JPS6261800B2 - - Google Patents
Info
- Publication number
- JPS6261800B2 JPS6261800B2 JP15811282A JP15811282A JPS6261800B2 JP S6261800 B2 JPS6261800 B2 JP S6261800B2 JP 15811282 A JP15811282 A JP 15811282A JP 15811282 A JP15811282 A JP 15811282A JP S6261800 B2 JPS6261800 B2 JP S6261800B2
- Authority
- JP
- Japan
- Prior art keywords
- flow
- differential
- user
- angle
- differential user
- 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
- 239000012530 fluid Substances 0.000 claims description 30
- 238000011144 upstream manufacturing Methods 0.000 claims description 4
- 238000011084 recovery Methods 0.000 description 9
- 230000007423 decrease Effects 0.000 description 8
- 230000000694 effects Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
- 238000013459 approach Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 239000011295 pitch Substances 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000010420 art technique Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は遠心形あるいは斜流形流体機械の羽根
付デイフユーザに関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a vaned differential user for a centrifugal or mixed flow type fluid machine.
［従来の技術］
第１図は従来の遠心形の流体機械（圧縮機）の
縦断面図であり、１は羽根車、２は回転軸、３は
前記羽根車１を回転軸２に固定するためのナツト
である。羽根車の半径方向外方には、一対のデイ
フユーザ板４および５により限られる流路すなわ
ち羽根なしデイフユーザ部６と、デイフユーザ板
４，５および羽根７よりなる羽根付デイフユーザ
部８とから成る羽根付デイフユーザが設けられ、
さらにその外方にはケーシング９が設けられてい
る。１０は羽根車１の吸込口に流体を導くための
吸込管である。[Prior Art] Fig. 1 is a vertical cross-sectional view of a conventional centrifugal fluid machine (compressor), in which 1 is an impeller, 2 is a rotating shaft, and 3 is the impeller 1 fixed to the rotating shaft 2. This is Natsuto. On the radially outward side of the impeller, there is a vaned blade including a flow path, that is, a bladeless diff user part 6, which is limited by a pair of diff user plates 4 and 5, and a vaned diff user part 8, which is made up of the diff user plates 4, 5 and the blades 7. A differential user is provided,
Furthermore, a casing 9 is provided on the outside thereof. 10 is a suction pipe for guiding fluid to the suction port of the impeller 1.
流体は吸込管を通じ、吸込口より羽根車に吸込
まれる。羽根車内ではその流路面に境界層が発達
し、またコリオリカや流路の曲がり等の影響を受
けるので、低運動量の流体が円周方向については
羽根の負圧面（回転方向後面）に、また羽根の幅
方向については側板側に集まる。（１３……心
板、１４……側板）。この結果、羽根車出口にお
いては第２図に示すような流れの歪が生ずる。す
なわち壁面付近では流れ角度（羽根車あるいはデ
イフユーザの回転中心を中心とする円周方向と流
れとがなす角）は小さく、流体のもつ運動量は小
さい。第２図に示したような流れの歪は羽根なし
デイフユーザ部６内でも消えずに残り、このため
羽根なしデイフユーザ部６での圧力回復率が低下
し、また流れの歪が大きい場合には羽根なしデイ
フユーザ部６の壁面付近で流れは剥離し、損失が
増加する。さらに羽根付デイフユーザ部８の入口
において流れ角に幅方向分布があると、入口の羽
根角度は幅方向に一定であるから、幅方向の特定
の位置では流れ角と羽根角度とを一致させること
ができても、他の位置では流れ角と羽根角とが一
致しなくなつて入射損失（衝突損失）が増大す
る。この入射損失は、特に、羽根入口の壁面付近
で大きい。また、羽根付デイフユーザ部８内では
主流は第３図に示す羽根の方向に沿つて流れる
が、デイフユーザ板４，５の流路表面付近の境界
層内では第４図に示すように羽根の圧力面１２か
ら負圧面１１に向う二次流れが生ずる。この結果
二次流れに基づく損失も発生する。 The fluid passes through the suction pipe and is sucked into the impeller from the suction port. Inside the impeller, a boundary layer develops on the flow path surface, and it is also affected by Coriolis and bending of the flow path. Therefore, fluid with low momentum flows in the circumferential direction onto the suction surface (rear surface in the rotational direction) of the blade, and on the blade In the width direction, it gathers on the side plate side. (13... core plate, 14... side plate). As a result, a flow distortion as shown in FIG. 2 occurs at the impeller outlet. That is, near the wall surface, the flow angle (the angle between the flow and the circumferential direction around the rotation center of the impeller or diff user) is small, and the momentum of the fluid is small. The flow distortion shown in FIG. 2 remains in the vaneless differential user section 6, and as a result, the pressure recovery rate in the vaneless differential user section 6 decreases, and if the flow distortion is large, the impeller None The flow separates near the wall surface of the differential user section 6, increasing loss. Furthermore, if there is a distribution in the width direction of the flow angle at the entrance of the bladed differential user section 8, since the blade angle at the entrance is constant in the width direction, it is difficult to match the flow angle and the blade angle at a specific position in the width direction. Even if it is possible, the flow angle and the blade angle will not match at other positions, resulting in an increase in incident loss (collision loss). This incidence loss is particularly large near the wall surface of the blade inlet. In addition, in the vaned differential user section 8, the main flow flows along the direction of the vanes as shown in FIG. A secondary flow occurs from surface 12 towards suction surface 11 . As a result, losses due to secondary flows also occur.
以上述べた羽根なしデイフユーザ部６内での損
失、羽根付デイフユーザ部８入口における入射損
失、および羽根付デイフユーザ部８内の二次流れ
損失は遠心圧縮機などの流体機械の性能向上を妨
げる原因となる。なお、この種従来技術としては
特公昭32−2127号公報に記載のものなどがある。 The losses in the vaned differential user section 6, the incident loss at the inlet of the vaned differential user section 8, and the secondary flow loss within the vaned differential user section 8 described above are causes that hinder the performance improvement of fluid machines such as centrifugal compressors. Become. Incidentally, this type of prior art includes the one described in Japanese Patent Publication No. 32-2127.
上記従来技術の羽根付デイフユーザの例として
は、実公昭46−28119号や日本特許第11044号など
がある。これらについて以下簡単に説明する。 Examples of the above-mentioned conventional bladed differential users include Utility Model Publication No. 46-28119 and Japanese Patent No. 11044. These will be briefly explained below.
実公昭46−28119号には、デイフユーザの翼間
に形成される空間内に延びる小翼を設け、デイフ
ユーザ翼の凸面外周に沿つて流れながら発達する
境界層の発生を防止するようにした遠心送風機、
ポンプのデイフユーザが開示されている。この技
術は小翼によつて境界層の発生を防止するだけの
ものであるから、その小翼の高さは境界層の厚さ
程度であつて、この小翼によつて羽根車出口の非
一様な流れを一様化することはできず、このため
上述した従来技術と同様、羽根なしデイフユーザ
部材での損失、および羽根付デイフユーザ部入口
における入射損失を低減することはできない。 Utility Model Publication No. 46-28119 discloses a centrifugal blower that is equipped with small blades that extend into the space formed between the blades of a diffuser to prevent the formation of a boundary layer that develops while flowing along the outer periphery of the convex surface of the diffuser blade. ,
A differential user of the pump is disclosed. Since this technology only prevents the formation of a boundary layer using the small blades, the height of the small blades is approximately the thickness of the boundary layer, and the small blades prevent the impeller outlet from forming. A uniform flow cannot be made uniform, and therefore, similarly to the prior art described above, it is not possible to reduce the loss in the bladeless differential user member and the incident loss at the entrance of the bladed differential user part.
日本特許第11044号のものには、デイフユーザ
にその流路幅と同じ高さの羽根が長短２種類設け
られているものである。このような羽根付デイフ
ユーザにおいては、デイフユーザ流路幅と同じ高
さの羽根がデイフユーザの入口直後から設けられ
ているために、羽根車出口直後の流速の大なる流
体がすぐ羽根に衝突し、流体のデイフユーザへの
入射損失が極めて大となるばかりでなく、羽根付
デイフユーザ部内に二次流れが発生することも防
止できない。 In Japanese Patent No. 11044, the diff user is provided with two types of vanes, long and short, each having the same height as the flow path width. In such a vaned differential user, since the vanes with the same height as the width of the diff user flow path are provided immediately after the entrance of the diff user, the fluid with a high flow velocity immediately after the impeller exit immediately collides with the vanes, causing the fluid to Not only does the incident loss to the differential user become extremely large, but it is also impossible to prevent secondary flow from occurring within the vaned differential user section.
上述した従来技術はいづれもデイフユーザの流
路幅と同一高さの羽根をもつ羽根付デイフユーザ
のものであるが、この他に上記したような羽根を
もたない羽根なしデイフユーザと呼ばれるものが
ある。この羽根なしデイフユーザにおいても、デ
イフユーザ内において二次流れ損失や剥離損失が
生じるため、それを防止する技術として、ソ連特
許発明第419639号や特開昭50−23004号が公知で
ある。これらの従来技術はいづれも、デイフユー
ザ流路内の流れ方向に沿つて境界層厚さにほぼ等
しい高さのリブをデイフユーザ板の流路表面上に
設けたものである。 All of the above-mentioned prior art techniques are bladed diff users having blades of the same height as the channel width of the diff user, but there is also a type called a vaneless diff user which does not have blades as described above. Even in this bladeless differential user, secondary flow loss and separation loss occur within the differential user, and techniques for preventing this are known as disclosed in Soviet Patent No. 419,639 and Japanese Patent Application Laid-Open No. 50-23004. In all of these conventional techniques, ribs having a height approximately equal to the boundary layer thickness are provided on the flow path surface of the diffuser plate along the flow direction within the diffuser flow path.
［発明が解決しようとする問題点］
上述した羽根付デイフユーザに関する従来技術
では、羽根なしデイフユーザ部での圧力回復率を
向上すること、羽根付デイフユーザ入口における
流体の羽根への衝突損失を低減することに関して
は全く考慮されていなかつた。[Problems to be Solved by the Invention] In the conventional technology related to the bladed differential user described above, it is necessary to improve the pressure recovery rate in the bladeless differential user section and to reduce the collision loss of fluid against the blades at the inlet of the bladed differential user. was not considered at all.
また、羽根なしデイフユーザに関する従来技術
でも、羽根車出口からの歪んだ流れを一様分布流
れに近づけて圧力回復率を向上させることに関し
ては何も考慮されていない。すなわち、実公昭46
−28119号公報では羽根付デイフユーザ部の上流
の羽根なしデイフユーザ部には小翼が設けられて
いないため、羽根車出口直後の歪んだ流れは幅方
向に一様化されることなく羽根入口部に到る。そ
のため、羽根なしデイフユーブ部の圧力回復が低
下するとともに、羽根入口部で大きな入射損失が
生ずる。 Further, in the conventional technology related to a vaneless differential user, no consideration is given to improving the pressure recovery rate by bringing the distorted flow from the impeller outlet closer to a uniformly distributed flow. In other words, Jikko 46
- In Publication No. 28119, the bladeless differential user section upstream of the bladed differential user section is not provided with small blades, so the distorted flow immediately after the impeller outlet is not uniformed in the width direction and flows into the impeller inlet section. Arrive. As a result, the pressure recovery in the bladeless diffuser portion is reduced and a large incident loss occurs at the blade inlet.
また、日本特許第11044号のものには、羽根車
出口直後に流路幅と同じ高さの羽根が設けられて
いるため、やはり羽根車出口直後の幅方向に歪ん
だ流れは一様化されることなく羽根と衝突する。
このため、大きな入射損失が発生する。さらに翼
間にはリブが設けられていないため、２次流れを
防止することができない。さらに、ソ連特許第
419639号には境界層厚さにほぼ等しい高さのリブ
が設けられているが、高さが低いため羽根なしデ
イフユーザ内の歪んだ流れ全体を幅方向に一様化
する作用は極めて小さい。 In addition, in the Japanese Patent No. 11044, since a blade with the same height as the flow path width is provided immediately after the impeller exit, the flow distorted in the width direction immediately after the impeller exit is also made uniform. It collides with the feather without any problem.
Therefore, a large incident loss occurs. Furthermore, since no ribs are provided between the blades, secondary flow cannot be prevented. In addition, Soviet patent no.
No. 419639 is provided with ribs having a height approximately equal to the boundary layer thickness, but because the height is low, the effect of uniformizing the entire distorted flow in the bladeless diffuser in the width direction is extremely small.
本発明の目的は、羽根車出口からの歪んだ流れ
をデイフユーザの入口直後から一様分布流れに近
づけ、それによつて羽根なしデイフユーザ部での
圧力回復率を向上し、また羽根付デイフユーザ部
入口における流体の羽根への衝突損失を低減し
て、大幅な性能向上を計るようにした羽根付デイ
フユーザを得ることにある。 The object of the present invention is to bring the distorted flow from the impeller outlet closer to a uniformly distributed flow immediately after the entrance of the differential user, thereby improving the pressure recovery rate at the bladeless differential user section, and to improve the pressure recovery rate at the entrance of the vaned differential user section. To obtain a differential user with vanes capable of greatly improving performance by reducing collision loss of fluid with vanes.
［問題点を解決するための手段］
上記目的を達成するため本発明は、羽根間の少
なくとも側板側のデイフユーザ板の流路表面状
に、デイフユーザ壁面付近の低流れ角度部分の流
れを案内するリブを設け、このリブは羽根の前縁
よりも上流側に形成された前記羽根なしデイフユ
ーザ部の入口直後まで延長して設け、そのリブの
前縁部における入口角を羽根の入口角よりも小さ
く形成し、羽根の出入口間におけるリブのそりは
羽根と同一のそりとなるように構成したものであ
る。[Means for Solving the Problems] In order to achieve the above object, the present invention provides a rib that guides the flow in a low flow angle portion near the wall surface of the diffuser on the flow path surface of the diffuser plate at least on the side plate side between the blades. , the rib is provided to extend immediately after the entrance of the bladeless diff user section formed upstream of the leading edge of the blade, and the entrance angle at the leading edge of the rib is formed to be smaller than the entrance angle of the blade. However, the curvature of the rib between the entrance and exit of the blade is the same as that of the blade.
なお、低流れ角度の領域とは、平均流れ角度よ
りも小さい流れ角度をもつ流れの領域をいう。 Note that the low flow angle region refers to a flow region having a flow angle smaller than the average flow angle.
［作用］
本発明は上記のように構成したことにより次の
作用を奏する。即ち本発明はリブ前縁部の入口角
を羽根の入口角よりも小さくしたので、羽根なし
デイフユーザ部では壁面付近の流れ角の小さい流
体が衝突損失なくリブに流入するようになる。更
に羽根なしデイフユーザ部では入口角を小さくし
たこととリブを延長したこととの相乗作用により
リブに沿つて剥離することなく流れ、その流体が
下流に進むに従つてその流れ角度はリブによつて
強制的に平均流れ角度付近の流れ角度まで大きく
きれる。このため、流れ角度の大きいデイフユー
ザ板間の中心付近を流れる流体の流れ角度は逆に
小さくなる。この理由はデイフユーザ板近くの低
流れ角度の流体を強制的に、その流れ角度を大き
くし、その部分の流れを半径方向に向けてやる
と、リブを設けた領域では流れの半径方向速度成
分は増大し、この領域を通過する流量が増加する
から、これに伴つて流れ角度の大きい領域の流量
は減少するので、リブの設けられていない領域の
流れ半径方向速度成分は減少し、この領域の流れ
角度は平均流れ角度付近まで小さくなる。従つ
て、デイフユーザ入口の歪んだ流れをリブによつ
て強制的に一様分布流れに近づけることができ
る。[Function] The present invention achieves the following effects by being configured as described above. That is, in the present invention, the inlet angle of the front edge of the rib is made smaller than the inlet angle of the vane, so that in the vaneless diffuser section, fluid with a small flow angle near the wall surface flows into the rib without collision loss. Furthermore, in the bladeless differential user section, the synergistic effect of the small inlet angle and the extended ribs causes the fluid to flow along the ribs without separation, and as the fluid advances downstream, the flow angle is changed by the ribs. The flow angle is forced to be large and close to the average flow angle. Therefore, the flow angle of the fluid flowing near the center between the diffuser plates, where the flow angle is large, becomes small. The reason for this is that if you force the fluid at a low flow angle near the diffuser plate, increase the flow angle, and direct the flow in that area in the radial direction, the radial velocity component of the flow in the region where the ribs are provided will decrease. Since the flow rate passing through this region increases, the flow rate in the region with a large flow angle decreases, so the radial velocity component of the flow in the region without ribs decreases, and the flow rate in this region increases. The flow angle decreases to near the average flow angle. Therefore, the distorted flow at the entrance of the diffuser can be forced to approach a uniformly distributed flow by the ribs.
［実施例］
次に、本発明の一実施例を第５図〜第７図によ
り説明する。[Example] Next, an example of the present invention will be described with reference to FIGS. 5 to 7.
この実施例は本発明を遠心形流体機械（圧縮
機）に適用した場合を示す。羽根付デイフユーザ
の羽根１ピツチの中間の位置に各デイフユーザ板
４，５の流路表面上に、デイフユーザ羽根７の高
さの半分より低くかつデイフユーザ板上の低流れ
角度の領域の流体のほぼ全体を案内する程度の高
さを有するリブ１５設けられている。このリブ１
５は羽根７の前縁よりも上流側に形成された羽根
なしデイフユーザ部６の入口直後まで延長して設
けられている。また、リブ１５は羽根７の出入口
間においては羽根７と同一のそりを持ち、このリ
ブ１５の前縁部においてはその入口角がデイフユ
ーザ羽根７の入口角より小さくなるように構成さ
れている。このようなリブ１５が設けられている
ことにより、羽根なしデイフユーザ部６では壁面
付近の流れ角の小さい流体が衝突損失なくリブに
流入し、かつ該リブ１５に沿つて剥離することな
く流れ、その流体が下流に進むに従つてその流れ
角度はリブ１５によつて強制的に平均流れ角度付
近の流れ角度まで大きくされる。このため、流れ
角度の大きいデイフユーザ板間の中心付近を流れ
る流体の流れ角度は逆に小さくなる。この理由
は、デイフユーザ板近くの低流れ角度の流体を強
制的にその流れ角度を大きくし、その部分の流れ
を半径方向に向けてやると、リブを設けた領域で
の流れの半径方向速度成分は増大し、この領域を
通過する流量が増加するから、これに伴つて流れ
角度の大きい領域の流量は減少するので、リブの
設けられていない領域の流れ半径方向速度成分は
減少し、この領域の流れ角度は平均流れ角度付近
まで小さくなる。従つて、全体としてデイフユー
ザ入口の歪んだ流れをリブによつて強制的に一様
分布流れに近づけることができる。 This embodiment shows a case where the present invention is applied to a centrifugal fluid machine (compressor). Substantially the entire fluid in the area lower than half the height of the diffuser blade 7 and at a low flow angle on the diffuser plate is placed on the flow path surface of each diffuser plate 4, 5 at a position midway between the pitches of the blades of the vaned differential user. A rib 15 is provided with a height sufficient to guide the. This rib 1
5 extends to immediately after the entrance of a bladeless diffuser section 6 formed upstream of the leading edge of the blade 7. Further, the rib 15 has the same curvature as the blade 7 between the entrance and exit of the blade 7, and the front edge of the rib 15 is configured such that its entrance angle is smaller than the entrance angle of the diffuser blade 7. By providing such a rib 15, in the bladeless diff user section 6, fluid with a small flow angle near the wall surface flows into the rib without collision loss, flows along the rib 15 without separation, and its As the fluid advances downstream, its flow angle is forced by the ribs 15 to increase to a flow angle near the average flow angle. Therefore, the flow angle of the fluid flowing near the center between the diffuser plates, where the flow angle is large, becomes small. The reason for this is that if the fluid with a low flow angle near the diffuser plate is forced to increase its flow angle and the flow in that area is directed in the radial direction, the radial velocity component of the flow in the region where the ribs are provided increases, and the flow rate passing through this region increases, so the flow rate in the region with a large flow angle decreases, so the radial velocity component of the flow in the region without ribs decreases, and the flow rate in this region increases. The flow angle decreases to around the average flow angle. Therefore, as a whole, the distorted flow at the entrance of the diffuser can be forced to approach a uniformly distributed flow by the ribs.
次に、本発明を遠心圧縮機のデイフユーザに適
用した場合の具体的実施例によつて本発明の効果
を説明する。 Next, the effects of the present invention will be explained with reference to a specific example in which the present invention is applied to a differential user of a centrifugal compressor.
第８図は、側板側のデイフユーザ板４の流路表
面上に、本発明に係るリブ１５を備える羽根付デ
イフユーザの場合と、リブ１５を備えていない従
来の羽根付デイフユーザの場合の、羽根付デイフ
ユーザ部入口（羽根７の前縁部分）における流体
のデイフユーザ流路幅方向の流れ角度分布を比較
して示したものである。図において、曲線ｍは従
来例を示し、リブを設けていない羽根付デイフユ
ーザ部入口の流れ角の分布を示すもので、流路幅
方向にかなり歪んでいると共に側板側の流れ角度
はかなり小さくなつている。また、曲線ｎは本発
明の例を示すもので、流路幅の21％の高さ（図の
破線ｌの領域）のリブを側板側壁面に取付けた場
合の羽根付デイフユーザ部入口の流れ角の分布を
示すもので、流れがほぼ一様化されていることが
わかる。羽根なしデイフユーザ部６の長さは第５
図に示すようにあまり長くはないが、羽根なしデ
イフユーザ部６の入口直後から設けられた高さの
かなり高い本発明に係るリブ１５によつて、羽根
車出口からの大きく歪んだ流れは羽根付デイフユ
ーザ部入口に達するまでにかなり一様分布流れに
近づくことがわかる。 FIG. 8 shows the case of a bladed differential user having ribs 15 according to the present invention on the flow path surface of the side plate side differential user plate 4, and the case of a conventional bladed differential user not having ribs 15. 7 shows a comparison of the flow angle distribution of the fluid in the width direction of the diffuser flow path at the entrance of the diffuser section (the leading edge portion of the blade 7). In the figure, curve m shows the conventional example, and shows the flow angle distribution at the inlet of the vaned differential user part without ribs, which is considerably distorted in the channel width direction and the flow angle on the side plate side is considerably small. ing. Curve n shows an example of the present invention, and shows the flow angle at the inlet of the vaned differential user section when a rib with a height of 21% of the flow path width (area indicated by the broken line l in the figure) is attached to the side wall surface of the side plate. It can be seen that the flow is almost uniform. The length of the bladeless differential user section 6 is 5th.
As shown in the figure, the highly distorted flow from the impeller outlet is prevented by the rib 15 according to the present invention, which is not very long but has a fairly high height and is provided immediately after the entrance of the bladeless differential user section 6. It can be seen that the flow approaches a uniformly distributed flow by the time it reaches the entrance of the differential user section.
なお、本発明に係るリブ１５の高さ、すなわち
「デイフユーザ板上の低流れ角度の領域の流体の
流れを案内する程度の高さ」とは羽根なしデイフ
ユーザ入口部の流路幅方向における流れ角の実際
値と平均流れ角が交差する値と同程度の高さであ
る。 Note that the height of the rib 15 according to the present invention, that is, "the height sufficient to guide the flow of fluid in the low flow angle region on the diffuser plate" refers to the flow angle in the width direction of the flow path at the inlet portion of the bladeless diffuser. It is as high as the value where the actual value of and the average flow angle intersect.
第９図には前記第８図に示した具体例のデイフ
ユーザ性能を説明する図で、リブを設けていない
従来の羽根付デイフユーザを備えた遠心圧縮機と
流路幅の21％の高さのリブを側板側壁面に取付け
ている本発明の羽根付デイフユーザを備えた遠心
圧縮機の断熱効率比を示すものである。曲線Ｍが
従来の羽根付デイフユーザを備えたものにおける
各吸込流量時の断熱効率比、曲線Ｎが本発明の羽
根付デイフユーザを備えたものにおける各吸込流
量時の断熱効率比である。基準値は、吸込流量が
設計点のときの従来の羽根付デイフユーザを備え
た遠心圧縮機の断熱効率を1.0としている。本発
明の羽根付デイフユーザを備えた遠心圧縮機にお
いては、羽根なしデイフユーザ部内の圧力回復率
を向上でき、また羽根付デイフユーザ部入口にお
ける流体の羽根への衝突損失などを低減できるの
で、図に示すように、従来の羽根付デイフユーザ
を備えたものに比べて大幅に性能向上を計ること
ができる。このように、大幅な性能向上が得られ
る理由は前述の［作用］の欄で述べたように、羽
根車出口からの歪んだ流れを羽根なしデイフユー
ザ部で一様分布流れに近づけることができるた
め、羽根なしデイフユーザ部では圧力回復率が向
上し、羽根付デイフユーザ部入口では流体の羽根
への衝突損失が低減できるためである。さらに、
本発明ではリブ１５を備えていることにより、羽
根付デイフユーザ部８内では、リブによつて圧力
面から負圧面に向う二次流れが防止されるので、
二次流れ損失も低減できる。 Fig. 9 is a diagram illustrating the differential user performance of the specific example shown in Fig. 8, and shows a centrifugal compressor equipped with a conventional vaned diff user without ribs and a centrifugal compressor with a height of 21% of the channel width. 2 shows the adiabatic efficiency ratio of a centrifugal compressor equipped with a vaned differential user of the present invention in which ribs are attached to the side wall surface of the side plate. Curve M is the adiabatic efficiency ratio at each suction flow rate in a device equipped with a conventional vaned differential user, and curve N is the adiabatic efficiency ratio at each suction flow rate in a device equipped with the vaned diff user of the present invention. The standard value assumes that the adiabatic efficiency of a conventional centrifugal compressor with a vaned differential user when the suction flow rate is at the design point is 1.0. In a centrifugal compressor equipped with a vaned differential user according to the present invention, it is possible to improve the pressure recovery rate in the vaned differential user section, and to reduce collision loss of fluid with the vanes at the inlet of the vaned differential user section, as shown in the figure. As a result, performance can be significantly improved compared to conventional vaned differential users. The reason for this significant performance improvement is that, as mentioned in the [Effect] section above, the distorted flow from the impeller outlet can be made closer to a uniformly distributed flow in the bladeless differential user section. This is because the pressure recovery rate is improved in the vaned differential user section, and the collision loss of the fluid against the vanes can be reduced at the inlet of the vaned differential user section. moreover,
In the present invention, by providing the ribs 15, the ribs prevent secondary flow from the pressure surface toward the negative pressure surface in the vaned diff user section 8.
Secondary flow losses can also be reduced.
なお前記実施例では羽根１ピツチの中間位置に
おいてデイフユーザ板の流路表面上に１枚のリブ
を設けたが、羽根１ピツチ間のリブを複数枚とす
ること等の応用も可能である。また、斜流形流体
機械にも同様に応用することができる。 In the above embodiment, one rib was provided on the channel surface of the diffuser plate at the middle position of one pitch of the blades, but it is also possible to provide a plurality of ribs between each pitch of the blades. Further, it can be similarly applied to a mixed flow type fluid machine.
［発明の効果］
以上述べたように、本発明は、羽根付デイフユ
ーザにおいて、羽根なしデイフユーザ部の入口直
後から、羽根車出口からの歪んだ流れを一様分布
流れに近づけるためのリブを設けたので、羽根な
しデイフユーザ部において羽根車出口からの歪ん
だ流れを一様分布流れに近づけることができ、し
たがつて羽根なしデイフユーザ部での圧力回復率
を向上できると共に、羽根付デイフユーザ部入口
における流体の羽根への衝突損失を低減でき、こ
れによつて大幅な性能向上を計ることのできる羽
根付デイフユーザが得られるという効果がある。[Effects of the Invention] As described above, the present invention provides a bladed differential user with ribs immediately after the entrance of the bladeless differential user section to bring the distorted flow from the impeller outlet closer to a uniformly distributed flow. Therefore, the distorted flow from the impeller outlet in the vaned differential user section can be brought closer to a uniformly distributed flow, and the pressure recovery rate in the vaned differential user section can be improved, and the fluid at the vaned differential user section inlet can be made closer to a uniformly distributed flow. This has the effect of reducing collision loss to the blades, thereby providing a differential user with blades that can significantly improve performance.
第１図は従来の羽根付デイフユーザを説明する
ための遠心形流体機械の縦断面図、第２図は羽根
車出口における流れ角の幅方向分布を示す概略
図、第３図は従来の羽根付デイフユーザの側断面
図、第４図は第３図のＡ−Ａ線矢視図、第５図は
本発明の羽根付デイフユーザの一実施例を説明す
るための遠心形流体機械の縦断面図、第６図はそ
の羽根付デイフユーザの側断面図、第７図は第６
図のＢ−Ｂ線矢視図、第８図及び第９図は本発明
の具体的実施例の効果を説明する図で、第８図は
羽根付デイフユーザ部入口における流れ角の実測
値を示す線図、第９図は第８図に示した具体的実
施例の圧縮機性能を説明する線図である。
１……羽根車、４……側板側のデイフユーザ
板、５……心板側のデイフユーザ板、６……羽根
なしデイフユーザ部、７……羽根、８……羽根付
デイフユーザ部、１５……リブ、ｍ……リブを設
けていない羽根付デイフユーザ部入口の流れ角の
分布を示す曲線、ｎ……リブを設けた羽根付デイ
フユーザ部入口の流れ角の分布を示す曲線。
Fig. 1 is a longitudinal cross-sectional view of a centrifugal fluid machine to explain a conventional vaned differential user, Fig. 2 is a schematic diagram showing the widthwise distribution of the flow angle at the impeller outlet, and Fig. 3 is a conventional vaned diff user. FIG. 4 is a side sectional view of a differential user, FIG. 4 is a view taken along the line A-A in FIG. Figure 6 is a side sectional view of the differential user with wings, and Figure 7 is a side sectional view of the differential user with blades.
The B-B line arrow view, FIGS. 8 and 9 are diagrams for explaining the effects of specific embodiments of the present invention, and FIG. 8 shows the actual measured value of the flow angle at the entrance of the vaned differential user section. 9 is a diagram illustrating the compressor performance of the specific embodiment shown in FIG. 8. 1... Impeller, 4... Diff user plate on the side plate side, 5... Diff user plate on the core plate side, 6... Diff user part without blades, 7... Vane, 8... Diff user part with blades, 15... Rib , m...Curve showing the flow angle distribution at the inlet of the vaned differential user section without ribs, n...Curve showing the flow angle distribution at the inlet of the winged differential user section provided with ribs.
Claims (1)
対のデイフユーザ板と、その流路の入口付近に形
成された羽根なしデイフユーザ部と、この羽根な
しデイフユーザ部の下流側に形成され羽根を円形
翼列状に配列して成る羽根付デイフユーザとを備
える流体機械のデイフユーザにおいて、前記羽根
間の少なくとも側板側のデイフユーザ板の流路表
面上に、デイフユーザ板上の壁面付近の低流れ角
度部分の流れを案内するリブを設け、このリブは
羽根の前縁よりも上流側に形成された前記羽根な
しデイフユーザ部の入口直後まで延長して設け、
そのリブの前縁部における入口角を羽根の入口角
よりも小さく形成し、羽根の出入口間におけるリ
ブのそりは羽根と同一のそりとなるように構成し
たことを特徴とする羽根付デイフユーザ。1 A pair of diffuser plates provided downstream of the impeller to form a flow path, a bladeless diffuser section formed near the entrance of the flow path, and a bladeless diffuser plate formed downstream of the bladeless diffuser section to form a circular blade. In a differential user of a fluid machine including a differential user with blades arranged in a row of blades, a flow in a low flow angle portion near a wall surface on the differential user plate is formed on the flow path surface of the diffuser plate at least on the side plate side between the blades. A rib is provided for guiding the blade, and the rib is provided to extend to immediately after the entrance of the bladeless differential user portion formed upstream of the leading edge of the blade,
A defuser with vanes, characterized in that the entrance angle at the front edge of the rib is smaller than the entrance angle of the vane, and the rib between the entrances and exits of the vane has the same curvature as the vane.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15811282A JPS5848799A (en) | 1982-09-13 | 1982-09-13 | Diffuser equipped with vane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15811282A JPS5848799A (en) | 1982-09-13 | 1982-09-13 | Diffuser equipped with vane |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5848799A JPS5848799A (en) | 1983-03-22 |
| JPS6261800B2 true JPS6261800B2 (en) | 1987-12-23 |
Family
ID=15664560
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15811282A Granted JPS5848799A (en) | 1982-09-13 | 1982-09-13 | Diffuser equipped with vane |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5848799A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108131329A (en) * | 2018-02-06 | 2018-06-08 | 西安交通大学 | A kind of centrifugal pump using double-deck guide vane blade |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0432560Y2 (en) * | 1984-12-27 | 1992-08-05 | ||
| JPH0710160Y2 (en) * | 1986-05-06 | 1995-03-08 | 株式会社ネリキ | Valve device for extracting ultra-high purity gas from gas storage container |
| JPH0615879B2 (en) * | 1987-09-28 | 1994-03-02 | 株式会社日立製作所 | Diff user of centrifugal fluid machine |
-
1982
- 1982-09-13 JP JP15811282A patent/JPS5848799A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108131329A (en) * | 2018-02-06 | 2018-06-08 | 西安交通大学 | A kind of centrifugal pump using double-deck guide vane blade |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5848799A (en) | 1983-03-22 |
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