JPH0544618Y2 - - Google Patents
Info
- Publication number
- JPH0544618Y2 JPH0544618Y2 JP7033588U JP7033588U JPH0544618Y2 JP H0544618 Y2 JPH0544618 Y2 JP H0544618Y2 JP 7033588 U JP7033588 U JP 7033588U JP 7033588 U JP7033588 U JP 7033588U JP H0544618 Y2 JPH0544618 Y2 JP H0544618Y2
- Authority
- JP
- Japan
- Prior art keywords
- sliding
- seal
- sliding ring
- groove
- circumferential
- 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 - Lifetime
Links
- 230000002093 peripheral effect Effects 0.000 claims description 5
- 239000000463 material Substances 0.000 claims description 2
- 230000013011 mating Effects 0.000 description 8
- 238000007789 sealing Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
Landscapes
- Mechanical Sealing (AREA)
Description
【考案の詳細な説明】
〔産業上の利用分野〕
本考案は、機器の回転軸周を密封するメカニカ
ルシールの改良に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to an improvement of a mechanical seal that seals around the rotating shaft of a device.
従来から、第２図に示すように、ハウジング５
１内周に気密的に嵌着された非回転の摺動リング
５２と、シヤフト５３外周に周方向に係合した状
態で気密的に装着されて回転する摺動リング５４
が、その対向端面においてバネ５５からの軸方向
荷重により対接し軸封作用を行なうメカニカルシ
ールには、硬度が異なる両摺動リング５２，５４
のうちの軟質側（図示の例では摺動リング５４）
の対接部５６に、該対接部５６と同心の円周溝５
７および該円周溝５７とシール外周空間Ｓ２とを
連通する複数の切欠溝５８を形成したものがあ
る。
Conventionally, as shown in FIG.
1. A non-rotating sliding ring 52 that is airtightly fitted to the inner periphery of the shaft 53, and a rotating sliding ring 54 that is airtightly fitted to the outer periphery of the shaft 53 and engaged in the circumferential direction.
However, the mechanical seal, which performs a shaft sealing action by facing each other due to the axial load from the spring 55 on its opposing end surfaces, has both sliding rings 52 and 54 of different hardness.
the soft side (sliding ring 54 in the illustrated example)
A circumferential groove 5 concentric with the contact portion 56 is provided in the contact portion 56 of the contact portion 56 .
7 and a plurality of notched grooves 58 are formed to communicate the circumferential groove 57 and the seal outer circumferential space S2.
このような構成のメカニカルシールは、たとえ
ばシール対象が気体であつてすなわちドライ条件
で使用されるもの等にみられ、シール作用は摺動
リング５４における円周溝５７の内周側の摺動シ
ール面５６ａとこれに対接する相手摺動リング５
２との間で行なわれ、円周溝５７の外周側の補助
受圧面５６ｂは前記摺動シール面５６ａにおける
単位面積あたりの負荷を低減して早期摩耗等を抑
止する作用を担つている。また、切欠溝５８は、
円周溝５７に侵入した摩耗粉をシール外周空間へ
排出する作用等をなす。 Mechanical seals with such a configuration are found, for example, in those that seal gas and are used under dry conditions. The surface 56a and the mating sliding ring 5 that is in contact with the surface 56a
2, and the auxiliary pressure receiving surface 56b on the outer peripheral side of the circumferential groove 57 has the function of reducing the load per unit area on the sliding seal surface 56a and suppressing premature wear. Moreover, the notch groove 58 is
It functions to discharge wear particles that have entered the circumferential groove 57 into the seal outer peripheral space.
しかし、上記メカニカルシールは、摺動シール
面５６ａと補助受圧面５６ｂが同一の高さである
ため、第３図に誇張して示すように、仕上げ精度
や組み込み精度の誤差等により、使用初期におい
て、相手摺動リング５２に対してたとえ僅かでも
補助摺動面５６ｂが摺動シール面５６ａよりも先
に接触しているような部分があると、切欠溝５８
から円周溝５７を経て、シール外周空間Ｓ１のシ
ール対象流体が大気側空間Ｓ２へ漏洩してしまう
といつた問題があつた。そしてこの場合、摺動に
伴なう経時的な摩耗によつて摺動シール面５６ａ
および補助受圧面５６ｂが完全に相手摺動リング
５２の対向面と密接状態となる（馴染む）までに
多量の漏洩量に達してしまうのを避けることがで
きなかつた。
However, in the above-mentioned mechanical seal, since the sliding seal surface 56a and the auxiliary pressure receiving surface 56b are at the same height, as shown exaggeratedly in FIG. If there is a portion where the auxiliary sliding surface 56b contacts the mating sliding ring 52 earlier than the sliding sealing surface 56a, even if only slightly, the notched groove 58
There was a problem in that the fluid to be sealed in the seal outer circumferential space S1 leaked into the atmosphere side space S2 through the circumferential groove 57. In this case, the sliding seal surface 56a is damaged due to wear over time due to sliding.
Furthermore, it was impossible to avoid a large amount of leakage occurring before the auxiliary pressure receiving surface 56b completely came into close contact (fitted) with the opposing surface of the mating sliding ring 52.
そこで本考案は、上記問題に鑑み、メカニカル
シールの初期漏洩を防止する目的でなされたもの
である。 In view of the above-mentioned problems, the present invention has been devised for the purpose of preventing the initial leakage of mechanical seals.
上記目的達成のため、本考案のメカニカルシー
ルは、軟質側の摺動リングの対接部のうち、円周
溝の内周側に位置する摺動シール面の高さを、そ
の外周側にあつて切欠溝が形成された補助受圧面
よりも僅かに高くした構成とした。
In order to achieve the above objective, the mechanical seal of the present invention has a height of the sliding seal surface located on the inner peripheral side of the circumferential groove among the contact parts of the sliding ring on the soft side. The pressure receiving surface is slightly higher than the auxiliary pressure receiving surface on which the notched groove is formed.
本考案によれば、使用初期において円周溝内周
の摺動シール面が切欠溝を有する外周の補助受圧
面よりも先に確実に相手摺動リングの対向面と接
触し、このとき補助受圧面が非接触であるため摺
動シール面における単位面積あたりの荷重が大き
く、したがつて初期シール性が向上する。また、
前記のように、初期において摺動シール面に対す
る荷重が大きく、該摺動シール面は摩耗を受ける
が、外周側の補助受圧面との高低差は僅かである
ため僅かな摩耗によつて該補助受圧面が相手摺動
リングと接触し前記荷重を分担して受け、摺動シ
ール面の負荷は軽減される。
According to the present invention, in the initial stage of use, the sliding seal surface on the inner circumference of the circumferential groove reliably contacts the opposing surface of the mating sliding ring before the auxiliary pressure receiving surface on the outer periphery having the notched groove, and at this time, the auxiliary pressure receiving surface Since the surfaces are non-contact, the load per unit area on the sliding seal surface is large, thus improving the initial sealing performance. Also,
As mentioned above, the load on the sliding seal surface is large in the initial stage, and the sliding seal surface is subject to wear, but since the difference in height from the auxiliary pressure-receiving surface on the outer circumferential side is small, the auxiliary pressure-receiving surface is affected by the slight wear. The pressure-receiving surface contacts the mating sliding ring and shares the load, reducing the load on the sliding sealing surface.
第１図に本考案の一実施例を示す。 FIG. 1 shows an embodiment of the present invention.
図において、３はハウジング１の内周面にパツ
キング２を介して気密的に装着された非回転の摺
動リング、６はシヤフト４の外周面にパツキング
５を介して気密的に装着されて該シヤフト４とと
もに回転し、前記摺動リング３よりも軟質の材料
からなる摺動リングである。 In the figure, 3 is a non-rotating sliding ring that is airtightly attached to the inner circumferential surface of the housing 1 via packing 2, and 6 is a non-rotating sliding ring that is airtightly attached to the outer circumferential surface of the shaft 4 via packing 5. This is a sliding ring that rotates together with the shaft 4 and is made of a softer material than the sliding ring 3.
軟質側摺動リング６における相手摺動リング３
との対接部７には、該対接部７と同心の円周溝８
が形成され、この円周溝８の内周側となる摺動シ
ール面７ａは、外周側にあつて円周溝８とシール
外周空間Ｓを連通する複数の切欠溝９が等配形成
された補助受圧面７ｂよりも数10μｍ、あるいは
数100μｍ程度、僅かに高くなつている。 Mating sliding ring 3 in soft side sliding ring 6
The contact portion 7 has a circumferential groove 8 concentric with the contact portion 7.
is formed, and the sliding seal surface 7a on the inner circumferential side of this circumferential groove 8 has a plurality of notched grooves 9 formed at equal intervals on the outer circumferential side communicating the circumferential groove 8 and the seal outer circumferential space S. It is slightly higher than the auxiliary pressure receiving surface 7b by several tens of μm or several hundred μm.
このため図示しないバネによつて摺動リング３
へ向けて押圧される軟質側摺動リング６は、仮に
相手側の前記摺動リング３との間に微小な加工精
度のバラツキや組み込み精度のバラツキがあつて
も、円周溝８内周の摺動シール面７ａが相手摺動
リング３と確実に接触し、しかも前記バネによる
荷重は摺動シール面７ａにのみ作用するため、良
好なシールが行なわれる。また該摺動シール面７
ａが僅かに摩耗しただけで補助受圧面７ｂが前記
荷重の一部を受けることとなり、摺動シール面７
ａの急速な損耗が防止される。 For this reason, the sliding ring 3 is moved by a spring (not shown).
Even if there is slight variation in machining accuracy or assembly accuracy between the soft side sliding ring 6 and the sliding ring 3 on the other side, the soft side sliding ring 6 is pressed toward the inner circumference of the circumferential groove 8. Since the sliding sealing surface 7a is in reliable contact with the mating sliding ring 3, and the load by the spring acts only on the sliding sealing surface 7a, good sealing is achieved. In addition, the sliding seal surface 7
Even if a is slightly worn, the auxiliary pressure receiving surface 7b will receive part of the load, and the sliding seal surface 7
Rapid wear and tear of a is prevented.
以上説明したように、本考案のメカニカルシー
ルは、軟質側摺動リングの摺動シール面をその外
周側の補助受圧面よりも僅かに高くしたことによ
つて、使用初期、前記摺動シール面が相手摺動リ
ングと確実に密接するようにしたため、補助受圧
面に設けた摩耗粉排出用の切欠溝から円周溝を経
てシール対象流体が多量に漏れるのを防止するこ
とができ、また、摺動シール面の僅かな摩耗によ
つて補助受圧面がバネ荷重を分担して受けるよう
になるため、前記摺動シール面の初期摩耗により
バネが大きく伸長してしまうことがなく、安定し
たシール性が得られる。
As explained above, the mechanical seal of the present invention has the sliding seal surface of the soft sliding ring slightly higher than the auxiliary pressure-receiving surface on the outer circumferential side of the mechanical seal. By ensuring that the seal is in close contact with the mating sliding ring, it is possible to prevent a large amount of the fluid to be sealed from leaking from the notch groove for discharging wear debris provided on the auxiliary pressure receiving surface through the circumferential groove. Due to slight wear on the sliding seal surface, the auxiliary pressure-receiving surface will share the spring load, so the spring will not be stretched too much due to initial wear on the sliding seal surface, resulting in a stable seal. You can get sex.
第１図は本考案の一実施例を示す組み込み状態
の要部半裁断面図、第２図は従来例を示す組み込
み状態の半裁断面図、第３図は同部分拡大図であ
る。
１……ハウジング、３，６……摺動リング、４
……シヤフト、７……対接部、７ａ……摺動シー
ル面、７ｂ……補助受圧面、８……円周溝、９…
…切欠溝、Ｓ……シール外周空間。
FIG. 1 is a half-cut sectional view of a main part in an assembled state showing an embodiment of the present invention, FIG. 2 is a half-cut sectional view of a conventional example in an assembled state, and FIG. 3 is an enlarged view of the same part. 1... Housing, 3, 6... Sliding ring, 4
... Shaft, 7 ... Contact portion, 7a ... Sliding seal surface, 7b ... Auxiliary pressure receiving surface, 8 ... Circumferential groove, 9 ...
...Notch groove, S...Seal outer peripheral space.
Claims (1)
対の摺動リングのうちの一方をハウジングの内周
に、他方をシヤフトの外周に気密的に装着し、バ
ネの軸方向荷重によつて該両摺動リングの対向端
面を対接させ、軟質側の摺動リングの対接部に円
周溝および該円周溝とシール外周空間とを連通す
る切欠溝を形成してなるメカニカルシールにおい
て、軟質側の摺動リングの対接部のうち、前記円
周溝の内周側に位置する摺動シール面の高さを、
その外周側にあつて前記切欠溝が形成された補助
受圧面よりも僅かに高くしたことを特徴とするメ
カニカルシール。 1 made of materials with different hardness and facing in the axial direction
One of the pair of sliding rings is attached to the inner periphery of the housing and the other to the outer periphery of the shaft, and the opposing end surfaces of the two sliding rings are brought into contact with each other by the axial load of the spring, and the soft In a mechanical seal in which a circumferential groove and a notch groove that communicates the circumferential groove and the seal outer circumferential space are formed in the opposing portion of the sliding ring on the soft side, of the opposing portion of the sliding ring on the soft side, The height of the sliding seal surface located on the inner circumferential side of the circumferential groove is
A mechanical seal characterized in that the outer peripheral side of the mechanical seal is slightly higher than the auxiliary pressure receiving surface on which the notched groove is formed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7033588U JPH0544618Y2 (en) | 1988-05-30 | 1988-05-30 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7033588U JPH0544618Y2 (en) | 1988-05-30 | 1988-05-30 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01173574U JPH01173574U (en) | 1989-12-08 |
| JPH0544618Y2 true JPH0544618Y2 (en) | 1993-11-12 |
Family
ID=31295584
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7033588U Expired - Lifetime JPH0544618Y2 (en) | 1988-05-30 | 1988-05-30 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0544618Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4606545B2 (en) * | 2000-05-02 | 2011-01-05 | イーグル工業株式会社 | Compressor shaft seal mechanism with mechanical seal |
-
1988
- 1988-05-30 JP JP7033588U patent/JPH0544618Y2/ja not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01173574U (en) | 1989-12-08 |
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