方向のシメシロを付与するアキシアルリツプ６
ａと、軸受箱の内径に摺接し、径方向のシメシロ
を付与するラジアルリツプ６ｂとを夫々一体に有
する合成ゴム等からなる弾性シール部材６とで構
成されている。軸受１にシール４を装着する際、
抜け防止の為、内輪２の大鍔外径２ａとシール芯
金８の円筒部８ａとのシメシロは通常0.05〜0.45
mmと大きく設定され、そのシメシロにより円筒部
８ａは変形δしようとするが、折曲重合部８ｃが
剛性の高い為、その変形δは円筒部８ａのみの微
少な量となる。従つて、変形によるシメシロの低
下は小さく、且つ内輪大鍔部面取部との干渉の恐
れもなく、シール芯金８の有効ハメアイ長さの減
少も最小限に押さえることができる。
尚、シール部材に関してはこの実施例に限定さ
れず、例えば外輪３の転走面に直接摺接する形式
のものでも許容される。
An embodiment of the tapered roller bearing seal according to this invention will be described below with reference to FIGS. 1 and 2. The seal of this embodiment has a large flange outer diameter 2a of the inner ring 2.
A seal core metal 8 consisting of a cylindrical portion 8a that is fitted into the cylindrical portion 8a, a bent overlapping portion 8c that is bent in the outer diameter direction from the cylindrical portion 8a and further connected to the positioning flange portion 8b of the seal 4, and slidingly contacts the radial end surface 3a;
Axial lip 6 that provides axial interference
a, and an elastic seal member 6 made of synthetic rubber or the like, each integrally having a radial lip 6b that slides on the inner diameter of the bearing box and provides radial interference. When installing the seal 4 on the bearing 1,
To prevent it from coming off, the interference between the outer diameter 2a of the large flange of the inner ring 2 and the cylindrical portion 8a of the sealing core 8 is usually 0.05 to 0.45.
mm, and the cylindrical portion 8a tends to undergo deformation δ due to the interference, but since the bending and overlapping portion 8c has high rigidity, the deformation δ is only a small amount in the cylindrical portion 8a. Therefore, the reduction in the interference due to deformation is small, there is no fear of interference with the chamfered portion of the inner ring large flange, and the reduction in the effective fit length of the seal core bar 8 can be suppressed to a minimum. Note that the sealing member is not limited to this embodiment; for example, a sealing member that directly slides into contact with the raceway surface of the outer ring 3 is also acceptable.
この考案の円すいころ軸受用シールによれば、
以下の効果が得られる。
(イ) シール装着時の芯金変形がシールリツプ部ま
で影響せず、所定のシール性能が得られる。
(ロ) シール芯金に径方向に延びる折曲重合部があ
り、剛性が高い為、シール装着時の芯金変形、
倒れを微少に押さえる事が出来る。
(ハ) 従つて、内輪大鍔外径寸法を厳しく管理する
必要がなく、研削工程を除くことが出来る。
(ニ) 内輪大鍔部の面取りを必要最小限に出来る
為、内輪大鍔外径とシール芯金円筒部との有効
ハメアイ長さを大きく取ることが可能である。
According to the tapered roller bearing seal of this invention,
The following effects can be obtained. (a) The deformation of the core metal during seal installation does not affect the seal lip, and the desired sealing performance can be obtained. (b) The seal core metal has a bending and overlapping part that extends in the radial direction and has high rigidity, so the core metal deforms when the seal is attached.
It is possible to suppress the fall to a slight extent. (c) Therefore, there is no need to strictly control the outer diameter dimension of the inner ring large flange, and the grinding process can be eliminated. (d) Since the chamfering of the inner ring large flange can be minimized, it is possible to increase the effective fit length between the inner ring large flange outer diameter and the seal core cylindrical part.
第１図および第２図は、本考案の円すいころ軸
受用シールを装着した一実施例を示す断面図。第
３図乃至第６図は従来の円すいころ軸受用シール
を装着した断面図。
１……軸受、２……内輪、３……外輪、４……
シール、５，７，８……シール芯金、６……シー
ル部材、８ａ……円筒部、８ｂ……フランジ部、
８ｃ……折曲重合部。
1 and 2 are cross-sectional views showing an embodiment of the tapered roller bearing seal of the present invention. 3 to 6 are cross-sectional views of a conventional tapered roller bearing seal. 1... Bearing, 2... Inner ring, 3... Outer ring, 4...
Seal, 5, 7, 8... Seal core metal, 6... Seal member, 8a... Cylindrical part, 8b... Flange part,
8c...Bending polymerization part.
Claims (1)
筒部と、該水鍔側端面に密着位置決め固定される
内径方向に延びるフランジ部と、該フランジ部と
上記円筒部とを連結し、外径方向に延びる折曲重
合部とからなるシール芯金に少なくとも外輪に摺
接するリツプを有する弾性シール部材を一体固着
したことを特徴とする円すいころ軸受用シール。 A cylindrical part that fits into the outer diameter of the inner ring large flange of a tapered roller bearing, a flange part extending in the inner diameter direction that is closely positioned and fixed to the end face on the water flange side, and the flange part and the cylindrical part are connected, 1. A seal for a tapered roller bearing, characterized in that an elastic seal member having a lip that makes sliding contact with at least an outer ring is integrally fixed to a seal core consisting of a bent overlapping portion extending in the radial direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17646285U JPH034824Y2 (en) | 1985-11-16 | 1985-11-16 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17646285U JPH034824Y2 (en) | 1985-11-16 | 1985-11-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6285724U JPS6285724U (en) | 1987-06-01 |
| JPH034824Y2 true JPH034824Y2 (en) | 1991-02-07 |
Family
ID=31116730
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17646285U Expired JPH034824Y2 (en) | 1985-11-16 | 1985-11-16 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH034824Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5327367B2 (en) * | 2012-08-06 | 2013-10-30 | 日本精工株式会社 | Rotational speed detection device for motorcycle wheels |
-
1985
- 1985-11-16 JP JP17646285U patent/JPH034824Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6285724U (en) | 1987-06-01 |
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