JPS6250711B2 - - Google Patents
Info
- Publication number
- JPS6250711B2 JPS6250711B2 JP5854581A JP5854581A JPS6250711B2 JP S6250711 B2 JPS6250711 B2 JP S6250711B2 JP 5854581 A JP5854581 A JP 5854581A JP 5854581 A JP5854581 A JP 5854581A JP S6250711 B2 JPS6250711 B2 JP S6250711B2
- Authority
- JP
- Japan
- Prior art keywords
- shaft sealing
- oil
- shaft
- bearing
- sealing chamber
- 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
- 238000007789 sealing Methods 0.000 claims description 53
- 239000003921 oil Substances 0.000 claims description 52
- 239000010687 lubricating oil Substances 0.000 claims description 27
- 230000035515 penetration Effects 0.000 claims 1
- 230000000694 effects Effects 0.000 description 5
- 230000000149 penetrating effect Effects 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000013016 damping Methods 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/44—Free-space packings
- F16J15/443—Free-space packings provided with discharge channels
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
Description
【発明の詳細な説明】
本発明はターボ圧縮機などの回転機械におい
て、機内のガスがケーシングの軸貫通部分から外
部へ洩れるのを防止するようにしたオイルフイル
ムシール形式の軸封装置に関し、さらに詳しく
は、大気側のシールリングに軸受としての機能も
もたせるようにした軸封装置に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an oil film seal type shaft sealing device for a rotating machine such as a turbo compressor, which prevents internal gas from leaking to the outside from a shaft penetrating portion of a casing. Specifically, the present invention relates to a shaft sealing device in which the seal ring on the atmosphere side also functions as a bearing.
従来の一般的なオイルフイルムシール形式の軸
封装置は第１図に示すような構造を有していた。
すなわち、回転する軸１に対し微少な間隙をもつ
ガス側フローテイングリング２および大気側フロ
ーテイングリング３をケーシング４の軸貫通部に
形成した軸封室５に設け、軸封室５には軸封油供
給口６から機内（ガス側Ａ）のガス圧力より若干
高い圧力の軸封油を供給し、軸１とガス側フロー
テイング２との間隙に油膜を形成することによ
り、機内ガスが外部へ洩れるのを防止するように
していた。大気側フローテイングリング３は軸封
室５内に供給された軸封油の油圧を保持するため
に設けられ、軸１との間には適当は間隙が形成さ
れている。フローテイングリング２，３を通過し
た軸封油はそれぞれ排出口７，８から機外へ排出
される。軸封室５の大気側Ｂにはケーシング４に
固設された軸受９が設けられており、この軸受９
は潤滑油供給口１０から供給された潤滑油により
潤滑される。 A conventional general oil film seal type shaft sealing device had a structure as shown in FIG.
That is, a gas-side floating ring 2 and an atmosphere-side floating ring 3 having a small gap with respect to the rotating shaft 1 are provided in a shaft sealing chamber 5 formed in the shaft penetrating portion of the casing 4. By supplying shaft sealing oil at a pressure slightly higher than the gas pressure inside the machine (gas side A) from the sealing oil supply port 6 and forming an oil film in the gap between the shaft 1 and the gas side floating 2, the gas inside the machine is released from the outside. I tried to prevent it from leaking. The atmosphere-side floating ring 3 is provided to maintain the oil pressure of the shaft sealing oil supplied into the shaft sealing chamber 5, and a gap is appropriately formed between it and the shaft 1. The shaft sealing oil that has passed through the floating rings 2 and 3 is discharged to the outside of the machine from discharge ports 7 and 8, respectively. A bearing 9 fixed to the casing 4 is provided on the atmospheric side B of the shaft sealing chamber 5.
is lubricated by lubricating oil supplied from the lubricating oil supply port 10.
このように構成された軸封装置では、軸封装置
と軸受とが別々に設けられているため、軸受間の
長さが長くなり、ローター系としての剛性が低下
する。また、構造も複雑になるから価格も高く、
メンテナンスも困難であるという欠点があつた。 In the shaft sealing device configured in this way, since the shaft sealing device and the bearing are provided separately, the length between the bearings becomes long and the rigidity of the rotor system is reduced. In addition, the structure is complicated and the price is high.
Another disadvantage was that maintenance was difficult.
上述した軸封装置の欠点を改良した従来の軸封
装置を第２図に示す。これは軸封室５の大気側Ｂ
に固定リング１１を固設し、この固定リング１１
に、第１図に示す大気側シールリング３と軸受９
の両方の機能をさせることにより、軸受間の長さ
を短かくすると共に構造の簡素化を計つたもので
ある。第２図において第１図と同一符号を付した
部分は同一部分である。このように構成された軸
封装置においては、機内ガス圧よりも若干高い油
圧の軸封油が軸受の潤滑油を兼用するため、潤滑
油圧が高くなり、このため軸受面圧が上昇して油
膜ダンパ効果を減少させるという欠点がある。ま
た、固定リング１１には軸封装置の圧力保持機能
と軸受としての機能をもたせているため、その軸
方向長さが長くなり、したがつて軸封油の潤滑油
としての潤滑長さが長くなるから潤滑油の温度上
昇が大きく、焼付きなどを引起し易いという欠点
もあつた。 FIG. 2 shows a conventional shaft sealing device that improves the drawbacks of the shaft sealing device described above. This is the atmospheric side B of the shaft sealing chamber 5.
A fixing ring 11 is fixedly attached to the fixing ring 11.
In addition, the atmosphere side seal ring 3 and bearing 9 shown in FIG.
By performing both functions, the length between the bearings can be shortened and the structure can be simplified. In FIG. 2, parts given the same reference numerals as in FIG. 1 are the same parts. In a shaft sealing device configured in this way, the shaft sealing oil, which has a hydraulic pressure slightly higher than the in-machine gas pressure, also serves as lubricating oil for the bearings, so the lubricating oil pressure becomes high, which increases the bearing surface pressure and causes an oil film. It has the disadvantage of reducing the damping effect. Furthermore, since the fixed ring 11 has a pressure holding function for the shaft seal device and a function as a bearing, its length in the axial direction becomes long, and therefore the lubrication length of the shaft seal oil as a lubricating oil becomes long. As a result, the temperature of the lubricating oil increases significantly, which also has the disadvantage of easily causing seizure.
本発明は上述した従来装置の欠点を改良し、軸
受間の長さを短かくできると共に、軸受のダンパ
効果を減少させることもなく、また潤滑油の油度
上昇も小さくできる軸封装置を提供することを目
的とするもので、ケーシングの軸貫通部に形成し
た軸封室と、この軸封室に軸封油を供給するため
の軸封油供給口と、軸封室のガス側に設けたガス
側フローテイングリングと、大気側に固設された
固定リングとを備え、固定リングにはその軸封室
側に圧力保持部を設けると共にその大気側には軸
受部を形成し、その圧力保持部と軸受部との間に
は環状の油溜りを設けてこの油溜りを排油口に連
通させ、かつ前記軸受部にも油溜りを設けてこの
油溜りは潤滑油の供給口に連通させるようにした
ものである。 The present invention improves the drawbacks of the conventional devices described above, and provides a shaft sealing device that can shorten the length between the bearings, does not reduce the damper effect of the bearings, and can reduce the increase in lubricating oil level. The purpose is to a floating ring on the gas side, and a fixed ring fixed on the atmosphere side. An annular oil reservoir is provided between the holding portion and the bearing portion, and this oil reservoir is communicated with an oil drain port, and an oil reservoir is also provided in the bearing portion, and this oil reservoir is communicated with a lubricating oil supply port. It was designed so that
以下、本発明の軸封装置の一実施例を第３図に
より説明する。図において、第１図および第２図
と同一符号を付した部分は同一若しくは相当する
部分を示す。 Hereinafter, one embodiment of the shaft sealing device of the present invention will be described with reference to FIG. In the figures, parts given the same reference numerals as in FIGS. 1 and 2 indicate the same or corresponding parts.
図において、５はケーシング４の軸貫通部に形
成された軸封室、６は軸封室５に軸封油を供給す
るための軸封油供給口、２は軸封室５のガス側Ａ
に設けたガス側フローテイングリング、１１は軸
封室５の大気側Ｂにおけるケーシング４の内周面
に固設された固定リングである。固定リング１１
の軸封室５側には軸封室５の圧力を保持するため
に軸１との間に微少な隙間を形成するように圧力
保持部１１ａが設けられている。また、固定リン
グ１１の大気側Ｂには軸１を支持するための軸受
部１１ｂが形成されている。さらに、固定リング
１１に形成された圧力保持部１１ａと軸受部１１
ｂとの間には環状の油溜り１１ｃが設けられ、こ
の油溜り１１ｃは排油口１２に連通され、かつ前
記軸受部１１ｂにも環状の油溜り１１ｄを設け、
この油溜り１１ｄは潤滑油の供給口１３および１
４に連通させるようにしている。供給口１３は固
定リング１１の軸受部外周側に均等に数ケ所形成
されている。 In the figure, 5 is a shaft sealing chamber formed in the shaft penetrating part of the casing 4, 6 is a shaft sealing oil supply port for supplying shaft sealing oil to the shaft sealing chamber 5, and 2 is a gas side A of the shaft sealing chamber 5.
A gas side floating ring 11 is a fixed ring fixed to the inner peripheral surface of the casing 4 on the atmosphere side B of the shaft sealing chamber 5. Fixed ring 11
A pressure holding part 11a is provided on the shaft sealing chamber 5 side so as to form a small gap with the shaft 1 in order to maintain the pressure in the shaft sealing chamber 5. Further, a bearing portion 11b for supporting the shaft 1 is formed on the atmospheric side B of the fixing ring 11. Furthermore, a pressure holding portion 11a and a bearing portion 11 formed on the fixing ring 11
An annular oil reservoir 11c is provided between the bearing portion 11b and the bearing portion 11b, and this oil reservoir 11c is communicated with the oil drain port 12, and an annular oil reservoir 11d is also provided in the bearing portion 11b.
This oil reservoir 11d is connected to lubricating oil supply ports 13 and 1.
I am trying to connect it to 4. The supply ports 13 are formed at several locations evenly on the outer peripheral side of the bearing portion of the fixed ring 11.
次に上述した一実施例の作用を説明する。機内
ガス圧より若干高い圧力の軸封油は軸封油供給口
６から軸封室５に供給され、ガス側フローテイン
グリング２と軸１との間に軸封油膜を形成して機
内のガスが外部に洩れないようにシールする。軸
封室５内の軸封油の圧力保持は固定リング１１に
設けられた圧力保持部１１ａによりなされ、この
圧力保持部１１ａと軸１との隙間を通過した軸封
油は油溜り１１ｃから排油口１２を通つて外部へ
排出される。一方、軸受潤滑油は軸受特性に応じ
て最適な圧力状態で潤滑油の供給口１４から固定
リング１１に形成した軸受部１１ｃの外周部に達
し、ここから固定リング１１に形成した供給口１
３を通つて軸受部外周数ケ所から均等に軸受面に
供給されるようになつている。軸受面に供給され
た潤滑油は油膜を形成しながら軸受部１１ｂの左
右方向に流れ、一方に流れた潤滑油は油溜り１１
ｃに達して排油口１２から外部に排出され、また
もう一方に流れた潤滑油は固定リング１１の端部
に達してここから直接外部に排出される。このよ
うに構成したことにより、軸受間の長さを第１図
に示す従来の軸封装置よりも大幅に短かくするこ
とができ、したがつてローター系としての剛性が
高くなるから軸系の安全性を高めることができ、
構造も簡素化されるから安価にできると共にメン
テナンスも容易に行なうことができる。また、固
定リング１１においては圧力保持部１１ａと軸受
部１１ｂとを油溜り１１ｃにより分離しているの
で、軸受部１１ｂには適切な圧力の潤滑油が供給
され、したがつて軸受面圧を最適にコントロール
できることより油膜ダンパ効果を最適に保持で
き、さらに運転状態に応じて軸封油および潤滑油
の圧力調整をそれぞれ単独に行なうことができ
る。また、潤滑油は軸受部１１ｂの外周側の数ケ
所から供給されるようになつているから、軸受部
１１ｂの全体に均一に潤滑油を供給して油膜形成
をすることができ、また油溜り１１ｄは軸受部１
１ｂのほぼ中央に形成されているので、潤滑油の
軸受面を流れる距離が短かくなり、よつて潤滑油
の異常温度上昇を確実に防止でき、軸受部１１ｂ
の焼付などを防ぐことができる。 Next, the operation of the above-mentioned embodiment will be explained. Shaft sealing oil at a pressure slightly higher than the in-machine gas pressure is supplied from the shaft sealing oil supply port 6 to the shaft sealing chamber 5, forming a shaft sealing oil film between the gas side floating ring 2 and the shaft 1, and suppressing the in-machine gas. Seal to prevent leakage to the outside. The pressure of the shaft sealing oil in the shaft sealing chamber 5 is maintained by a pressure holding part 11a provided on the fixed ring 11, and the shaft sealing oil that has passed through the gap between this pressure holding part 11a and the shaft 1 is drained from the oil reservoir 11c. The oil is discharged to the outside through the oil port 12. On the other hand, the bearing lubricating oil reaches the outer periphery of the bearing portion 11c formed in the fixed ring 11 from the lubricating oil supply port 14 under the optimum pressure condition according to the bearing characteristics, and from there, the lubricating oil reaches the outer circumference of the bearing portion 11c formed in the fixed ring 11.
3, and is evenly supplied to the bearing surface from several locations on the outer periphery of the bearing portion. The lubricating oil supplied to the bearing surface flows in the left-right direction of the bearing part 11b while forming an oil film, and the lubricating oil flowing in one direction flows into the oil sump 11.
The lubricating oil reaches the end of the fixing ring 11 and is discharged to the outside from the oil drain port 12. With this configuration, the length between the bearings can be made much shorter than that of the conventional shaft sealing device shown in Figure 1, which increases the rigidity of the rotor system. can increase safety,
Since the structure is simplified, it can be made at low cost and maintenance can be performed easily. In addition, in the fixed ring 11, the pressure holding part 11a and the bearing part 11b are separated by the oil reservoir 11c, so lubricating oil at an appropriate pressure is supplied to the bearing part 11b, thereby optimizing the bearing surface pressure. Since the oil film damper effect can be maintained optimally, the pressure of the shaft sealing oil and lubricating oil can be adjusted independently depending on the operating conditions. Furthermore, since the lubricating oil is supplied from several locations on the outer circumferential side of the bearing part 11b, it is possible to uniformly supply the lubricating oil to the entire bearing part 11b to form an oil film, and also to eliminate oil stagnation. 11d is bearing part 1
Since the lubricating oil is formed almost in the center of the bearing part 1b, the distance through which the lubricating oil flows on the bearing surface is shortened, thereby reliably preventing an abnormal temperature rise of the lubricating oil.
This can prevent burn-in, etc.
第４図および第５図に本発明装置の他の実施例
を示すもので、図において、第３図と同一符号を
付した部分は同一部分である。この実施例は軸系
のホワーリング現象をより抑制するために、図に
示すように、固定リング１１の軸受部１１ｂの軸
受面に均等に数ケ所チヤンフアー１５を設けるよ
うにしたもので、他の構成は前記一実施例と同一
である。 FIGS. 4 and 5 show other embodiments of the apparatus of the present invention, and in the figures, parts given the same reference numerals as in FIG. 3 are the same parts. In this embodiment, in order to further suppress the whirling phenomenon of the shaft system, chamfers 15 are provided at several locations evenly on the bearing surface of the bearing portion 11b of the fixed ring 11, as shown in the figure. is the same as in the previous embodiment.
本発明の軸封装置は以上詳述したように、圧力
保持部と軸受部を有する固定リングを軸封室の大
気側に固設し、この固定リングの圧力保持部と軸
受部との間に油溜りを設けてこれを排油口に連通
させ、かつ軸受部にも油溜りを設けてこれは潤滑
油の供給口に連通させるように構成したので、軸
受間の長さを短かくできると共に、軸受のダンパ
効果を減少させることもないから軸系の安定性を
向上できる。また、軸受部に供給された潤滑油の
潤滑長さも短かくなるから潤滑油の温度上昇も確
実に防止できるという効果がある。 As described in detail above, the shaft sealing device of the present invention has a fixing ring having a pressure holding part and a bearing part fixedly installed on the atmospheric side of the shaft sealing chamber, and a space between the pressure holding part and the bearing part of the fixing ring. An oil sump is provided and communicated with the oil drain port, and an oil sump is also provided on the bearing and this communicates with the lubricating oil supply port, so the length between the bearings can be shortened. Since the damper effect of the bearing is not reduced, the stability of the shaft system can be improved. Furthermore, since the lubrication length of the lubricating oil supplied to the bearing portion is also shortened, there is an effect that an increase in the temperature of the lubricating oil can be reliably prevented.
第１図は従来の一般的な軸封装置を示す縦断面
図、第２図は従来装置の値の例を示す縦断面図、
第３図は本発明の軸封装置の一実施例を示す縦断
面図、第４図および第５図は本発明装置の他の実
施例を示すもので、第４図は要部の縦断面図、第
５図は第４図の−線矢視図である。
１……軸、２……ガス側フローテイングリン
グ、４……ケーシング、５……軸封室、６……軸
封油供給口、１１……固定リング、１１ａ……圧
力保持部、１１ｂ……軸受部、１１ｃ，１１ｄ…
…油溜り、１２……排油口、１３，１４……（潤
滑油の）供給口、Ａ……ガス側、Ｂ……大気側。
Fig. 1 is a longitudinal sectional view showing a conventional general shaft sealing device, Fig. 2 is a longitudinal sectional view showing an example of values of the conventional device,
FIG. 3 is a longitudinal cross-sectional view showing one embodiment of the shaft sealing device of the present invention, and FIGS. 4 and 5 are longitudinal cross-sectional views of other embodiments of the shaft sealing device of the present invention. FIG. 5 is a view taken along the - line in FIG. 4. DESCRIPTION OF SYMBOLS 1...Shaft, 2...Gas side floating ring, 4...Casing, 5...Shaft sealing chamber, 6...Shaft sealing oil supply port, 11...Fixing ring, 11a...Pressure holding part, 11b... ...Bearing part, 11c, 11d...
...Oil sump, 12...Oil drain port, 13, 14...(Lubricating oil) supply port, A...Gas side, B...Atmospheric side.
Claims (1)
この軸封室に軸封油を供給するための軸封油供給
口と、前記軸封室のガス側に設けたガス側フロー
テイングリングと、軸封室の大気側に固設された
固定リングとを備え、固定リングにはその軸封室
側に軸封室の圧力を保持するための圧力保持部を
設けると共にその大気側には軸を支持するための
軸受部を形成し、その圧力保持部と軸受部との間
には環状の油溜りを設けてこの油溜りを排油口に
連通させ、かつ前記軸受部にも油溜りを設けてこ
の油溜りは潤滑油の供給口に連通させるようにし
たことを特徴とする軸封装置。1. A shaft sealing chamber formed in the shaft penetration part of the casing;
A shaft sealing oil supply port for supplying shaft sealing oil to the shaft sealing chamber, a gas side floating ring provided on the gas side of the shaft sealing chamber, and a fixed ring fixedly installed on the atmospheric side of the shaft sealing chamber. The fixing ring is provided with a pressure holding part on the shaft sealing chamber side for holding the pressure of the shaft sealing chamber, and a bearing part for supporting the shaft is formed on the atmospheric side, and the pressure holding part is provided on the shaft sealing chamber side. An annular oil reservoir is provided between the bearing section and the bearing section, and this oil reservoir is communicated with an oil drain port, and an oil reservoir is also provided in the bearing section, and this oil reservoir is communicated with a lubricating oil supply port. A shaft sealing device characterized by:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5854581A JPS57173670A (en) | 1981-04-20 | 1981-04-20 | Shaft sealing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5854581A JPS57173670A (en) | 1981-04-20 | 1981-04-20 | Shaft sealing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57173670A JPS57173670A (en) | 1982-10-26 |
| JPS6250711B2 true JPS6250711B2 (en) | 1987-10-26 |
Family
ID=13087414
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5854581A Granted JPS57173670A (en) | 1981-04-20 | 1981-04-20 | Shaft sealing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57173670A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0611364B2 (en) * | 1988-01-28 | 1994-02-16 | 日本下水道事業団 | Reaction tank submersion type sludge concentrator |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100917031B1 (en) | 2007-11-13 | 2009-09-10 | 권복화 | Contactless seal |
-
1981
- 1981-04-20 JP JP5854581A patent/JPS57173670A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0611364B2 (en) * | 1988-01-28 | 1994-02-16 | 日本下水道事業団 | Reaction tank submersion type sludge concentrator |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57173670A (en) | 1982-10-26 |
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