WO2011007466A1 - インペラおよび回転機械 - Google Patents
インペラおよび回転機械 Download PDFInfo
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- WO2011007466A1 WO2011007466A1 PCT/JP2010/001050 JP2010001050W WO2011007466A1 WO 2011007466 A1 WO2011007466 A1 WO 2011007466A1 JP 2010001050 W JP2010001050 W JP 2010001050W WO 2011007466 A1 WO2011007466 A1 WO 2011007466A1
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- Prior art keywords
- impeller
- blade
- hub
- inlet
- bulging portion
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- 239000012530 fluid Substances 0.000 claims abstract description 31
- 230000007423 decrease Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
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Classifications
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- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
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- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
- F04D29/286—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors multi-stage rotors
Definitions
- the present invention relates to an impeller and a rotary machine, and particularly relates to a flow path shape thereof.
- Impeller performance needs to be improved. Therefore, in recent years, in order to improve the performance of the impeller, an impeller has been proposed in which a concave portion is provided at the front edge between the blade tip and the hub to effectively suppress the secondary flow and separation (for example, refer to Patent Document 1). .
- a plurality of grooves are formed in the hub surface between the blades so that the boundary layer of the flow along the hub surface does not expand so that the flow along the hub surface.
- FIG. 9 shows the vicinity of the blade leading edge of a conventional impeller.
- the blade angle of the blade 203 on the inlet 206 side is set to the inlet 206 at the design point flow rate. Since the design is such that the angle in the impeller radial direction is greater than the angle at which fluid flows into the inlet (inlet flow angle), the fluid inlet flow angle (hereinafter referred to as the incident angle ⁇ ) with respect to the blade angle becomes large.
- the boundary layer enlarges due to the decrease in the inflow rate, particularly on the hub surface on the suction surface n side of the blade where the flow rate is the smallest in the vicinity of the inlet 206. Therefore, there is a problem that the efficiency is lowered or the vehicle is stalled.
- the present invention has been made in view of the above circumstances, and suppresses reduction in efficiency or stall due to expansion of the boundary layer on the hub surface on the suction surface side of the inlet when the inflow flow rate is reduced. It is an object of the present invention to provide an impeller and a rotating machine that can be used.
- the present invention adopts the following configuration in order to solve the above-described problems and achieve the object.
- the impeller according to the present invention (for example, the impeller 1 in the embodiment) has a flow direction from the axial direction to the radial direction as it goes from the radially inner side to the radially outer side of the fluid channel (for example, the impeller channel 10 in the embodiment).
- An impeller of a rotating machine that gradually changes as follows: a hub surface that forms at least a part of the fluid flow path (for example, the hub surface 4 in the embodiment), and a blade surface that forms at least a part of the fluid flow path Among the corners (for example, the corner 12 in the embodiment) where the pressure surface of the blade surface and the hub surface contact (for example, the corner 12 in the embodiment) (for example, the pressure surface p and the negative pressure surface n in the embodiment).
- the inlet 6 in the embodiment includes a bulging portion (for example, a bulging portion b in the embodiment) that bulges toward the inside of the fluid flow path at a corner near the inlet.
- the blade leading edge on the hub surface side is formed thick by providing the bulging portion at the corner where the hub surface and the pressure surface in the vicinity of the inlet are in contact with each other.
- the radius of the rounded portion due to the bulging portion of the leading edge is increased.
- the flow slowly flows through the rounded portion of the bulging portion of the blade leading edge whose radius is increased. Since it wraps around, the enlargement of the boundary layer on the suction surface side of the leading edge is suppressed, and the development of the boundary layer on the suction surface side of the hub surface can be suppressed.
- the amount of decrease in the throat area can be minimized.
- the strength of the portion where the blade contacts the hub that receives force from the fluid and also generates centrifugal stress due to rotation of the impeller can be increased.
- an increase in the number of parts can be suppressed.
- a corner formed by the suction surface of the blade surface and the hub surface bulges toward the inside of the fluid flow path at a corner near the fluid flow inlet.
- the second bulging portion is provided at the corner formed by the negative pressure surface of the blade and the hub surface. Since the thickness dimension of the blade leading edge on the hub surface side can be further increased, the expansion of the boundary layer due to a decrease in the flow rate can be further suppressed, and the portion of the entrance where the blade and the hub are in contact with each other can be further suppressed. The strength can be further increased.
- the impeller of the rotating machine even when the fluid incident angle is increased with respect to the inlet blade angle when the flow rate is reduced, the inlet leading edge radius is increased by the bulging portion.
- the expansion of the boundary layer generated on the hub surface on the suction surface side can be suppressed and the efficiency can be prevented from decreasing or stalling on the small flow rate side.
- FIG. 1 is a cross-sectional view of a centrifugal compressor according to an embodiment of the present invention.
- FIG. 2 is an enlarged front view showing a main part of the impeller in the embodiment of the present invention.
- FIG. 3 is a cross-sectional view taken along line AA in FIG. 4 is a cross-sectional view taken along line BB in FIG.
- FIG. 5 is an enlarged cross-sectional view of the blade leading edge in the embodiment of the present invention.
- FIG. 6 is a graph showing efficiency characteristics with respect to the flow rate of the impeller in the embodiment of the present invention.
- FIG. 7 is a graph showing the head characteristics with respect to the flow rate of the impeller in the embodiment of the present invention.
- FIG. 8 is a cross-sectional view corresponding to FIG. 4 in another example of the embodiment of the present invention.
- FIG. 9 is a front view of the vicinity of the leading edge of a blade in a conventional impeller.
- the impeller of this embodiment will be described by taking as an example an impeller of a centrifugal compressor that is a rotating machine.
- a centrifugal compressor 100 that is a rotating machine according to the present embodiment mainly includes a shaft 102 that is rotated around an axis O, and a process that uses centrifugal force attached to the shaft 102.
- the impeller 1 that compresses the gas (gas) G
- the casing 105 that supports the shaft 102 rotatably and has a flow path 104 that allows the process gas G to flow from the upstream side to the downstream side are formed.
- the casing 105 is formed so as to form a substantially cylindrical outline, and the shaft 102 is disposed so as to penetrate the center.
- Journal bearings 105a are provided at both ends of the shaft 102 in the axial direction, and thrust bearings 105b are provided at one end.
- the journal bearing 105a and the thrust bearing 105b support the shaft 102 in a rotatable manner. That is, the shaft 102 is supported by the casing 105 via the journal bearing 105a and the thrust bearing 105b.
- a suction port 105c through which the process gas G flows from the outside is provided at one end side in the axial direction of the casing 105, and a discharge port 105d through which the process gas G flows out to the outside is provided at the other end side.
- an internal space that communicates with the suction port 105c and the discharge port 105d, respectively, and repeats the diameter reduction and the diameter expansion is provided.
- This internal space functions as a space for accommodating the impeller 1 and also functions as the flow path 104. That is, the suction port 105 c and the discharge port 105 d communicate with each other via the impeller 1 and the flow path 104.
- a plurality of impellers 1 are arranged at intervals in the axial direction of the shaft 102. In the illustrated example, six impellers 1 are provided, but it is sufficient that at least one impeller 1 is provided.
- the hub 2 to 3 show the impeller 1 of the centrifugal compressor 100, and the impeller 1 includes a hub 2 and a plurality of blades 3.
- the hub 2 is formed in a substantially circular shape when viewed from the front, and is rotatable around the axis about the axis O described above.
- a hub surface 4 is curvedly formed on the hub 2 from a predetermined position S on the radially inner side that is slightly spaced radially outward from the axis O toward the radially outer side.
- the curved hub surface 4 is formed such that a surface positioned radially inward is formed along the axis O and gradually along the radial direction toward the radially outer side.
- the hub 2 has an axial thickness dimension that decreases from one of the axial end faces (upstream side) from the radially inner position S slightly spaced from the axis O toward the radially outer side. The size is larger toward the inner side and smaller toward the outer side.
- the radial direction of the hub 2 is indicated by an arrow.
- the plurality of blades 3 are arranged substantially radially on the hub surface 4 described above, and are erected substantially vertically (normal direction) to the hub surface 4 as shown in FIG. 4. Yes.
- the blade 3 is formed to have a substantially uniform thickness from the hub end h to the tip end t, and in the direction of rotation of the hub 2 (indicated by an arrow in FIG. 2) from the hub end h (see FIG. 3) to the tip end t. It has a curved shape with a slightly convex surface.
- the blade surface on the convex side of the concave blade side and the convex blade surface of the curved blade 3 becomes the pressure surface p, while the blade surface on the concave surface on the back side of the convex surface is negative. It becomes the pressure surface n.
- the tip end t of the blade 3 is curved from the radially inner side to the radially outer side of the hub 2. More specifically, like the hub surface 4 described above, it is formed in a concave shape along the axis O toward the radially inner side and gradually along the radial direction toward the radially outer side.
- the blade 3 is formed such that its height dimension is higher on the inner side in the radial direction of the hub 2 and lower on the outer side in the radial direction with respect to the hub surface 4.
- the tip end t side of the blade 3 is covered with a casing 105 (see FIG. 1), and the shroud surface 5 constituted by the casing 105 and the pressure surface p and negative pressure of the adjacent blade 3 described above.
- the impeller channel 10 of the impeller 1 is configured by the pressure surface n and the hub surface 4 between the pressure surface p and the negative pressure surface n. Then, as the impeller 1 rotates, fluid flows in the axial direction from the inlet 6 of the impeller flow path 10 located on the radially inner side of the hub 2, and from the outlet 7 located on the radially outer side by centrifugal force. The fluid flows outward along the radial direction.
- the impeller channel 10 having the above-described configuration has its flow direction gradually changed from the axial direction to the radial direction from the radially inner side to the radially outer side of the hub 2. Curved formation.
- a bulge b that bulges toward the inside of the impeller channel 10 is formed at the corner 12 near the inlet 6.
- the bulging portion b is formed integrally with the hub surface 4 and the pressure surface p (see FIGS. 2 to 4).
- the front edge 20 of the blade 3 has a substantially semicircular cross section (see FIG. 5), and the bulging portion b is formed on the corner 12 near the inlet 6 in the corner 12 described above, that is, on the front edge 20. It is formed in a corner 12 of a part of the adjacent range.
- the bulging portion b has a maximum width set to about 20% of the width of the impeller flow path 10 and about 20% of the blade height, and is a curved surface convex toward the inside of the impeller flow path 10 and in the vicinity of the inlet 6. It rises smoothly toward the downstream side in the flow direction, and immediately reaches the maximum width and height. And the bulging part b falls gradually from the position where it became the maximum width and the maximum height by a curved surface similar to the rising, and is about 10% of the channel length from the inlet 6 to the outlet 7 of the impeller channel 10. Is smoothly connected to the hub surface 4 and the pressure surface p.
- the thickness dimension of the leading edge 20 of the blade 3 on the hub surface 4 side increases, and the blade leading edge radius of the leading edge 20 is substantially increased as shown in FIG. r1 increases to the blade leading edge radius r2.
- FIG. 6 is a graph showing the efficiency characteristics of a rotating machine using the impeller 1 and a conventional impeller.
- the vertical axis represents the efficiency ⁇ and the horizontal axis represents the flow rate Q.
- the efficiency of the rotary machine provided with the impeller which is not provided with the bulging part b is shown by a solid line
- the efficiency of the rotary machine provided with the impeller 1 provided with the bulge part b is shown by a broken line.
- FIG. 6 it can be seen that the efficiency when the bulging portion b is provided at the same flow rate Q is improved as compared with the case where the bulging portion b is not provided.
- the efficiency on the small flow rate side is greatly improved.
- FIG. 7 is a graph showing the head (work) characteristics of the rotating machine using the impeller 1 and the conventional impeller, where the vertical axis represents the head (work) and the horizontal axis represents the flow rate Q.
- the head of the rotary machine provided with the impeller which is not provided with the bulging part b is shown by a solid line
- the head of the rotary machine provided with the impeller 1 provided with the bulge part b is shown by a broken line.
- the above-described impeller 1 provided with the bulging portion b is more than the surge point (indicated by a solid circle in the drawing) of the rotating machine provided with the impeller not provided with the bulging portion b. It can be seen that the surge point (indicated by a white circle in the figure) of the rotating machine provided is displaced to the lower flow rate side and the surge margin is expanded.
- the characteristics of the impeller 1 are improved as compared with the impeller without the bulging portion b, and the reason that the surge point is displaced to the low flow rate side is that the flow rate is reduced. This is because, when the incident angle of the fluid shown in FIG. 2 is enlarged, the boundary layer becomes difficult to develop on the suction surface n side due to a partial increase in the blade leading edge radius of the inlet 6.
- the surge point is a minimum flow rate necessary for the rotating machine to operate normally without surging.
- the bulging portion b is provided at the corner portion 12 where the hub surface 4 in the vicinity of the inlet 6 and the pressure surface p are in contact with each other. 3 is partially increased, the blade leading edge radius r1 on the hub surface 4 side is substantially increased to the blade leading edge radius r2. The development of the boundary layer can be suppressed.
- the leading edge 20 of the blade 3 on the hub surface 4 side is formed thick by the bulging portion b and the blade leading edge radius r1 substantially increases to the blade leading edge radius r2, the blade angle (see FIG. 2). Even when the angle of incidence of the fluid on the surface increases, the boundary layer develops on the negative pressure surface n side of the hub surface 4 to suppress the decrease in efficiency and prevent stall on the small flow rate side.
- the margin can be expanded.
- the corner portion 12 on the hub surface 4 side that is, the bulging portion b limited to the local area
- the amount of decrease in the throat area on the inlet 6 side of the impeller channel 10 can be minimized.
- a portion of the contact portion between the blade 3 and the hub 2 that receives a force from the fluid and also generates centrifugal stress due to the impeller 1 rotating at a high speed. Strength can be increased.
- the blade 3 and the hub 2 are formed integrally, an increase in the number of parts can be suppressed.
- the bulging portion b is provided in the corner portion 12 located in the vicinity of the inlet 6 of the impeller passage 10 among the corner portions 12 in contact with the pressure surface p and the hub surface 4 .
- a bulging portion b ′ may be provided at the corner 22 where the negative pressure surface n and the hub surface 4 are in contact with each other near the inlet 6 of the impeller flow path 10.
- the impeller of the centrifugal rotary machine has been described as an example.
- the impeller is not limited to this, and may be an impeller of a mixed flow type rotary machine.
- it is not restricted to a compressor, You may apply to impellers, such as an air blower and a turbine.
- a so-called open type impeller in which the opposite side of the hub surface 4 is covered by the shroud surface 5 has been described as an example.
- a closed type including a wall that covers the tip end t side integrally formed with the blade 3 is provided. It may be applied to the impeller.
- the shroud surface 5 of the above-described embodiment may be read as the inner surface of the wall covering the tip end t.
- the fillet R due to the roundness of the tip of the cutting cutter tool is slightly attached to the boundary portion between the hub surface 4 and the blade surface (negative pressure surface n, pressure surface p) other than the bulging portion b as usual.
- the impeller of the rotating machine even when the fluid incident angle is increased with respect to the inlet blade angle when the flow rate is reduced, the inlet leading edge radius is increased by the bulging portion.
- the expansion of the boundary layer generated on the hub surface on the suction surface side can be suppressed, and the efficiency can be prevented from decreasing or stalling on the small flow rate side.
Abstract
Description
本願は、2009年7月13日に日本出願された特願2009-164782に基づいて優先権を主張し、その内容をここに援用する。
また、遠心型や斜流型のインペラの性能向上を図るために、ハブ面に沿う流れの境界層が拡大しないよう羽根間のハブ面に複数本の溝を形成してハブ面に沿う流れに乱れを生じさせるものや、境界層の局部集中を防止するために羽根間に複数の小翼を設けたものがある(例えば、特許文献2,3参照)。
本発明に係るインペラ(例えば、実施形態におけるインペラ1)は、流体流路(例えば、実施形態におけるインペラ流路10)の径方向内側から径方向外側へ向かうに従い流れ方向が軸方向から径方向へと漸次変化する回転機械のインペラであって、前記流体流路の少なくとも一部を構成するハブ面(例えば、実施形態におけるハブ面4)と、前記流体流路の少なくとも一部を構成する羽根面(例えば、実施形態における圧力面p、負圧面n)と、前記羽根面の圧力面と前記ハブ面とが接する隅部(例えば、実施形態における隅部12)のうち、前記流体流路の入口(例えば、実施形態における入口6)近傍の隅部に前記流体流路の内側へ向かって膨出する膨出部(例えば、実施形態における膨出部b)とを備える。
この発明に係る回転機械のインペラによれば、入口近傍のハブ面と圧力面とが接する隅部に膨出部が設けられることでハブ面側の羽根前縁が厚く形成されて実質的に羽根前縁の膨出部による丸み部の半径が増加される。これにより、ハブ面側の流入速度が小さいことにより羽根角度に対する流体の入射角が大きくなった場合であっても、半径が増加された羽根前縁の膨出部による丸み部を流れがゆっくりと回り込むため、前縁負圧面側での境界層の肥大が抑制され、ハブ面の負圧面側で境界層が発達するのを抑制することができる。さらに、ハブ面側の隅部すなわち局所に限定した膨出部が設けられることで、スロート面積の低下量を最小限に抑えることができる。
そして、入口近傍の隅部に膨出部を設けることで、流体から力を受け、かつ、インペラが回転することにより遠心応力も発生する羽根とハブとの接する部分の強度を増加させることができる。さらに、羽根およびハブと一体的に形成した場合には部品点数の増加を抑制することができる。
この場合、羽根の圧力面とハブ面との隅部に配置される膨出部に加えて、羽根の負圧面とハブ面とで形成される隅部に第2膨出部が設けられるので、ハブ面側の羽根前縁の厚さ寸法をさらに拡大することができるため、流量の低下による境界層の拡大をさらに抑制することができ、また入口の隅部における羽根とハブとの接する部分の強度をさらに増加させることができる。
また、ケーシング105の軸方向の一端側にはプロセスガスGを外部から流入させる吸込口105cが設けられ、他端側にはプロセスガスGが外部に流出する排出口105dが設けられている。ケーシング105内には、これら吸込口105c及び排出口105dにそれぞれ連通し、縮径及び拡径を繰り返す内部空間が設けられている。この内部空間は、インペラ1を収容する空間として機能すると共に上記流路104としても機能する。
即ち、吸込口105cと排出口105dとは、インペラ1及び流路104を介して連通している。
ハブ2は、正面視で略円形に形成され、上述した軸線Oを中心として軸周りに回転可能になっている。ハブ2には、図3に示すように、軸線Oから径方向外側にやや離間した径方向内側の所定の位置Sから径方向外側に向かってハブ面4が湾曲形成されている。この湾曲形成されたハブ面4は、径方向内側に位置する面が軸線Oに沿って形成されるとともに、径方向外側に向かうにつれて徐々に径方向に沿うように形成される。つまり、ハブ2は、その軸線Oからやや離間した径方向内側の位置Sから径方向外側に向かうほどその軸方向厚さ寸法が軸方向端面の一方(上流側)から減少し、この軸方向厚さ寸法が内側ほど大きく外側ほど小さくなる。なお、図3において、ハブ2の径方向を矢印で示している。
そして、羽根3は、ハブ面4を基準にするとその高さ寸法が、ハブ2の径方向内側ほど高く、径方向外側ほど低く形成される。
図6に示すように、同一の流量Qで膨出部bを設けた場合の方が膨出部bを設けない場合と比較して効率が向上していることが分かる。特に、小流量側での効率が大きく向上していることが分かる。
図7に示すように、膨出部bを設けていないインペラを備える回転機械のサージ点(図中、塗りつぶしの丸で示す。)よりも、膨出部bを設けている上述のインペラ1を備える回転機械のサージ点(図中、白抜きの丸で示す。)の方が、より低流量側に変位してそのサージ余裕が拡大したことが分かる。
また、入口6近傍の隅部12に膨出部bを設けることで、流体から力を受け、かつ、インペラ1が高速回転することによって遠心応力も発生する羽根3とハブ2との接する部分の強度を増加させることができる。さらに、羽根3およびハブ2と一体的に形成した場合には部品点数の増加を抑制することができる。
また、上述した実施形態の膨出部bの形状および位置は一例であって、これに限られるものではない。
4 ハブ面
6 入口
7 出口
10 インペラ流路(流体流路)
12 隅部
22 隅部
100 遠心圧縮機
p 圧力面(羽根面)
n 負圧面(羽根面)
b 膨出部
b’ 膨出部(第2膨出部)
Claims (3)
- 流体流路の径方向内側から径方向外側へ向かうに従い流れ方向が軸方向から径方向へと変化する回転機械のインペラであって、
前記流体流路の少なくとも一部を構成するハブ面と、
前記流体流路の少なくとも一部を構成する羽根面と、
前記羽根面を構成する圧力面と前記ハブ面とが接する隅部のうち前記流体流路の入口近傍の隅部に前記流体流路の内側へ向かって膨出する膨出部とを備えるインペラ。 - 前記羽根の負圧面と前記ハブ面とで形成される隅部のうち前記流体流の入口近傍の隅部に前記流体流路の内側へ向かって膨出する第2膨出部をさらに備える請求項1に記載のインペラ。
- 請求項1又は2に記載のインペラを備える回転機械。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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CN201080015580.1A CN102365464B (zh) | 2009-07-13 | 2010-02-18 | 叶轮和旋转机械 |
EP10799530.0A EP2410186B1 (en) | 2009-07-13 | 2010-02-18 | Impeller and rotary machine |
US13/262,929 US9404506B2 (en) | 2009-07-13 | 2010-02-18 | Impeller and rotary machine |
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Application Number | Priority Date | Filing Date | Title |
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JP2009-164782 | 2009-07-13 | ||
JP2009164782A JP2011021492A (ja) | 2009-07-13 | 2009-07-13 | インペラおよび回転機械 |
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WO2011007466A1 true WO2011007466A1 (ja) | 2011-01-20 |
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PCT/JP2010/001050 WO2011007466A1 (ja) | 2009-07-13 | 2010-02-18 | インペラおよび回転機械 |
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US (1) | US9404506B2 (ja) |
EP (1) | EP2410186B1 (ja) |
JP (1) | JP2011021492A (ja) |
CN (1) | CN102365464B (ja) |
WO (1) | WO2011007466A1 (ja) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
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ITCO20130024A1 (it) * | 2013-06-13 | 2014-12-14 | Nuovo Pignone Srl | Giranti di compressore |
ITCO20130037A1 (it) * | 2013-09-12 | 2015-03-13 | Internat Consortium For Advanc Ed Design | Girante resistente al liquido per compressori centrifughi/liquid tolerant impeller for centrifugal compressors |
DE102015214854A1 (de) * | 2015-08-04 | 2017-02-09 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Verdichterrad für einen Abgasturbolader |
FI3440360T3 (fi) | 2016-04-06 | 2023-09-26 | Smidth As F L | Alhaisen tulopyörrevoimakkuuden juoksupyörä, jolla on parannellut hydrodynaamiset kulumisominaisuudet |
CN105822589B (zh) * | 2016-04-29 | 2019-04-23 | 合肥中科根云设备管理有限公司 | 一种工作效率高的离心泵叶轮 |
KR102634097B1 (ko) * | 2017-01-06 | 2024-02-05 | 한화파워시스템 주식회사 | 와류 발생 장치를 구비한 임펠러 |
FR3077803B1 (fr) | 2018-02-15 | 2020-07-31 | Airbus Helicopters | Methode d'amelioration d'une pale afin d'augmenter son incidence negative de decrochage |
FR3077802B1 (fr) * | 2018-02-15 | 2020-09-11 | Airbus Helicopters | Methode de determination d'un cercle initial de bord d'attaque des profils aerodynamiques d'une pale et d'amelioration de la pale afin d'augmenter son incidence negative de decrochage |
US10962021B2 (en) * | 2018-08-17 | 2021-03-30 | Rolls-Royce Corporation | Non-axisymmetric impeller hub flowpath |
JP7438240B2 (ja) * | 2019-12-09 | 2024-02-26 | 三菱重工エンジン&ターボチャージャ株式会社 | 遠心圧縮機の羽根車、遠心圧縮機及びターボチャージャ |
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- 2010-02-18 EP EP10799530.0A patent/EP2410186B1/en not_active Not-in-force
- 2010-02-18 US US13/262,929 patent/US9404506B2/en not_active Expired - Fee Related
- 2010-02-18 CN CN201080015580.1A patent/CN102365464B/zh not_active Expired - Fee Related
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Also Published As
Publication number | Publication date |
---|---|
US20120027599A1 (en) | 2012-02-02 |
US9404506B2 (en) | 2016-08-02 |
CN102365464B (zh) | 2014-10-29 |
CN102365464A (zh) | 2012-02-29 |
EP2410186B1 (en) | 2017-07-05 |
EP2410186A1 (en) | 2012-01-25 |
EP2410186A4 (en) | 2015-05-06 |
JP2011021492A (ja) | 2011-02-03 |
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