JPH04171370A - Noncontact type shaft seal device - Google Patents
Noncontact type shaft seal deviceInfo
- Publication number
- JPH04171370A JPH04171370A JP29666090A JP29666090A JPH04171370A JP H04171370 A JPH04171370 A JP H04171370A JP 29666090 A JP29666090 A JP 29666090A JP 29666090 A JP29666090 A JP 29666090A JP H04171370 A JPH04171370 A JP H04171370A
- Authority
- JP
- Japan
- Prior art keywords
- groove
- seal
- air feeding
- feeding groove
- air supply
- 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.)
- Granted
Links
- 238000007789 sealing Methods 0.000 claims abstract description 43
- 230000003068 static effect Effects 0.000 abstract description 6
- 238000013016 damping Methods 0.000 abstract description 4
- 230000005284 excitation Effects 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 4
- 210000000988 bone and bone Anatomy 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
Landscapes
- Mechanical Sealing (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、ポンプ装置等の回転軸とケーシングとの間の
軸封等に適用される非接触式軸封装置に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a non-contact type shaft sealing device that is applied to a shaft seal between a rotating shaft and a casing of a pump device or the like.
この種の軸封装置として、従来から第5図に示すものが
知られている。同図において、■はケーシングであり、
このケーシングlを貫通して設けられた回転軸2には、
回転密封環3が嵌装されている。4はOリングである。As a shaft sealing device of this type, one shown in FIG. 5 has been known. In the same figure, ■ is the casing;
The rotating shaft 2 provided through the casing l has
A rotary sealing ring 3 is fitted. 4 is an O-ring.
5は上記ケーシング1と回転軸2との間に配設された静
止密封環であり、上記回転密封環3の一側面3aとの対
向面5aがシール面として構成されている。この静止密
封環5の他側面5bに形成された凹部6と上記ケーシン
グ1にボルト7等で固定されたばね受部材8との間には
、静止密封環5に対して上記回転密封環3側への弾性力
を(ばね力)を付与するばね部材9が介在されている。Reference numeral 5 denotes a stationary sealing ring disposed between the casing 1 and the rotating shaft 2, and a surface 5a facing the one side 3a of the rotating sealing ring 3 is configured as a sealing surface. Between the recess 6 formed on the other side surface 5b of the stationary seal ring 5 and the spring bearing member 8 fixed to the casing 1 with bolts 7, etc. A spring member 9 is interposed to provide an elastic force (spring force).
1O111は上記ケーシングlの内周面と上記静止密封
環5の外周面との間に介在された0リングである。1O111 is an O-ring interposed between the inner circumferential surface of the casing l and the outer circumferential surface of the stationary sealing ring 5.
上記静止密封環5のシール面5aには、横断面形状が矩
形(凹形)の複数、たとえば4個の円弧状給気溝50が
第6図のように周方向へ等間隔に配置して形成されてい
る。13は上記ケーシングlに形成されて外部からのシ
ールガスGを取り込む入力ポート、14は」1記静止密
封環5に形成されて上記入力ポート13に取り込まれた
シールガスGをオリフィス15を介して上記給気溝12
に導く導入路である。On the sealing surface 5a of the stationary sealing ring 5, a plurality of, for example, four arcuate air supply grooves 50 having a rectangular (concave) cross-sectional shape are arranged at equal intervals in the circumferential direction as shown in FIG. It is formed. Reference numeral 13 indicates an input port formed in the casing 1 to take in the seal gas G from the outside; The above air supply groove 12
It is an introduction route that leads to.
このような構成において、回転軸2の回転に伴なって静
止密封環5のシール面5aが回転密封環3の側面3aに
弾性的に摺接させる。一方、入力ポート13に取り込ま
れたシールガスGはオリフィス15で絞り込まれた後、
導入路14を経て各給気溝50に供給され、回転密封環
3と静止密封環5との間の隙間を給気溝50から内周側
および外周側へ向って流出する。この結果、上記両者3
.5間の隙間が自動調整されシールガスがシール潤滑膜
となって軸封が達成される。In such a configuration, as the rotating shaft 2 rotates, the sealing surface 5a of the stationary sealing ring 5 is brought into elastic sliding contact with the side surface 3a of the rotating sealing ring 3. On the other hand, after the seal gas G taken into the input port 13 is narrowed down by the orifice 15,
The air is supplied to each air supply groove 50 through the introduction path 14, and flows out from the air supply groove 50 toward the inner circumferential side and the outer circumferential side through the gap between the rotating seal ring 3 and the stationary seal ring 5. As a result, both of the above 3
.. The gap between the shafts 5 and 5 is automatically adjusted, and the seal gas becomes a seal lubricating film to achieve shaft sealing.
ところで、上記した従来の非接触式軸封装置の場合は、
ニューマチックハンマーと称される自励振動が起こり易
い。このような自励振動の発生要因のひとつに給気溝5
0内のシールガスの質量がある。By the way, in the case of the conventional non-contact type shaft seal device mentioned above,
Self-excited vibration called pneumatic hammer is likely to occur. One of the causes of such self-excited vibration is the air supply groove 5.
There is a mass of seal gas within 0.
すなわち、給気溝5の容積が大きいはど自励振動が生じ
易い。そこで、たとえば上記給気溝50の溝幅を小さく
することも考えられるが、この場合は、回転密封環に対
する圧力分布に偏りが生じて回転軸2の円滑な回転の支
障となる。That is, when the volume of the air supply groove 5 is large, self-excited vibration is likely to occur. Therefore, it is conceivable to reduce the width of the air supply groove 50, for example, but in this case, the pressure distribution against the rotary sealing ring will be biased, which will impede smooth rotation of the rotary shaft 2.
また、上記のように給気溝50の横断面が矩形の場合、
組立時等に給気溝50の開口端縁を欠損させるおそれも
ある。Further, when the cross section of the air supply groove 50 is rectangular as described above,
There is also a risk that the opening edge of the air supply groove 50 may be damaged during assembly or the like.
本発明は上記の実情に鑑みてなされたもので、シール性
能の向上と給気溝の損傷防止とを図ることができる非接
触式軸封装置を提供することを目的とする。The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a non-contact type shaft sealing device that can improve sealing performance and prevent damage to the air supply groove.
上記目的を達成するため、本発明に係る非接触式軸封装
置は、
静止密封環のシール面に形成される給気溝の横断面形状
を、溝底側へ向って先細り状に形成したものである。In order to achieve the above object, the non-contact type shaft sealing device according to the present invention has the following features: The cross-sectional shape of the air supply groove formed on the sealing surface of the stationary sealing ring is tapered toward the groove bottom side. It is.
本発明の非接触式軸封装置によれば、給気溝の溝幅を小
さ(しなくともその容積を小さくできるので、自励振動
が抑制されてシール減衰特性が改善され、また給気溝が
溝底側へ向って先細り状であるため、取扱い時にその開
口縁が欠損されることを防止できる。According to the non-contact type shaft sealing device of the present invention, the groove width of the air supply groove can be reduced (or even the volume can be reduced, so self-excited vibrations are suppressed and the seal damping characteristics are improved, and the air supply groove Since the groove is tapered toward the bottom side, it is possible to prevent the opening edge from being damaged during handling.
以下、本発明の実施例を図面に基づいて説明する。 Embodiments of the present invention will be described below based on the drawings.
第1図および第2図は本発明の一実施例を静圧形非接触
式シール装置に適用した例を示すもので、従来のものと
同一部所には、同一符号を付して説明を省略する。Figures 1 and 2 show an example in which an embodiment of the present invention is applied to a static pressure type non-contact sealing device, and the same parts as in the conventional one are given the same reference numerals and explained. Omitted.
同図において、12は静止密封環5のシール面に形成さ
れた溝深さがhの給気溝であり、その横断面形状は、溝
底に向って先細り状、たとえば三角形状に形成されてい
る。In the figure, reference numeral 12 denotes an air supply groove with a groove depth h formed in the sealing surface of the stationary sealing ring 5, and its cross-sectional shape is tapered toward the bottom of the groove, for example, triangular. There is.
このような構成においては、外部からのシールガスGが
オリフィス15で絞り込まれた後、給気溝12に供給さ
れることにより、従来と同様に回転静止環3と静止密封
環5との間の隙間がシールされる。In such a configuration, the seal gas G from the outside is narrowed down by the orifice 15 and then supplied to the air supply groove 12, thereby increasing the gap between the rotating stationary ring 3 and the stationary sealing ring 5 as in the conventional case. Gaps are sealed.
この場合は、上記給気溝12の横断面形状が三角形とな
っているので、溝幅を小さくしなくても給気溝12の容
積を小さくすることができる。したがって、給気溝12
内のシールガスGの全質量が小さくなって自励振動の発
生が抑制され、シールの減衰性能を高めることができる
うえ、回転密封環3に対する偏った圧力付勢もなく、回
転軸2の安定回転が保証される。In this case, since the cross-sectional shape of the air supply groove 12 is triangular, the volume of the air supply groove 12 can be reduced without reducing the groove width. Therefore, the air supply groove 12
The total mass of the seal gas G inside is reduced, suppressing the occurrence of self-excited vibrations, improving the damping performance of the seal, and eliminating uneven pressure on the rotating seal ring 3, making the rotating shaft 2 more stable. Rotation is guaranteed.
また、上記給気溝12の開口縁のシール面5aに対する
角度も90°以上となるので組付けなどの取扱い時に不
用意に上記開口縁を欠落など損傷させるおそれもな(な
る。Furthermore, since the angle of the opening edge of the air supply groove 12 with respect to the sealing surface 5a is 90 degrees or more, there is no risk of the opening edge being accidentally damaged such as being broken during assembly or other handling.
なお、給気溝12は、溝深さhが0.3〜1,5砿、溝
壁間の角度θが60°〜120°の各範囲から選定すれ
ば、上記の効果が有効に発揮される。In addition, if the air supply groove 12 is selected from a range in which the groove depth h is from 0.3 to 1.5 mm and the angle θ between the groove walls is from 60° to 120°, the above effects will be effectively exhibited. Ru.
ところで、上記の例では、給気溝12の横断面形状が三
角形のもので説明したが、第3図および第4図に示すよ
うに横断面形状が台形の給気孔22であっても、上記実
施例と同様の効果を奏する。By the way, in the above example, the cross-sectional shape of the air supply groove 12 was explained as being triangular, but even if the cross-sectional shape of the air supply hole 22 is trapezoidal as shown in FIGS. 3 and 4, the above-mentioned The same effects as in the embodiment are achieved.
また、上記各実施例では、静圧形のもので説明したが、
回転密封環3の側面3aにスパイラルグループを設けた
動圧形のものやヘリツクボーン型などのハイブリッド形
のものにも適用可能である。In each of the above embodiments, the static pressure type was explained, but
It is also applicable to a dynamic pressure type in which a spiral group is provided on the side surface 3a of the rotary sealing ring 3 and a hybrid type such as a helical bone type.
以上ように、本発明によれば、静止密封環のシール面に
形成された給気溝の横断面形状を溝底に向って先細り状
に形成したから、溝幅を小さくすることなく、その容積
を小さくでき、したがって、シール減衰性能の向上が図
れ、しかも給気溝の開口縁が破損されることを防止する
ことができる。As described above, according to the present invention, since the cross-sectional shape of the air supply groove formed on the sealing surface of the stationary sealing ring is tapered toward the groove bottom, the volume can be increased without reducing the groove width. Therefore, the seal damping performance can be improved, and the opening edge of the air supply groove can be prevented from being damaged.
第1図は本発明の実施例である静圧形非接触式軸封装置
を示す要部の断面図、第2図は同装置における静止密封
環の半分を示す正面図、第3図および第4図はそれぞれ
本発明の他の実施例を示す要部の断面図および静止密封
環の半分の正面図、第5図は従来の非接触式軸封装置を
示す断面図、第6図は従来の静止密封環の半分を示す正
面図である。
1・・・ケーシング、2・・・回転軸、3・・・回転密
封環、3a・・・側面、5・・・静止密封環、5a・・
・シール面、12.22・・・給気溝、G・・・シール
ガス。
特許 出願人 日本ビラー工業株式会社代理人 弁理
士 鈴 江 孝 −
(ばか]名)
第 1!21
G、 シづレカ′ス
第 2 図
[3図FIG. 1 is a sectional view of the main parts of a static pressure type non-contact type shaft sealing device which is an embodiment of the present invention, FIG. 2 is a front view showing half of a stationary sealing ring in the same device, FIG. Fig. 4 is a sectional view of a main part and a half front view of a stationary sealing ring showing another embodiment of the present invention, Fig. 5 is a sectional view showing a conventional non-contact type shaft sealing device, and Fig. 6 is a sectional view of a conventional non-contact type shaft sealing device. FIG. DESCRIPTION OF SYMBOLS 1... Casing, 2... Rotating shaft, 3... Rotating sealing ring, 3a... Side surface, 5... Stationary sealing ring, 5a...
・Seal surface, 12.22... Air supply groove, G... Seal gas. Patent Applicant Nippon Biller Industry Co., Ltd. Agent Patent Attorney Takashi Suzue - (stupid name) No. 1!21 G, Shizureka's No. 2 [Fig. 3]
Claims (1)
の間に配設された静止密封環を、上記回転軸に嵌装され
た回転密封環の側面に弾性的に当接させ、上記回転密封
環の側面に対向する静止密封環側のシール面に周方向で
等間隔に配置して形成された複数の給気溝に外部からシ
ールガスを供給するようになした非接触式軸封装置にお
いて、上記給気溝の横断面形状を、溝底側へ向かって先
細り状に形成したことを特徴とする非接触式軸封装置。(1) A stationary sealing ring disposed between the rotating shaft passing through the casing and the casing is brought into elastic contact with a side surface of the rotating sealing ring fitted to the rotating shaft, and the rotating sealing ring In a non-contact type shaft sealing device, seal gas is supplied from the outside to a plurality of air supply grooves arranged at equal intervals in the circumferential direction on the sealing surface of the stationary sealing ring side facing the side surface of the shaft. A non-contact type shaft sealing device, characterized in that the cross-sectional shape of the air supply groove is tapered toward the bottom of the groove.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2296660A JP2568459B2 (en) | 1990-10-31 | 1990-10-31 | Non-contact type shaft sealing device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2296660A JP2568459B2 (en) | 1990-10-31 | 1990-10-31 | Non-contact type shaft sealing device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH04171370A true JPH04171370A (en) | 1992-06-18 |
JP2568459B2 JP2568459B2 (en) | 1997-01-08 |
Family
ID=17836428
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2296660A Expired - Fee Related JP2568459B2 (en) | 1990-10-31 | 1990-10-31 | Non-contact type shaft sealing device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2568459B2 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000240807A (en) * | 1999-02-22 | 2000-09-08 | Nippon Pillar Packing Co Ltd | Mechanical seal |
WO2000075540A1 (en) | 1999-06-07 | 2000-12-14 | Nippon Pillar Packing Co., Ltd. | Non-contact type shaft sealing device |
JP2002508490A (en) * | 1997-12-17 | 2002-03-19 | エイ・ダブリュー・チェスタトン・カンパニー | Non-contact mechanical face seal with concentric sealing surface |
US7044470B2 (en) | 2000-07-12 | 2006-05-16 | Perkinelmer, Inc. | Rotary face seal assembly |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4826094A (en) * | 1971-08-06 | 1973-04-05 | ||
JPS4998666U (en) * | 1972-12-16 | 1974-08-26 | ||
JPS53120039A (en) * | 1977-03-29 | 1978-10-20 | Gutehoffnungshuette Sterkrade | Device for sealing shaft with gas |
-
1990
- 1990-10-31 JP JP2296660A patent/JP2568459B2/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4826094A (en) * | 1971-08-06 | 1973-04-05 | ||
JPS4998666U (en) * | 1972-12-16 | 1974-08-26 | ||
JPS53120039A (en) * | 1977-03-29 | 1978-10-20 | Gutehoffnungshuette Sterkrade | Device for sealing shaft with gas |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002508490A (en) * | 1997-12-17 | 2002-03-19 | エイ・ダブリュー・チェスタトン・カンパニー | Non-contact mechanical face seal with concentric sealing surface |
JP4740453B2 (en) * | 1997-12-17 | 2011-08-03 | エイ・ダブリュー・チェスタトン・カンパニー | Non-contact mechanical face seal with concentric sealing surface |
JP2000240807A (en) * | 1999-02-22 | 2000-09-08 | Nippon Pillar Packing Co Ltd | Mechanical seal |
WO2000075540A1 (en) | 1999-06-07 | 2000-12-14 | Nippon Pillar Packing Co., Ltd. | Non-contact type shaft sealing device |
US7044470B2 (en) | 2000-07-12 | 2006-05-16 | Perkinelmer, Inc. | Rotary face seal assembly |
JP2007263374A (en) * | 2000-07-12 | 2007-10-11 | Perkinelmer Fluid Sciences | Rotary face seal assembly |
Also Published As
Publication number | Publication date |
---|---|
JP2568459B2 (en) | 1997-01-08 |
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