JPH09317692A - Centrifugal impeller of rotational fluid machinery - Google Patents

Centrifugal impeller of rotational fluid machinery

Info

Publication number
JPH09317692A
JPH09317692A JP12829496A JP12829496A JPH09317692A JP H09317692 A JPH09317692 A JP H09317692A JP 12829496 A JP12829496 A JP 12829496A JP 12829496 A JP12829496 A JP 12829496A JP H09317692 A JPH09317692 A JP H09317692A
Authority
JP
Japan
Prior art keywords
blade
casing
impeller
turbine
centrifugal impeller
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.)
Withdrawn
Application number
JP12829496A
Other languages
Japanese (ja)
Inventor
Minoru Masutani
穣 枡谷
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to JP12829496A priority Critical patent/JPH09317692A/en
Publication of JPH09317692A publication Critical patent/JPH09317692A/en
Withdrawn legal-status Critical Current

Links

Abstract

PROBLEM TO BE SOLVED: To collect motive power from a leaking flow flowing in a clearance between a shroud disc and a casing of a centrifugal impeller and to reduce leakage itself. SOLUTION: A turbine blade 4 having a blade angle in the opposite direction of a main blade 3 is installed on a back surface facing a casing 2 of a shroud disc 1, and motive power is collected by generating torque on the turbine blade 4 by a leaking flow flowing between the shroud disc 1 and the casing 2. Additionally, leakage is reduced by lowering pressure of the leaking flow at the time when it passes the turbine blade 4.

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【発明の属する技術分野】本発明は、遠心圧縮機、遠心
ブロア、遠心ポンプ等の回転流体機械の遠心羽根に関す
る。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a centrifugal blade of a rotary fluid machine such as a centrifugal compressor, a centrifugal blower and a centrifugal pump.

【0002】[0002]

【従来の技術】従来の遠心圧縮機、遠心ブロア、遠心ポ
ンプ等におけるクローズ型遠心羽根車では、シュラウド
ディスク背面は何もつけない平滑面であった。即ち、図
4に示すように、ケーシング2内に配置されたシュラウ
ドディスク1に主軸10によって回転し流体を昇圧又は
移動させるメインブレード3が取付けられていて、メイ
ンブレード3は羽根車内の主流路中に配置されている。
前記シュラウドディスク1のケーシング2に面しメイン
ブレード3が取付けられていない側の背面は何も取付け
られていない平滑面であった。なお、図4中5は、ケー
シング2とシュラウドディスク1上流端との間に設けら
れたラビリンスである。
2. Description of the Related Art In conventional centrifugal compressors, centrifugal blowers, centrifugal pumps, and other closed type centrifugal impellers, the back surface of the shroud disk is a smooth surface with nothing attached. That is, as shown in FIG. 4, a main blade 3 that is rotated by a main shaft 10 to pressurize or move a fluid is attached to a shroud disk 1 arranged in a casing 2, and the main blade 3 is in a main flow path in an impeller. It is located in.
The rear surface of the shroud disk 1 facing the casing 2 and not having the main blade 3 attached thereto was a smooth surface having nothing attached. Reference numeral 5 in FIG. 4 denotes a labyrinth provided between the casing 2 and the upstream end of the shroud disc 1.

【0003】[0003]

【発明が解決しようとする課題】前記の従来の遠心羽根
車において、シュラウドディスクとケーシングの間のす
き間をもれるもれ流れは、小流量用羽根車では主流流量
の約10〜20%であり、このもれ流れは、羽根車出口
からシュラウドディスクとケーシングの間のすき間を流
れて羽根車入口に合流して羽根車出口と入口間に還流を
つくり、羽根車に対主流流量比と同じ比率の約10〜2
0%の所要動力を増加させていた。
In the conventional centrifugal impeller described above, the leakage flow leaking through the gap between the shroud disk and the casing is about 10 to 20% of the main flow rate in the small flow impeller. , This leakage flow flows from the impeller outlet through the gap between the shroud disc and the casing, joins the impeller inlet, and creates reflux between the impeller outlet and inlet, and the same ratio as the main flow rate ratio to the impeller. About 10-2
The required power of 0% was increased.

【0004】このもれ流れを制限しているのは、シュラ
ウドディスク上流端のラビリンスであるが、もれ流れを
減らすためにラビリンスのすき間を小さくすると、ラビ
リンスで起こる励振力を増すことになり、また、接触に
よる振動増幅を招く危険性も増すことにもなり、望まし
くはない。
It is the labyrinth at the upstream end of the shroud disk that limits the leakage flow. However, if the clearance of the labyrinth is reduced to reduce the leakage flow, the excitation force generated in the labyrinth increases. Moreover, the risk of vibration amplification due to contact increases, which is not desirable.

【0005】本発明は、以上の問題点を解決することが
できる回転流体機械の遠心羽根車を提供しようとするも
のである。
The present invention is intended to provide a centrifugal impeller of a rotary fluid machine capable of solving the above problems.

【0006】[0006]

【課題を解決するための手段】本発明の回転流体機械の
遠心羽根車は、シュラウドディスクのケーシングに面す
る背面に流体を昇圧させるブレードとは反対方向の翼角
をもつタービングブレードを設けたことを特徴とする。
In a centrifugal impeller of a rotary fluid machine according to the present invention, a turbine blade having a blade angle opposite to a blade for pressurizing a fluid is provided on a rear surface of a shroud disk facing a casing. It is characterized by

【0007】本発明では、シュラウドディスクのケーシ
ングに面する背面に流体を昇圧又は移動させるブレード
と反対方向の翼角をもつタービングブレードが取付けら
れているので、シュラウドディスクとケーシングの間の
すきまに生じるもれ流れ中に、前記タービンブレードが
置かれることとなり、シュラウドディスクに回転方向の
トルクが発生する。これによって、羽根車全体に反回転
方向にかかっているトルクを軽減し、遠心羽根車の所要
動力を減少させることができる。
According to the present invention, since the turbine blade having the blade angle opposite to the blade that pressurizes or moves the fluid is attached to the back surface of the shroud disk facing the casing, the clearance between the shroud disk and the casing is set. In the resulting leak flow, the turbine blades will be placed and a torque will be generated in the shroud disc in the direction of rotation. As a result, the torque applied to the entire impeller in the counter-rotational direction can be reduced, and the required power of the centrifugal impeller can be reduced.

【0008】また、もれ流れがタービンブレードを通過
することによって、圧力が降下し、もれ量自身も減少す
る。
Further, as the leak flow passes through the turbine blade, the pressure drops and the leak amount itself also decreases.

【0009】[0009]

【発明の実施の形態】本発明の実施の一形態を、図1な
いし図3によって説明する。本実施の形態では、図4に
示される遠心羽根車において、シュラウドディスク1の
ケーシング2に面しメインブレード3が取付けられた側
とは反対側の背面に、メインブレード3とは反対方向の
翼角をもつ複数のタービンブレード4を等間隔をおいて
取付けている。
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIGS. In the present embodiment, in the centrifugal impeller shown in FIG. 4, on the rear surface of the shroud disk 1 facing the casing 2 and on the side opposite to the side on which the main blade 3 is attached, blades in the direction opposite to the main blade 3 are provided. A plurality of angled turbine blades 4 are attached at equal intervals.

【0010】前記タービンブレード4は、図2に示すよ
うに、タービン入口にあたる羽根車出口旋回量Cu2
出口周速U2 、もれ量流速Cm2 から入口翼角を求め、
タービン出口で旋回量が0となるように出口翼角を求
め、曲線状のブレード形状とするのが効率がよいが、製
作容易化のため直線としてもよい。また、図2中のW2
はタービン入口相対流速、C2 はタービン入口絶対流
速、W1 はタービン出口相対流速U1 はタービン出口周
速、Cm1 はタービン出口のもれ量流速を示し、タービ
ンブレード4を曲線ブレード形状にする時には、タービ
ン入口翼角はW1 の方向近くに向け、タービン出口翼角
は流出方向がW2 の方向へなるように決める。ただし、
タービンブレード4を直線状ブレード形状にする時に
は、タービン入口翼角をW1 の方向近くへ向けるだけと
する。
As shown in FIG. 2, the turbine blade 4 has an impeller outlet turning amount Cu 2 , which corresponds to a turbine inlet,
The inlet blade angle is calculated from the outlet peripheral velocity U 2 and the leakage flow velocity Cm 2 .
It is efficient to calculate the outlet blade angle so that the turning amount is 0 at the turbine outlet and form a curved blade shape, but a straight line may be used for ease of manufacturing. Also, W 2 in FIG.
Is the turbine inlet relative flow velocity, C 2 is the turbine inlet absolute flow velocity, W 1 is the turbine outlet relative flow velocity U 1 is the turbine outlet peripheral velocity, Cm 1 is the leakage flow velocity at the turbine outlet, and the turbine blade 4 has a curved blade shape. In this case, the turbine inlet blade angle is set close to the direction of W 1 , and the turbine outlet blade angle is set so that the outlet direction is in the W 2 direction. However,
When making the turbine blade 4 into a straight blade shape, the turbine inlet blade angle is merely directed toward the direction of W 1 .

【0011】以上のように構成された本実施の形態で
は、羽根車が回転を初めると、シュラウドディスク1の
背面とケーシング2との間のすき間に羽根車出口から羽
根車入口へ還るもれ流れが生じる。このもれ流れは、シ
ュラウドディスク1に取付けられているタービンブレー
ド4の間を通過し、羽根車に回転方向のトルクを生じさ
せ、所要軸動力を軽減させることができる。
In the present embodiment configured as described above, when the impeller starts rotating, the leakage flow returning from the impeller outlet to the impeller inlet in the gap between the back surface of the shroud disk 1 and the casing 2. Occurs. This leakage flow passes between the turbine blades 4 attached to the shroud disk 1, and causes a torque in the rotating direction in the impeller to reduce the required shaft power.

【0012】遠心羽根車の小流量用の羽根車ではもれ流
れが主流の10〜20%であり、これがそのまま所要軸
動力の増加になっていたが、本実施の形態では、図3に
示すように、同じもれ量に対しても、動力を回収し、軸
動力を減少させてインペラの効率を向上させる。(効率
は流量×ヘッド/軸動力であるので、軸動力が減ること
により効率の分母が小さくなり、効率が上昇する。)な
お、図3中点線は従来の遠心羽根車、実線は本実施の形
態を示す。
In the impeller for a small flow rate of the centrifugal impeller, the leakage flow is 10 to 20% of the main flow, which directly increases the required shaft power, but in the present embodiment, it is shown in FIG. Thus, even for the same amount of leakage, the power is recovered and the shaft power is reduced to improve the efficiency of the impeller. (The efficiency is the flow rate x head / shaft power, so the denominator of the efficiency is reduced and the efficiency is increased by reducing the shaft power.) The dotted line in Fig. 3 is the conventional centrifugal impeller, and the solid line is the present embodiment. The morphology is shown.

【0013】また、前記もれ流れがタービンブレード4
の間の通過することによって圧力が降下し、ラビリンス
5前後の差圧が減り、もれ量自身も減少することにな
る。
Further, the leakage flow is caused by the turbine blade 4
As a result of the passage between the two, the pressure drops, the differential pressure before and after the labyrinth 5 decreases, and the leak amount itself also decreases.

【0014】[0014]

【発明の効果】本発明の回転流体機械の遠心羽根車は、
シュラウドディスクのケーシングに面する背面に流体を
昇圧又は移動させるブレードと反対方向の翼角をもつタ
ービンブレードを取付けているので、同タービンブレー
ドの発生するトルクによって遠心羽根車の所要動力を減
少させることができ、また、もれ流れがタービンブレー
ドを通過することによって圧力が降下し、もれ量を減少
させることができる。
The centrifugal impeller of the rotary fluid machine of the present invention is
Since a turbine blade having a blade angle in the opposite direction to the blade that pressurizes or moves the fluid is attached to the back surface facing the casing of the shroud disk, the torque required by the turbine blade reduces the power required for the centrifugal impeller. In addition, the leakage flow passes through the turbine blades, so that the pressure drops and the leakage amount can be reduced.

【図面の簡単な説明】[Brief description of drawings]

【図1】本発明の実施の一形態に係る遠心羽根車の子午
面断面図である。
FIG. 1 is a meridional sectional view of a centrifugal impeller according to an embodiment of the present invention.

【図2】図1のA−A断面(周方向断面)図である。FIG. 2 is a cross-sectional view (cross section in the circumferential direction) taken along the line AA of FIG.

【図3】同実施の形態の効果を表わす性能曲線図であ
る。
FIG. 3 is a performance curve diagram showing an effect of the same embodiment.

【図4】従来の遠心羽根車を示す子午面断面図である。FIG. 4 is a meridional sectional view showing a conventional centrifugal impeller.

【符号の説明】[Explanation of symbols]

1 シュラウドディスク 2 ケーシング 3 メインブレード 4 タービンブレード 5 ラビリンス 10 主軸 1 Shroud disk 2 Casing 3 Main blade 4 Turbine blade 5 Labyrinth 10 Spindle

Claims (1)

【特許請求の範囲】[Claims] 【請求項1】 シュラウドディスクのケーシングに面す
る背面に流体を昇圧又は移動させるブレードと反対方向
の翼角をもつタービンブレードを取付けたことを特徴と
する回転流体機械の遠心羽根車。
1. A centrifugal impeller of a rotary fluid machine, wherein a turbine blade having a blade angle in a direction opposite to a blade for pressurizing or moving a fluid is attached to a back surface of the shroud disk facing the casing.
JP12829496A 1996-05-23 1996-05-23 Centrifugal impeller of rotational fluid machinery Withdrawn JPH09317692A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP12829496A JPH09317692A (en) 1996-05-23 1996-05-23 Centrifugal impeller of rotational fluid machinery

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP12829496A JPH09317692A (en) 1996-05-23 1996-05-23 Centrifugal impeller of rotational fluid machinery

Publications (1)

Publication Number Publication Date
JPH09317692A true JPH09317692A (en) 1997-12-09

Family

ID=14981253

Family Applications (1)

Application Number Title Priority Date Filing Date
JP12829496A Withdrawn JPH09317692A (en) 1996-05-23 1996-05-23 Centrifugal impeller of rotational fluid machinery

Country Status (1)

Country Link
JP (1) JPH09317692A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102797697A (en) * 2012-04-01 2012-11-28 苏州市世强流体技术有限公司 Light and portable pump impeller
CN102797696A (en) * 2012-04-01 2012-11-28 苏州市世强流体技术有限公司 Novel pump impeller

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102797697A (en) * 2012-04-01 2012-11-28 苏州市世强流体技术有限公司 Light and portable pump impeller
CN102797696A (en) * 2012-04-01 2012-11-28 苏州市世强流体技术有限公司 Novel pump impeller

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Legal Events

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Effective date: 20030805