JPH11257290A - Diffuser of centrifugal compressor - Google Patents
Diffuser of centrifugal compressorInfo
- Publication number
- JPH11257290A JPH11257290A JP8298998A JP8298998A JPH11257290A JP H11257290 A JPH11257290 A JP H11257290A JP 8298998 A JP8298998 A JP 8298998A JP 8298998 A JP8298998 A JP 8298998A JP H11257290 A JPH11257290 A JP H11257290A
- Authority
- JP
- Japan
- Prior art keywords
- diffuser
- angle
- impeller
- side wall
- guide blade
- 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
【０００１】[0001]
【発明の属する技術分野】本発明は、遠心圧縮機におい
て、案内羽根による拡大通路によって流体の運動エネル
ギーを圧力エネルギーに変換するディフューザーの構造
に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of a diffuser in a centrifugal compressor, which converts kinetic energy of fluid into pressure energy by an enlarged passage formed by guide vanes.
【０００２】[0002]
【従来の技術】遠心圧縮機では、羽根車の外周側周囲に
拡大通路によるディフューザーが形成され、羽根車の回
転によって付与された流体の運動エネルギーをディフュ
ーザーによって圧力エネルギーに変換するように構成さ
れる。2. Description of the Related Art In a centrifugal compressor, a diffuser is formed by an enlarged passage around an outer peripheral side of an impeller, and the kinetic energy of fluid given by rotation of the impeller is converted into pressure energy by the diffuser. .
【０００３】このようなディフューザーとして、拡大通
路に案内羽根を備えたものがある。[0003] As such a diffuser, there is one having a guide blade in an enlarged passage.
【０００４】羽根付きディフューザーは、図４に遠心圧
縮機のディフューザー部位の部分概略断面図、図５にそ
のＣ−Ｃ断面図を示すように、羽根車３０の外周側に形
成された回転軸方向前後の側壁１０Ｈ，１０Ｓ（羽根車
のハブ側と対応するハブ側側壁１０Ｈ，羽根車のシュラ
ウド側と対応するシュラウド側側壁１０Ｓ）によって挟
まれた通路空間（ハブ側側壁１０Ｈの内面２０Ｈとシュ
ラウド側側壁１０Ｓの内面２０Ｓの間の空間）が、周方
向に複数配設された案内羽根２１（２１′）…によって
仕切られ、案内羽根２１と隣接する案内羽根２１′の間
に所定の広がり角の拡大通路を形成するように構成され
ている。A diffuser with blades is shown in FIG. 4 in a partial schematic sectional view of a diffuser portion of a centrifugal compressor, and FIG. 5 is a sectional view taken along line CC of FIG. A passage space (the inner surface 20H of the hub side wall 10H and the shroud side) sandwiched between the front and rear side walls 10H, 10S (the hub side wall 10H corresponding to the hub side of the impeller, the shroud side wall 10S corresponding to the shroud side of the impeller). The space between the inner surfaces 20S of the side walls 10S is partitioned by a plurality of guide vanes 21 (21 ')... Arranged in the circumferential direction, and a predetermined spread angle is formed between the guide vane 21 and the adjacent guide vane 21'. It is configured to form an enlarged passage.
【０００５】案内羽根２１は、高さ方向（通路の厚さ方
向）で断面形状一定の二次元翼であってその形状は羽根
車３０からの流体の流出角に基づいて設定されるが、羽
根車３０からの流出角は、羽根車３０の形状に起因して
通路の厚さ方向（羽根車３０の回転軸と平行する方向）
で異なって図７に示すように羽根車３０のシュラウド側
で大きくハブ側で小さく、また、その流量も厚さ方向の
位置によって分布を有するため、これら流出角分布及び
流量分布を勘案して平均的に高い効率が得られるように
設定される。The guide blade 21 is a two-dimensional blade having a constant cross-sectional shape in the height direction (the thickness direction of the passage) and its shape is set based on the outflow angle of the fluid from the impeller 30. The outflow angle from the wheel 30 depends on the shape of the impeller 30 in the thickness direction of the passage (the direction parallel to the rotation axis of the impeller 30).
Differently, as shown in FIG. 7, the flow rate is large on the shroud side of the impeller 30 and small on the hub side, and the flow rate also has a distribution depending on the position in the thickness direction. It is set so that high efficiency is obtained.
【０００６】尚、通路の厚さは通常は一定に設定される
が、希に外周側が広がるように形成して圧縮機全体の外
形を小さく構成するようにしたものもある。Incidentally, the thickness of the passage is usually set to a constant value, but there is a case where the outer shape of the compressor is rarely formed so as to reduce the outer shape of the entire compressor.
【０００７】[0007]
【発明が解決しようとする課題】しかしながら、羽根車
３０の形状に起因する流出角の差異は２０〜３０゜にも
及び、上記従来のごとく案内羽根２１の形状を平均的に
設定した場合、特に流出角が小さい羽根車のハブ側と対
応する案内羽根２１の圧力面２１Ａに流体剥離が発生す
るという問題があった。即ち、図６及びそのＥ矢視図に
相当する通路出口図である図７中に低速領域を示すよう
に、案内羽根２１の後端部のハブ側内面２０Ｈの近傍に
剥離が発生する低速部位がある。However, the difference in the outflow angle due to the shape of the impeller 30 is as large as 20 to 30 °, and when the shape of the guide blade 21 is set averagely as in the above-mentioned conventional case, particularly, There has been a problem that fluid separation occurs on the pressure surface 21A of the guide blade 21 corresponding to the hub side of the impeller having a small outflow angle. That is, as shown in FIG. 6 and FIG. 7 which is a passage exit view corresponding to the view taken in the direction of arrow E, a low-speed region where peeling occurs near the hub-side inner surface 20H at the rear end of the guide blade 21 is shown. There is.
【０００８】このような剥離が生ずると、ディフューザ
ーの全圧損失が増加し、性能低下を来す。[0008] When such peeling occurs, the total pressure loss of the diffuser increases and the performance decreases.
【０００９】本発明は、上記解決課題に鑑みて成された
ものであって、流出角の小さなハブ側においても案内羽
根の圧力面側に剥離を生ずることがなく、ディフューザ
ーの全圧損失の増加を防いで効率向上を可能とする遠心
圧縮機のディフューザーを提供することを目的とする。SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and does not cause separation on the pressure surface side of the guide blade even on the hub side having a small outflow angle, thereby increasing the total pressure loss of the diffuser. It is an object of the present invention to provide a diffuser for a centrifugal compressor, which can improve efficiency by preventing the occurrence of a diffuser.
【００１０】[0010]
【課題を解決するための手段】上記目的を達成する本発
明に係る遠心圧縮機のディフューザーは、遠心圧縮機に
おいて案内羽根による拡大通路によって流体の運動エネ
ルギーを圧力エネルギーに変換するディフューザーであ
って、前記案内羽根は、その圧力面と、羽根車のハブ側
と対応する側壁面とが成す角度が、９０゜より狭角とな
る方向に所定角度で傾斜形成されていることを特徴とす
る。According to the present invention, there is provided a diffuser for a centrifugal compressor according to the present invention for converting kinetic energy of fluid into pressure energy by an enlarged passage formed by guide vanes in the centrifugal compressor. The guide blade is characterized in that an angle formed between a pressure surface thereof and a side wall surface corresponding to the hub side of the impeller is inclined at a predetermined angle in a direction in which the angle is smaller than 90 °.
【００１１】[0011]
【発明の実施の形態】以下添付図面を参照して本発明の
実施の形態について説明する。図１は、本発明に係る遠
心圧縮機のディフューザーの一構成例を適用した圧縮機
のディフューザー部位の部分概略断面図であり、図２は
そのＡ−Ａ断面図である。Embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a partial schematic cross-sectional view of a diffuser part of a compressor to which a configuration example of a diffuser of a centrifugal compressor according to the present invention is applied, and FIG. 2 is a cross-sectional view along AA.
【００１２】図示圧縮機１は、ケーシング１０によっ
て、羽根車室１１とその外周側の渦形室１２の間にディ
フューザー２０が形成されており、羽根車室１１内に配
設された羽根車３０が図示しない回転駆動手段によって
回転駆動されて、吸気口１３から吸入した流体に径方向
の運動エネルギーを与えると共にディフューザー２０で
圧力エネルギーに変換して渦形室１２に吐出するように
なっている。The illustrated compressor 1 has a casing 10 in which a diffuser 20 is formed between an impeller chamber 11 and a spiral chamber 12 on the outer periphery thereof, and an impeller 30 disposed in the impeller chamber 11 is provided. Are rotationally driven by rotation driving means (not shown) to apply kinetic energy in the radial direction to the fluid sucked from the intake port 13 and convert the fluid into pressure energy by the diffuser 20 and discharge the pressure energy to the spiral chamber 12.
【００１３】ディフューザー２０は、羽根車３０の外周
側に、ケーシング１０の側壁（羽根車３０のハブ側と対
応するハブ側側壁１０Ｈ，羽根車３０のシュラウド側と
対応するシュラウド側側壁１０Ｓ）に挟まれた通路空間
（ハブ側側壁１０Ｈの内面２０Ｈとシュラウド側側壁１
０Ｓの内面２０Ｓの間の空間）が周方向に複数配設され
た案内羽根２１（２１′）…によって仕切られ、案内羽
根２１と隣接する案内羽根２１′の間にスロートから下
流が半径方向に所定の広がり角で拡大通路を形成してい
る。The diffuser 20 is sandwiched on the outer peripheral side of the impeller 30 by the side wall of the casing 10 (hub side wall 10H corresponding to the hub side of the impeller 30, shroud side wall 10S corresponding to the shroud side of the impeller 30). Passage space (the inner surface 20H of the hub side wall 10H and the shroud side wall 1).
The space between the inner surfaces 20S of the outer and outer guides 21S is partitioned by a plurality of guide vanes 21 (21 ')... An enlarged passage is formed at a predetermined spread angle.
【００１４】ここで、案内羽根２１は、その圧力面２１
Ａと、ハブ側側壁１０Ｈの内面２０Ｈとが成す角度：θ
が、９０゜より狭角となる方向に所定角度で傾斜形成さ
れている。案内羽根２１の羽根車回転軸方向の断面形状
は一定とされて入口角及び出口角一定となるように形成
されており、従って、拡大通路の案内羽根２１と交差す
る方向の断面形状は、図２のＢ矢視図に相当する通路出
口図である図３に示すように平行四辺形を呈している。Here, the guide blade 21 has its pressure surface 21
A and the angle formed by the inner surface 20H of the hub side wall 10H: θ
Are inclined at a predetermined angle in a direction that is narrower than 90 °. The cross-sectional shape of the guide blade 21 in the impeller rotation axis direction is constant and formed so as to have a constant entrance angle and a constant exit angle. Therefore, the cross-sectional shape of the enlarged passage in the direction intersecting with the guide blade 21 is shown in FIG. 2 shows a parallelogram as shown in FIG. 3 which is a passage exit view corresponding to the view on arrow B of FIG.
【００１５】このように、案内羽根２１の圧力面２１Ａ
と、ハブ側側壁１０Ｈの内面２０Ｈとが成す角度が９０
゜より狭角に形成されていることにより、案内羽根２１
の後端に発達する剥離を抑制することが可能となる。As described above, the pressure surface 21A of the guide blade 21
And the inner surface 20H of the hub side wall 10H has an angle of 90 °.
案 内 Because it is formed at a narrower angle, the guide blade 21
Can be prevented from developing at the rear end.
【００１６】即ち、隣接する案内羽根２１によって形成
された拡大通路内では、案内羽根２１の圧力面側２１Ａ
に流体剥離を生じ易いが、羽根車３０の形状に起因する
通路厚さ方向の流出分布によって、流出角の大きいシュ
ラウド側側壁１０Ｈの内面２０Ｈの境界層内に案内羽根
２１の負圧面２１Ｂ側から圧力面２１Ａ側へ流れる二次
流れが生じ、この二次流れが圧力面２１Ａに衝突した後
圧力面２１Ａに沿ってハブ側側壁１０Ｈ（内面２０Ｈ）
に向かうためにこれによって剥離が押さえられ、二次流
れの大きい案内羽根２１の先端部位では剥離が小さく、
案内羽根２１の後端のハブ側側壁１０Ｈの内面２０Ｈ近
傍に剥離領域が形成される。That is, in the enlarged passage formed by the adjacent guide vanes 21, the pressure surface side 21A of the guide vanes 21
However, due to the outflow distribution in the thickness direction of the passage caused by the shape of the impeller 30, the outflow distribution in the inner surface 20H of the shroud-side side wall 10H having a large outflow angle is located within the boundary layer of the guide blade 21 from the negative pressure surface 21B side. A secondary flow that flows to the pressure surface 21A side is generated, and after the secondary flow collides with the pressure surface 21A, the hub side wall 10H (the inner surface 20H) along the pressure surface 21A.
Therefore, the separation is suppressed at the tip of the guide blade 21 where the secondary flow is large,
A peeling region is formed near the inner surface 20H of the hub side wall 10H at the rear end of the guide blade 21.
【００１７】この剥離領域を形成する案内羽根２１の圧
力面２１Ａとハブ側側壁１０Ｈの内面２０Ｈの成す角度
が狭角とされるため、流速が向上することとなって図３
中に示すように低流速域が減少し剥離を抑制することが
できるものである。Since the angle formed between the pressure surface 21A of the guide blade 21 forming the separation area and the inner surface 20H of the hub side wall 10H is made narrow, the flow velocity is improved, and the flow rate is improved as shown in FIG.
As shown in the figure, the low flow velocity region is reduced and the separation can be suppressed.
【００１８】圧力面２１Ａのハブ側側壁１０Ｈの内面２
０Ｈとが成す角度：θは、主流域の流速の増大を伴うこ
となく低速領域が消滅する程度に設定し、７５゜〜４５
゜程度が好ましい。尚、図４は略４５゜とした例であ
る。Inner surface 2 of hub side wall 10H of pressure surface 21A
Is set to such an extent that the low-speed region disappears without increasing the flow velocity in the main flow region, and 75 ° to 45 °.
゜ is preferred. FIG. 4 shows an example in which the angle is approximately 45 °.
【００１９】上記のごとく、案内羽根２１が、その圧力
面２１Ａとハブ側側壁１０Ｈの内面２０Ｈとが成す角
度：θが、９０゜より狭角となる方向に所定角度で傾斜
形成されていることにより、案内羽根２１の圧力面２１
Ａの後端近傍での流体剥離域が減少し、その結果、ディ
フューザーの全圧損失の増加を防いで効率を向上させる
ことができる。As described above, the guide blade 21 is formed to be inclined at a predetermined angle in a direction in which the angle θ formed by the pressure surface 21A and the inner surface 20H of the hub side wall 10H is smaller than 90 °. The pressure surface 21 of the guide blade 21
The fluid separation area in the vicinity of the rear end of A is reduced, and as a result, an increase in the total pressure loss of the diffuser can be prevented and the efficiency can be improved.
【００２０】[0020]
【発明の効果】以上述べたように、本発明による遠心圧
縮機のディフューザーによれば、案内羽根が、その圧力
面と、羽根車のハブ側と対応する側壁面とが成す角度
が、９０゜より狭角となる方向に所定角度で傾斜形成さ
れていることにより、案内羽根の圧力面後端近傍での流
体剥離を抑制することができ、ディフューザーの全圧損
失の増加を防いで効率を向上させることができるもので
ある。As described above, according to the diffuser of the centrifugal compressor according to the present invention, the angle between the pressure surface of the guide blade and the side wall surface corresponding to the hub side of the impeller is 90 °. Since it is inclined at a predetermined angle in the direction of becoming narrower, fluid separation near the rear end of the pressure surface of the guide blade can be suppressed, and the total pressure loss of the diffuser is prevented from increasing, improving efficiency. That can be done.
【図１】本発明に係る遠心圧縮機のディフューザーの一
構成例を適用した圧縮機のディフューザー部位の部分概
略断面図である。FIG. 1 is a partial schematic cross-sectional view of a diffuser part of a compressor to which a configuration example of a diffuser of a centrifugal compressor according to the present invention is applied.
【図２】図１のＡ−Ａ断面図である。FIG. 2 is a sectional view taken along line AA of FIG.
【図３】図２のＢ矢視図に相当する通路出口の低速領域
を示す図である。FIG. 3 is a view showing a low speed region at a passage exit corresponding to a view taken in the direction of arrow B in FIG. 2;
【図４】従来例としての圧縮機のディフューザー部位の
部分概略断面図である。FIG. 4 is a partial schematic sectional view of a diffuser portion of a compressor as a conventional example.
【図５】図５のＣ−Ｃ断面図である。FIG. 5 is a sectional view taken along the line CC of FIG. 5;
【図６】図５のＤ矢視図に相当する通路出口の低速領域
を示す図である。FIG. 6 is a diagram showing a low speed region at a passage exit corresponding to a view taken in the direction of arrow D in FIG. 5;
【図７】通路の厚さ方向における流出角分布を示す図で
ある。FIG. 7 is a diagram showing an outflow angle distribution in a thickness direction of a passage.
１ 圧縮機（遠心圧縮機） ２０ ディフューザー ２０Ｈ ハブ側側壁内面（羽根車のハブ側と対応する側
壁面） ２１ 案内羽根 ２１Ａ 圧力面 θ 案内羽根の圧力面と羽根車のハブ側と対応する側壁
面とが成す角度DESCRIPTION OF SYMBOLS 1 Compressor (centrifugal compressor) 20 Diffuser 20H Inner surface of side wall on hub side (side wall surface corresponding to hub side of impeller) 21 Guide blade 21A Pressure surface θ Pressure surface of guide blade and side wall surface corresponding to hub side of impeller Angle between
Claims (1)
大通路によって流体の運動エネルギーを圧力エネルギー
に変換するディフューザーであって、 前記案内羽根は、その圧力面と、羽根車のハブ側と対応
する側壁面とが成す角度が、９０゜より狭角となる方向
に所定角度で傾斜形成されていることを特徴とする遠心
圧縮機のディフューザー。1. A diffuser for converting kinetic energy of fluid into pressure energy by an enlarged passage of a guide blade in a centrifugal compressor, wherein the guide blade has a pressure surface and a side corresponding to a hub side of an impeller. A diffuser for a centrifugal compressor, wherein the diffuser is inclined at a predetermined angle in a direction in which an angle formed by a wall surface is smaller than 90 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8298998A JPH11257290A (en) | 1998-03-13 | 1998-03-13 | Diffuser of centrifugal compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8298998A JPH11257290A (en) | 1998-03-13 | 1998-03-13 | Diffuser of centrifugal compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH11257290A true JPH11257290A (en) | 1999-09-21 |
Family
ID=13789640
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8298998A Pending JPH11257290A (en) | 1998-03-13 | 1998-03-13 | Diffuser of centrifugal compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH11257290A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002332996A (en) * | 2001-05-10 | 2002-11-22 | Mitsubishi Heavy Ind Ltd | Diffuser and turbo-pump |
| JP2009504974A (en) * | 2005-08-09 | 2009-02-05 | プラクスエア・テクノロジー・インコーポレイテッド | Lean type centrifugal compressor airfoil diffuser |
| CN105683582A (en) * | 2013-08-19 | 2016-06-15 | 动力推进***有限公司 | Diffuser for a forward-swept tangential flow compressor |
| CN113074142A (en) * | 2020-01-06 | 2021-07-06 | 广东威灵电机制造有限公司 | Diffusion device, fan and dust catcher |
| CN115978005A (en) * | 2023-03-17 | 2023-04-18 | 潍柴动力股份有限公司 | Guide vane and design method thereof, diffuser, compressor and supercharger |
-
1998
- 1998-03-13 JP JP8298998A patent/JPH11257290A/en active Pending
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002332996A (en) * | 2001-05-10 | 2002-11-22 | Mitsubishi Heavy Ind Ltd | Diffuser and turbo-pump |
| JP2009504974A (en) * | 2005-08-09 | 2009-02-05 | プラクスエア・テクノロジー・インコーポレイテッド | Lean type centrifugal compressor airfoil diffuser |
| KR101286344B1 (en) * | 2005-08-09 | 2013-07-15 | 프랙스에어 테크놀로지, 인코포레이티드 | Leaned centrifugal compressor airfoil diffuser |
| CN105683582A (en) * | 2013-08-19 | 2016-06-15 | 动力推进***有限公司 | Diffuser for a forward-swept tangential flow compressor |
| CN113074142A (en) * | 2020-01-06 | 2021-07-06 | 广东威灵电机制造有限公司 | Diffusion device, fan and dust catcher |
| CN115978005A (en) * | 2023-03-17 | 2023-04-18 | 潍柴动力股份有限公司 | Guide vane and design method thereof, diffuser, compressor and supercharger |
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