JPS59180002A - Centrifugal type fluid machine - Google Patents
Centrifugal type fluid machineInfo
- Publication number
- JPS59180002A JPS59180002A JP5238183A JP5238183A JPS59180002A JP S59180002 A JPS59180002 A JP S59180002A JP 5238183 A JP5238183 A JP 5238183A JP 5238183 A JP5238183 A JP 5238183A JP S59180002 A JPS59180002 A JP S59180002A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- shaft
- vibrations
- casing
- shape
- 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.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/04—Antivibration arrangements
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Sliding-Contact Bearings (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は高速で運転され軸振動に係シ、高い信頼性が要
求される遠心形流体機械に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Application of the Invention] The present invention relates to a centrifugal fluid machine that operates at high speed, is concerned with shaft vibration, and requires high reliability.
従来の遠心形流体機械を第1図(a)、 (b)に示す
遠心ポンプによシ説明する。遠心羽根車1は側板la、
羽根tb、主板ICよ如なシ、回転軸2に固定されてい
る。羽根車1の出口側には案内羽根3が設けられ、水返
し羽根4を介して次段の羽根車(図示せず)に向かう流
路5が形成されている。A conventional centrifugal fluid machine will be explained using a centrifugal pump shown in FIGS. 1(a) and 1(b). The centrifugal impeller 1 has a side plate la,
The blade tb, main plate IC, etc. are fixed to the rotating shaft 2. A guide vane 3 is provided on the outlet side of the impeller 1, and a flow path 5 is formed that goes to the next stage impeller (not shown) via a water return vane 4.
羽根車1の側板1g、主板ICの壁面に近接して固定ケ
ーシング6.7が設けられている。側板1aの外周面と
固定ケーシング6の内周面、主板ICの外周面と固定ケ
ーシング7の内周面との間には細隙8,9が形成されて
いる。また、側板11aと固定ケーシング6、主板IC
と固定ケーシング7との間には隙間10,11、細隙部
12゜13が形成されている。A fixed casing 6.7 is provided close to the side plate 1g of the impeller 1 and the wall surface of the main plate IC. Gaps 8 and 9 are formed between the outer peripheral surface of the side plate 1a and the inner peripheral surface of the fixed casing 6, and between the outer peripheral surface of the main plate IC and the inner peripheral surface of the fixed casing 7. In addition, the side plate 11a, the fixed casing 6, the main plate IC
Gaps 10 and 11 and narrow gaps 12 and 13 are formed between the fixed casing 7 and the fixed casing 7.
上記の構成であるから、羽根車1から吐出された流水の
一部は細隙8、隙間101細隙部12を通って羽根車1
の吸込側に漏洩する。一方、次段羽根車の吸込側から流
水の一部が細隙部13を通って隙間11に流入し、細隙
9から羽根車1の出口側に漏洩する。With the above configuration, a part of the flowing water discharged from the impeller 1 passes through the slit 8, the gap 101 and the slit 12, and passes through the impeller 1.
leaks to the suction side. On the other hand, part of the flowing water from the suction side of the next-stage impeller flows into the gap 11 through the slit 13 and leaks from the slit 9 to the outlet side of the impeller 1.
ところで、前記細隙8.9は第1図(b)に示すように
環状の隙間となっており、羽根車が高廟速で回転すると
、この細隙には油潤滑の動圧軸受と同様な軸受作用が生
じる。この場合、ケーシング内周面の形状が真円である
と動圧軸受作用が小さいため羽根車の径方向の偏心に対
する負荷能力が小さく、また軸自励振動に対する防振効
果が小さい欠点があった。By the way, the slit 8.9 is an annular gap as shown in Fig. 1(b), and when the impeller rotates at a high speed, this slit 8.9 has a ring-shaped gap similar to an oil-lubricated hydrodynamic bearing. A bearing effect occurs. In this case, if the shape of the inner circumferential surface of the casing is a perfect circle, the dynamic pressure bearing effect is small, so the load capacity against eccentricity in the radial direction of the impeller is small, and the vibration isolation effect against shaft self-excited vibration is also small. .
本発明の目的は、前記従来技術の欠点をなくし、軸振動
が小さく軸自励振動の生じない遠心形流体機械を提供す
ることにある。−
〔発明の概要〕
本発明は上記目的を達成するために、ケーシング内周面
の形状を非真円にすることにより、動圧軸受作用を太き
くし軸自励撮動を抑制するようにしたものである。SUMMARY OF THE INVENTION An object of the present invention is to eliminate the drawbacks of the prior art and provide a centrifugal fluid machine with small shaft vibrations and no shaft self-excited vibrations. - [Summary of the Invention] In order to achieve the above object, the present invention makes the shape of the inner circumferential surface of the casing non-perfect circular, thereby thickening the dynamic pressure bearing action and suppressing the self-excited motion of the comb shaft. It is something.
以下、本発明の実施例を第2図〜第4図について説明す
る。第1図と同一部分には同一符号を付して説明を省略
する。第2図は本発明の第1実施例を示し、ケーシング
6.7の内周面の形状を周方向にステップ状にしである
。このため、羽根車の回転により細隙8,9に生ずる動
圧軸受作用が大幅に増大し、羽根車の径方向の偏心に対
する負荷能力が増大し軸振動が小さくなる。また、軸自
励振動に対する防振効果が増大するので、軸自励振動を
生ずることなく安定なポンプ運転を継続できる。Embodiments of the present invention will be described below with reference to FIGS. 2 to 4. Components that are the same as those in FIG. 1 are given the same reference numerals, and their explanation will be omitted. FIG. 2 shows a first embodiment of the present invention, in which the shape of the inner peripheral surface of the casing 6.7 is stepped in the circumferential direction. Therefore, the dynamic pressure bearing effect generated in the narrow gaps 8 and 9 due to the rotation of the impeller is greatly increased, the load capacity against eccentricity in the radial direction of the impeller is increased, and shaft vibration is reduced. Furthermore, since the vibration damping effect against shaft self-excited vibration is increased, stable pump operation can be continued without producing shaft self-excited vibration.
第3図は本発明の第2実施例を示し、ケーシング6.7
の内周面の形状を周方向に多円弧状(図では三円弧)に
しである。また、第4図は本発明の第3実施例を示し、
ケーシング6.7の内周面の形状を周方向にくい違い多
円弧状(図ではくい違い三円弧)にしである。このよう
に構成することによって第1実施例により説明したもの
と同じ効果を得ることができる。FIG. 3 shows a second embodiment of the invention, in which the casing 6.7
The shape of the inner peripheral surface is multi-arc shaped (three arcs in the figure) in the circumferential direction. Further, FIG. 4 shows a third embodiment of the present invention,
The shape of the inner circumferential surface of the casing 6.7 is made into a multi-circular arc shape with slight differences in the circumferential direction (in the figure, three circular arcs with different angles). With this configuration, it is possible to obtain the same effects as those described in the first embodiment.
以上説明した本発明によれば、羽根車の側板またけ主板
の外周面に細隙を介して対向するケーシング内周面の形
状を非真円にしたので、細隙に生ずる動圧軸受作用を大
幅に増大させることができ、したがって軸振動を小さく
シ、軸自励振動を生じない効果がある。According to the present invention as described above, the shape of the inner circumferential surface of the casing that faces the outer circumferential surface of the main plate spanning the side plates of the impeller through the gap is made non-circular, so that the dynamic pressure bearing action that occurs in the gap is suppressed. This has the effect of reducing shaft vibration and preventing shaft self-excited vibration.
第1図(a)は従来の遠心形流体機械の縦断面図、第1
図(b)は第1図(a)のAあるいはB矢視断面図、第
2図(a)は本発明の遠心形流体機械の第1実施例を示
す縦断面図、第2図(b)は第2図(a)のAあるいは
B矢視断面図、第3図、第4図はそれぞれ本発明の第2
実施例、第3実施例の断面図である。
1a・・・側板、IC・・・主板、6.7・・・ケーシ
ング、8.9・・・細隙。
茅2囚(oL)
トさ
(ト2Figure 1(a) is a vertical cross-sectional view of a conventional centrifugal fluid machine.
FIG. 2(b) is a sectional view taken along arrows A or B in FIG. 1(a), FIG. ) is a sectional view taken along arrow A or B in FIG. 2(a), and FIGS.
FIG. 3 is a cross-sectional view of an embodiment and a third embodiment. 1a... Side plate, IC... Main plate, 6.7... Casing, 8.9... Slit. Kaya 2 Prisoner (oL) Tosa (To 2
Claims (1)
向するケーシング内周面の形状を非真円としたことを特
徴とする遠心形流体機械。 2 前記ケーシング内周面の形状をステップ状とするこ
とによシ非真円としたことを特徴とする特許請求の範囲
第1項記載の遠心形流体機械。 & 前記ケーシング内周面の形状を多円弧状とすること
により非真円としたことを特徴とする特許請求の範囲第
1項記載の遠心形流体機械。 4、前記ケーシング内周面の形状をくい違い多円弧状と
することによシ非真円としたことを特徴とする特許請求
の範囲第1項記載の遠心形流体機械。[Scope of Claims] 1. A centrifugal fluid machine characterized in that the inner peripheral surface of the casing, which faces the outer peripheral surface of the side plate or main plate of the impeller with a gap in between, has a non-perfect circular shape. 2. The centrifugal fluid machine according to claim 1, wherein the inner circumferential surface of the casing has a step-like shape so that it is not a perfect circle. & The centrifugal fluid machine according to claim 1, wherein the shape of the inner peripheral surface of the casing is made into a multi-arc shape so that the shape is not a perfect circle. 4. The centrifugal fluid machine according to claim 1, wherein the shape of the inner circumferential surface of the casing is made into a polygonal arc shape so that it is not a perfect circle.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP5238183A JPS59180002A (en) | 1983-03-30 | 1983-03-30 | Centrifugal type fluid machine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP5238183A JPS59180002A (en) | 1983-03-30 | 1983-03-30 | Centrifugal type fluid machine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS59180002A true JPS59180002A (en) | 1984-10-12 |
Family
ID=12913218
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP5238183A Pending JPS59180002A (en) | 1983-03-30 | 1983-03-30 | Centrifugal type fluid machine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS59180002A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105378297A (en) * | 2013-07-10 | 2016-03-02 | 大金工业株式会社 | Turbo compressor and turbo refrigerating machine |
US10995759B2 (en) | 2019-03-19 | 2021-05-04 | Coavis | Water pump |
-
1983
- 1983-03-30 JP JP5238183A patent/JPS59180002A/en active Pending
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105378297A (en) * | 2013-07-10 | 2016-03-02 | 大金工业株式会社 | Turbo compressor and turbo refrigerating machine |
EP3020981A1 (en) * | 2013-07-10 | 2016-05-18 | Daikin Industries, Ltd. | Turbo compressor and turbo refrigerating machine |
EP3020981A4 (en) * | 2013-07-10 | 2017-03-29 | Daikin Industries, Ltd. | Turbo compressor and turbo refrigerating machine |
US10227995B2 (en) | 2013-07-10 | 2019-03-12 | Daikin Industries, Ltd. | Turbo compressor and turbo refrigerating machine |
US10995759B2 (en) | 2019-03-19 | 2021-05-04 | Coavis | Water pump |
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