JPS60108596A - Impeller for centrifugal compressor - Google Patents
Impeller for centrifugal compressorInfo
- Publication number
- JPS60108596A JPS60108596A JP21505683A JP21505683A JPS60108596A JP S60108596 A JPS60108596 A JP S60108596A JP 21505683 A JP21505683 A JP 21505683A JP 21505683 A JP21505683 A JP 21505683A JP S60108596 A JPS60108596 A JP S60108596A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- diffuser
- speed
- shroud
- centrifugal compressor
- 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
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、遠心圧縮機におけるディフューザの効率を改
善する羽根車の構造に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an impeller structure that improves the efficiency of a diffuser in a centrifugal compressor.
従来、遠心圧縮機においては、第１図に示したように、
端部に羽根車１を取り付けだ駆動軸２が軸受及びシール
装置乙によって圧縮機本体４内に支承され、ディフュー
ザ５及び渦巻室６が形成されかつ吸込管７が連結される
吸込カバー８と圧縮機本体４間に前記の羽根車１が収め
られている。Conventionally, in a centrifugal compressor, as shown in Figure 1,
An impeller 1 is attached to the end of the drive shaft 2. The drive shaft 2 is supported within the compressor main body 4 by a bearing and a sealing device B, and is connected to a suction cover 8, in which a diffuser 5 and a volute chamber 6 are formed, and a suction pipe 7 is connected thereto. The impeller 1 is housed between the machine bodies 4.
そして、その作用は、吸込管７を経て流体は羽根車１に
よって昇圧されるとともに速度エネルギを与えられ、デ
ィフューザ５に入ってここで速度エネルギは圧力のエネ
ルギに変換されながらディフユーザ５出口に至り、渦巻
室６で回収されて図示しない吐出管に導かれる。The action is that the fluid passes through the suction pipe 7, is pressurized by the impeller 1, and is given velocity energy, enters the diffuser 5, where the velocity energy is converted into pressure energy, and reaches the outlet of the diffuser 5. , and is collected in the swirl chamber 6 and guided to a discharge pipe (not shown).
この場合の羽根車１内で作動流体が通過する軌跡（子午
面流線と称する）は、羽根車１の形状からしてシーラウ
ド側（外壁側）Ｓの方が短く、ハブ側（内壁側）Ｈの方
が長い。しかも、羽根車１０入口から出口に至る過程で
、流体が羽根車翼によって受ける流れの転向角は、シュ
ラウド側Ｓの方が大きい。ところで、従来の羽根車１の
出口径及び周方向に対する出口翼角度は、シーラウド側
Ｓ及びハブ側Ｈにおいて同じであり、そのために羽根車
１出口で流体が翼から受ける角運動量はシュラウド側Ｓ
の方が小さく、ハブ側Ｈの方が大きいという状態になシ
、すべり速度Ｃｓｒ、 （第７図参照）がハブ側Ｈより
もシュラウド側Ｓの方が大きく、その結果子午面速度も
ハブ側Ｈで大きく、シュラウド側Ｓで小さくなる。In this case, the trajectory (referred to as a meridional streamline) that the working fluid passes within the impeller 1 is shorter on the sealoud side (outer wall side) S, considering the shape of the impeller 1, and on the hub side (inner wall side). H is longer. Moreover, the turning angle of the flow that the fluid receives by the impeller blades during the process from the inlet to the outlet of the impeller 10 is larger on the shroud side S. By the way, the exit diameter and the exit blade angle with respect to the circumferential direction of the conventional impeller 1 are the same on the searoud side S and the hub side H, so the angular momentum that the fluid receives from the blades at the exit of the impeller 1 is the same on the shroud side S.
is smaller and larger on the hub side H, the slip velocity Csr, (see Figure 7) is larger on the shroud side S than on the hub side H, and as a result, the meridional velocity is also smaller on the hub side. It is large at H and becomes small at S on the shroud side.
すなわち、羽根車１の周方向に対する翼角度βの子午面
に沿った分布は第２図の如くなり、羽根車１の出口では
翼角度βはシュラウド側Ｓもハブ側Ｈも等しくなってお
り、その羽根車１の軸直角断面は第３図に示したような
形状となっている。That is, the distribution of the blade angle β with respect to the circumferential direction of the impeller 1 along the meridian plane is as shown in FIG. 2, and at the outlet of the impeller 1, the blade angle β is equal on both the shroud side S and the hub side H. The axis-perpendicular cross section of the impeller 1 has a shape as shown in FIG.
この場合、第２図示のように、シーラウド側Ｓの子午面
流路長さ訓はハブ側Ｈのそれに比べて短いことに加えて
、流れの転向角（翼角度βの変化と考えることができる
）は大きい。In this case, as shown in the second diagram, in addition to the meridional flow path length on the sealoud side S being shorter than that on the hub side H, the turning angle of the flow (which can be considered as a change in the blade angle β) is shorter than that on the hub side H. ) is large.
したがって、羽根車１が流体に与える仕事（角運動量）
は、ハブ側Ｈで大きくシュラウド側Ｓで小さいことにな
シ、その結果、ディフーーザ５人口での子午面速度Ｃｍ
２は第４図に、ディフューザ５人口での旋回速度Ｃｕｚ
は第５図にそれぞれ示したような分布で、ディフューザ
５人口の速度をゆがめることになり、ディフーーザ５の
効率を低下させ、遠心圧縮機としての性能を悪くしてい
る。Therefore, the work (angular momentum) that impeller 1 gives to the fluid
is large on the hub side H and small on the shroud side S. As a result, the meridional velocity Cm at the diffuser 5 population is
2 is shown in Figure 4, the rotation speed Cuz at the diffuser 5 population.
The distributions shown in FIG. 5 distort the velocity of the diffuser 5, reducing the efficiency of the diffuser 5 and deteriorating its performance as a centrifugal compressor.
このようなディフューザ５人口（羽根車１出口）での速
度のゆがみは、比速度の大きい（羽根車出口幅の大きい
）羽根車又は翼数の少ない羽根車には特に顕著に見られ
るところである。Such speed distortion at the diffuser 5 (impeller 1 exit) is particularly noticeable in impellers with a large specific speed (large impeller exit width) or impellers with a small number of blades.
また、半開放形羽根車の場合にも、シーラウド側が静止
壁面と接するために速度が大きいことや、遠心羽根車の
特徴としてシーラウド側の曲率が大きいこと等により、
境界層の発達が・・ブ側に比べて激しくなることが原因
して、前述したようなディフューザ入口の速度のゆがみ
がよく観察されるところである。In addition, even in the case of a semi-open impeller, the speed is high because the sea loud side is in contact with the stationary wall surface, and the curvature of the sea loud side is large, which is a feature of centrifugal impellers.
The above-mentioned distortion of the velocity at the diffuser inlet is often observed due to the fact that the boundary layer develops more rapidly than on the side.
本発明は、このような従来のディフーーザ入口における
速度のゆがみを改善し、ディフューザ入口で均一化して
ディフーーザの効率を向上せしめ、もって遠心圧縮機の
性能を高めようとすることを目的とするものである。The present invention aims to improve the speed distortion at the inlet of a conventional diffuser and make it uniform at the inlet of the diffuser, thereby improving the efficiency of the diffuser and thereby improving the performance of the centrifugal compressor. be.
本発明は、羽根車の出口径及び、又は周方向に対する出
口翼角度をハブ側よりシュラウド側の方に犬ならしめた
ことを特徴とするものである。The present invention is characterized in that the outlet diameter of the impeller and/or the outlet blade angle with respect to the circumferential direction are made closer to the shroud side than to the hub side.
さらに本発明の実施例を図面を参照しながら説明すれば
、第６図示例において、各部の構成は従来例を示した第
１図示例と同様でちるが、羽根車１の出口径をハブ側Ｈ
よシもシュラウド側Ｓの方に大きくしである。したがっ
て、第７図に示した羽根車１出口の速度三角形からも明
らかなように、径が大きくなる分だけ羽根車１出口の周
速度Ｕ２、子午面速度Ｃｍ２及び旋回速度Ｃｕ２は増大
し、第４図及び第５図に示したようなディフーーザ５人
口におけるシーラウド側Ｓの速度が補償され、ディフュ
ーザ５人口における速度のゆがみが改善されてディフー
ーザ５０幅間で均一化され、デイフ二−ザ５の効率が向
上される。Further, to explain the embodiment of the present invention with reference to the drawings, in the sixth illustrated example, the configuration of each part is the same as the first illustrated example showing the conventional example, but the outlet diameter of the impeller 1 is set to the hub side. H
The width is also larger towards the shroud side S. Therefore, as is clear from the velocity triangle at the outlet of the impeller 1 shown in FIG. The speed of the sea loud side S in the diffuser 5 population as shown in FIG. 4 and FIG. Efficiency is improved.
また、羽根車１の出口径をノ・プ側Ｈとシーラウド側Ｓ
とで同一にし、第８図及び第９図示のように、羽根車１
出口での翼角度βをシュラウド側Ｓに大きく、ノ・ブ側
Ｈに小さくすれば、前記第７図に示した速度三角形にお
ける羽根車１出口の相対流れ角度β２も大きくなり、シ
ュラウド側Ｓの羽根車１出口の子午面速度Ｃｍ２及び旋
回速度Ｃｕ２が増大し、ディフーーザ５人口における速
度のゆがみが改善される。なお、第７図中βｚｔｈは羽
根車出口翼角度を、Ｃ３ｌ、はすべり速度を示す。Also, the outlet diameter of the impeller 1 is set to the no-pu side H and the sea-loud side S.
and as shown in FIGS. 8 and 9, the impeller 1
If the blade angle β at the outlet is made larger on the shroud side S and smaller on the knob side H, the relative flow angle β2 at the impeller 1 outlet in the speed triangle shown in FIG. The meridional velocity Cm2 and the turning velocity Cu2 at the outlet of the impeller 1 are increased, and the distortion of the velocity in the diffuser 5 population is improved. In addition, in FIG. 7, βzth indicates the impeller exit blade angle, and C3l indicates the sliding speed.
さらにまた、羽根車１の出口径及び周方向に対する出口
翼角度βの両者を、同時にノ・プ側Ｈよりもシュラウド
側Ｓの方に大ならしめることも同様にディフーーザ５人
口における速度のゆがみを改善するのに有効である。Furthermore, simultaneously increasing both the outlet diameter of the impeller 1 and the outlet blade angle β with respect to the circumferential direction toward the shroud side S than the nop side H also reduces the distortion of the speed in the diffuser 5 population. It is effective for improving.
以上述べたように本発明によれば、羽根車が流体に与え
る角運動量を・・プ側に比べてシーラウド側の方に太き
−くなるような構造にしたために、ディフューザ入口幅
間の速度が均一化され、ディフーーザの効率を向上させ
、遠心圧縮機の性能を高めることができるという工栗上
きわめて有益なる効果を得ることができるものである。As described above, according to the present invention, the impeller has a structure in which the angular momentum given to the fluid is greater on the sea loud side than on the... side, so that the velocity across the diffuser inlet width is It is possible to obtain extremely beneficial effects in that the efficiency of the diffuser can be made uniform, the efficiency of the diffuser can be improved, and the performance of the centrifugal compressor can be improved.
第１図は、従来の遠心圧縮機の一部の断面図、第２図は
従来の羽根車の翼角度と子午面流路長さの関係を示す線
図、第３図は従来の羽根車の軸直角断面図、第４図は従
来のディフーーザ入口での子午面速度線図、第５図は従
来のディフューザ入口での旋回速度線図、第６図は本発
明の実施例を示す遠心圧縮機の一部の断面図、第７図は
羽根車出口の速度三角形、第８図は本発明の羽根車の梠
角度と子午面流路長さの関係を示す線図、第９図は本発
明の羽根車の軸直角断面図である。
１・・・羽根車、２・・・駆動軸、３・・・軸受及びシ
ール装置１．４・・・圧縮機本体、５−・・・ディフュ
ーザ、６・・・渦巻室、７・・・吸込管、８・・・吸込
カバー、Ｓ・・・シーラウド側、Ｈ・・・ハブ側、β・
・・羽根車の翼角度、Ｓｍ・・・羽根車の子午面流路長
さ、Ｃｍ２・・・ディフューザ入口での子午面速度、Ｃ
ｕ２・・・ディ７゜−ザ入口での旋回速度、Ｃ８Ｌ・・
・すべり速度、Ｕ２・・・羽根車出口の周速度、β２・
・・羽根車出口の相対流れ角度、βｚｔｈ・・・羽根車
出口翼角度。
特許出願人 株式会社荏原製作所
代理人弁理士 高 木 正 行
代理人弁理士 千 １） 稔
代理人弁理士 丸 山 隆 夫Figure 1 is a cross-sectional view of a part of a conventional centrifugal compressor, Figure 2 is a diagram showing the relationship between the blade angle and meridional flow path length of a conventional impeller, and Figure 3 is a diagram of a conventional impeller. Fig. 4 is a meridional velocity diagram at the inlet of a conventional diffuser, Fig. 5 is a rotation velocity diagram at the inlet of a conventional diffuser, and Fig. 6 is a centrifugal compression diagram showing an embodiment of the present invention. A cross-sectional view of a part of the machine, Fig. 7 is a velocity triangle at the impeller outlet, Fig. 8 is a diagram showing the relationship between the impeller angle and meridional flow path length of the impeller of the present invention, and Fig. 9 is a diagram of the present invention. FIG. 3 is an axis-perpendicular cross-sectional view of the impeller of the invention. DESCRIPTION OF SYMBOLS 1... Impeller, 2... Drive shaft, 3... Bearing and seal device 1.4... Compressor body, 5-... Diffuser, 6... Volute chamber, 7... Suction pipe, 8... Suction cover, S... Sealoud side, H... Hub side, β.
...Blade angle of the impeller, Sm...Meridional flow path length of the impeller, Cm2...Meridional speed at the diffuser inlet, C
u2...D7゜Turning speed at the entrance, C8L...
・Slip speed, U2... Circumferential speed at impeller exit, β2・
... Relative flow angle at the impeller outlet, βzth... Impeller outlet blade angle. Patent applicant Masayuki Takagi, patent attorney representing Ebara Corporation Patent attorney Minoru Takao Maruyama, patent attorney
Claims (1)
ハブ側よりシュラウド側の方に大ならしめたことを特徴
とする遠心圧縮機の羽根車。An impeller for a centrifugal compressor, characterized in that the outlet diameter of the impeller and/or the outlet blade angle relative to the circumferential direction are made larger on the shroud side than on the hub side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21505683A JPS60108596A (en) | 1983-11-17 | 1983-11-17 | Impeller for centrifugal compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21505683A JPS60108596A (en) | 1983-11-17 | 1983-11-17 | Impeller for centrifugal compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60108596A true JPS60108596A (en) | 1985-06-14 |
Family
ID=16666027
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21505683A Pending JPS60108596A (en) | 1983-11-17 | 1983-11-17 | Impeller for centrifugal compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60108596A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2189663A3 (en) * | 2008-11-21 | 2012-07-04 | Hitachi Plant Technologies, Ltd. | Centrifugal compressor |
| JP2015194091A (en) * | 2014-03-31 | 2015-11-05 | 株式会社Ihi | Compressor impeller, centrifugal compressor and supercharger |
| CN113833675A (en) * | 2021-09-16 | 2021-12-24 | 势加透博洁净动力如皋有限公司 | Impeller and air compressor with same |
-
1983
- 1983-11-17 JP JP21505683A patent/JPS60108596A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2189663A3 (en) * | 2008-11-21 | 2012-07-04 | Hitachi Plant Technologies, Ltd. | Centrifugal compressor |
| US8475131B2 (en) | 2008-11-21 | 2013-07-02 | Hitachi Plant Technologies, Ltd. | Centrifugal compressor |
| JP2015194091A (en) * | 2014-03-31 | 2015-11-05 | 株式会社Ihi | Compressor impeller, centrifugal compressor and supercharger |
| CN113833675A (en) * | 2021-09-16 | 2021-12-24 | 势加透博洁净动力如皋有限公司 | Impeller and air compressor with same |
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