WO2011043125A1 - 遠心圧縮機のインペラ - Google Patents
遠心圧縮機のインペラ Download PDFInfo
- Publication number
- WO2011043125A1 WO2011043125A1 PCT/JP2010/063581 JP2010063581W WO2011043125A1 WO 2011043125 A1 WO2011043125 A1 WO 2011043125A1 JP 2010063581 W JP2010063581 W JP 2010063581W WO 2011043125 A1 WO2011043125 A1 WO 2011043125A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- blade
- full
- splitter
- hub surface
- surface side
- Prior art date
Links
- 239000012530 fluid Substances 0.000 claims abstract description 41
- 230000000694 effects Effects 0.000 description 8
- 230000002452 interceptive effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000001629 suppression Effects 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000002542 deteriorative effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
Images
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
- F04D29/26—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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
-
- 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
-
- 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
Definitions
- the present invention relates to an impeller (impeller) of a centrifugal compressor used for vehicles, marine turbochargers, and the like, and in particular, a splitter blade (short blade) provided between adjacent full blades (all blades). And the shape of the wing at the inlet of the fluid.
- Centrifugal compressors used in compressors for vehicular and marine turbochargers give kinetic energy to the fluid through the rotation of the impeller and discharge the fluid radially outward to increase the pressure due to centrifugal force It is. Since this centrifugal compressor is required to have a high pressure ratio and high efficiency in a wide operating range, a splitter blade (short blade) 03 is provided between adjacent full blades (all blades) 01 as shown in FIG.
- the impeller 05 is often used, and various contrivances have been made for its wing shape.
- the full blade 01 and the splitter blade 03 are alternately installed on the surface of the hub 07 as shown in FIGS.
- the general splitter blade 03 has a shape obtained by simply cutting away the upstream side of the full blade 01.
- the inlet end of the splitter blade 03 is located downstream from the inlet edge (LE1) of the full blade 01 by a certain distance.
- the edge (LE2) is located, the outlet end edge (TE) is provided to coincide, and the leading edge blade angle ⁇ of the splitter blade 03 (shown as an angle between the direction of the leading edge and the axial direction G of the impeller 05) is
- the flow direction F of the fluid flowing through the flow path between the full blades 01 is set to be the same.
- Patent Document 1 Japanese Patent Application Laid-Open No. 10-213094
- Patent Document 2 Japanese Patent No. 3876195
- the flow velocity is different on both sides of the splitter blade 09, that is, on the pressure surface side and the suction surface side of the full blade 01
- the fluid that has entered between the full blades 01 gathers mainly on the suction surface side. Therefore, even if the cross-sectional area of the passages on both sides of the splitter blade 09 is geometrically equal, the flow rate increases on the negative pressure surface side compared to the pressure surface side, and the flow rate increases. There is a problem that uniformity occurs, the fluid cannot be evenly distributed, the blade load becomes uneven, the flow path loss increases, and the improvement of the impeller efficiency is hindered.
- Patent Document 3 Japanese Patent Laid-Open No. 2002-332992
- Japanese Patent Laid-Open No. 2002-332992 Japanese Patent Laid-Open No. 2002-332992
- the leading edge blade angle of the splitter blade 011 remains ⁇ , and the leading edge is deliberately biased toward the suction surface side of the full blade 01 so that A1> A2.
- the flow rate in both side passages of the splitter blade 011 is made uniform.
- the present invention has been made in view of these problems, and a full blade provided adjacent to each other from the inlet portion to the outlet portion of the fluid, and a splitter provided from the middle of the flow path to the outlet portion between the full blades.
- the inlet shape of the splitter blade that achieves uniform flow distribution, high pressure ratio, and high efficiency is achieved by adapting to the complicated internal flow of the centrifugal compressor The issue is to provide.
- the first invention of the present application is formed between a plurality of full blades provided on the hub surface from the inlet portion to the outlet portion of the fluid and the full blades provided adjacent to each other.
- the leading edge blade angle at the inlet end portion of the splitter blade is varied in the height direction from the hub surface, and the tip The portion is inclined toward the suction surface side of the full blade with a larger inclination angle than the other portions.
- the leading blade angle at the inlet end of the splitter blade is made different in the height direction from the hub surface, and the front end portion in the height direction is inclined at a larger inclination angle than the other portions.
- the first point is adaptation to the tip leakage flow.
- the fluid inlet of the full blade A blade tip leakage flow W is generated in which the fluid on the pressure surface side of the full blade of the adjacent fluid passage leaks to the suction surface side of the full blade through the gap portion B between the tip portion of the blade at the end and the casing.
- This leakage flow is accompanied by a strong vortex flow (blade tip leakage vortex), and there is a problem that the flow does not flow along the full blade but a drift M occurs in the vicinity of the tip of the inlet end of the splitter blade.
- the tip end portion P in the height direction from the hub surface at the inlet end portion of the splitter blade is inclined toward the suction surface side Sb of the full blade, whereby the tip end of the inlet end portion of the splitter blade.
- the drift M caused by the blade tip leakage vortex generated in the vicinity of the portion can be shaped along the drift, and the drift can be smoothly guided to the outlet side, and the high pressure ratio and High efficiency can be achieved.
- the second point is to avoid interference with the tip leakage vortex.
- the tip leakage vortex is an area of low energy fluid accumulation, and if such vortex flow interferes with the tip of the splitter blade inlet end toward the tip end of the splitter blade, separation or further vortex structure As a result, the loss generation of the flow is increased and the efficiency is lowered.
- the tip end portion of the inlet end portion of the splitter blade is preferably 70% or more in the height direction.
- the third point is suppression of surging by changing the reverse pressure gradient.
- the low energy fluid tends to accumulate on the blade tip side, that is, on the tip side in the height direction from the hub surface.
- this low energy fluid easily flows back by the reverse pressure gradient in the impeller, that is, the pressure gradient from the fluid outlet side to the inlet side (pressure gradient from high pressure on the outlet side to low pressure on the inlet side). It was a factor that led to surging.
- the tip end portion in the height direction from the hub surface is inclined toward the suction surface side of the full blade at the inlet end portion of the splitter blade.
- the direction of the pressure gradient is directed in the circumferential direction Y rather than the direction X in the normal case (when the front blade angle of the splitter blade is the same as that of the full blade), and the tip side in the height direction from the hub surface, that is, the casing Backflow in the vicinity of the surface is suppressed, surging that is likely to occur due to a pressure gradient from the outlet side to the inlet side can be prevented, and the compressor can be widened.
- the tip portion in the height direction is approximately 70% or more of the total height, and the inclination angle is gradually increased to a certain angle toward the tip starting from the position of the approximately 70%. Good.
- the position of about 70% is set based on the result of the flow state generated at the inlet end of the splitter blade based on the numerical analysis of the drift due to the blade tip leakage vortex, and the effect of the blade tip leakage vortex is effectively reduced. Can be reduced.
- a plurality of full blades provided on the hub surface from the inlet portion to the outlet portion of the fluid, and an outlet from the middle of the flow path formed between the full blades provided adjacent to each other.
- the leading edge blade angle at the inlet end of the splitter blade is varied in the height direction from the hub surface, and the hub surface side portion is the other portion.
- the full blade is inclined toward the pressure surface side with a larger inclination angle.
- the low energy fluid in the boundary layer formed in the vicinity of the hub surface loses the pressure gradient between the full blades, and as shown in the flow line of the numerical analysis result of FIG. A secondary flow Z from the pressure surface side Sa toward the suction surface side Sb is formed.
- the hub surface side portion Q in the height direction from the hub surface at the inlet end of the splitter blade is inclined toward the pressure surface side of the full blade so as to be adapted to the secondary flow Z, thereby being formed near the hub surface.
- the fluid can be smoothly guided to the outlet side with respect to the secondary flow Z, and a high pressure ratio and high efficiency can be achieved.
- the hub surface side portion is approximately 70% or less of the total height, and the inclination angle is gradually increased to a certain angle toward the hub surface starting from the position of the approximately 70%. Good.
- the position of about 70% is set based on the result of the flow state generated at the inlet end of the splitter blade based on the drift due to the blade tip leakage vortex and the numerical analysis of the secondary flow near the hub surface. It can effectively adapt to the secondary flow near the surface.
- a plurality of full blades provided on the hub surface from the fluid inlet portion to the outlet portion, and an outlet from the middle of the flow path formed between the full blades provided adjacent to each other.
- the leading edge blade angle at the inlet end of the splitter blade is varied in the height direction from the hub surface, and the height direction from the hub surface.
- the upper end portion of the blade is inclined toward the suction surface side of the full blade, and the hub surface side portion in the height direction is inclined toward the pressure surface side of the full blade.
- the effects of the first aspect of the invention and the action of the second aspect of the invention are obtained, and in addition, the flow distribution of each passage in the full blade divided by the splitter blade is made uniform.
- the throat width of the flow path divided by the splitter blade is biased and causes uneven flow, but the flow from the hub surface is high.
- the upper end portion in the height direction and the hub surface side may be divided by an upper portion and a lower portion from about 70% of the total height from the hub surface.
- the leading edge blade angle at the inlet end of the splitter blade is made different in the height direction from the hub surface, and the tip portion is inclined to the suction surface side of the full blade with a larger inclination angle than the other portions. Since it is inclined, it is possible to make the shape suitable for the blade tip leakage flow, smoothly guide the drift to the outlet side, avoid interference with the blade tip leakage vortex, and achieve a high pressure ratio and high efficiency .
- the direction of the reverse pressure gradient from the outlet side to the inlet side in the flow path is directed to the circumferential direction Y rather than the normal direction X, and the height from the hub surface is increased. Back flow near the tip side in the direction, that is, near the casing surface is suppressed, and surging that is likely to occur due to a pressure gradient from the outlet side to the inlet side can be prevented, and the compressor can be widened.
- the front blade angle at the inlet end of the splitter blade is varied in the height direction from the hub surface, and the hub surface side portion is inclined with a larger inclination angle than the other portions. Therefore, the secondary flow formed near the hub surface can be smoothly guided to the outlet side. It is possible to increase the pressure ratio and efficiency.
- the leading edge blade angle at the inlet end of the splitter blade is varied in the height direction from the hub surface, and the upper end portion in the height direction from the hub surface is Since the hub surface side portion in the height direction is inclined toward the pressure surface side of the full blade, the respective passages on both sides divided by the splitter blade are added in addition to the effects of the first and second inventions.
- the flow distribution can be made uniform.
- the shape of the inlet portion of the splitter blade that achieves a high pressure ratio, high efficiency, and uniform flow distribution can be provided by adapting to the complicated internal flow of the centrifugal compressor. it can.
- FIG. 1 It is a perspective view which shows the principal part of the impeller of the centrifugal compressor provided with the splitter blade of this invention. It is a section explanatory view showing the relation between the full blade and splitter blade of a 1st embodiment. It is explanatory drawing which shows the change of the pressure gradient in 1st Embodiment. It is sectional explanatory drawing which shows the relationship between the full blade and splitter blade of 2nd Embodiment. It is a numerical analysis result which shows the wing tip leakage flow from the full blade tip formed at the tip of the inlet end of the splitter blade. It is a numerical analysis result which shows the secondary flow formed in the hub surface vicinity of the inlet end part of a splitter blade.
- FIG. 1 is a perspective view showing a main part of an impeller of a centrifugal compressor to which a splitter blade of the present invention is applied.
- the impeller 1 includes a plurality of adjacent full blades (all blades) 5 on a top surface of a hub 3 fitted to a rotor shaft (not shown), and splitter blades (short blades) 7 provided between the full blades 5. , Are alternately erected at an equal pitch in the circumferential direction.
- the splitter blade 7 is shorter than the full blade 5 in the fluid flow direction, and is provided from the middle of the flow path 9 formed between the full blades 5 and 5 to the outlet portion.
- FIG. 2 shows the relationship between the splitter blade 7 and the full blade 5 in a sectional shape along the longitudinal direction of the blade (corresponding to a sectional view taken along line AA in FIG. 10).
- the shape here indicates the relationship in the radially outer position, that is, the casing side position.
- the impeller 1 shall rotate in the arrow direction.
- the leading edge 7a that is the inlet side end of the splitter blade 7 is located downstream of the leading edge 5a of the inlet side end of the full blade 5 in the flow direction, and the trailing edge 7b that is the outlet side edge of the splitter blade 7. And the position of the trailing edge 5b of the outlet side edge of the full blade 5 is coincident. Further, the flow path 9 formed between the pressure surface side Sa of the full blade 5 and the suction surface side Sb of the full blade 5 is divided into two by the splitter blade 7, and the pressure surface side Sa of the splitter blade 7 and the full blade 5 is divided.
- the pressure surface side flow path 11 is formed between the negative pressure surface side flow path 11 and the negative pressure surface side flow path 13 between the negative pressure surface side Sb and the wall surface.
- the impeller 1 configured as described above is configured as an open impeller having a blade tip clearance between a full blade 5 and a casing (not shown) that covers the splitter blade 7. Therefore, the blade end leakage flow W in which the fluid on the pressure surface side of the full blade 5 in the adjacent fluid passage leaks to the suction surface side of the full blade 5 through the gap portion between the inlet end portion of the full blade 5 and the casing. Occurs.
- Blade tip leakage flow W affects the flow at the inlet end of the splitter blade 7
- the state of this blade tip leakage flow W was numerically analyzed.
- a flow diagram of the numerical analysis results is shown in FIG.
- Blade tip leakage flows through the gap B at the tip of the leading edge 5a of the full blade 5.
- the blade tip leakage flow W is accompanied by a strong vortex flow (blade tip leakage vortex) as shown in FIG. 5, and has a strong blocking action against the flow along the full blade 5. In the vicinity of the front end portion, the flow does not flow along the full blade 5, and there is a problem that a drift M occurs toward the inlet end portion of the splitter blade 7 using the vortex as a nucleus.
- the inflow angle of the fluid flowing in the flow path 9 at the leading edge 7a portion of the splitter blade 7 is obtained by numerical analysis, and the result is shown in FIG. It shows with.
- the horizontal axis indicates the leading edge blade angle ⁇ of the splitter blade and the inflow angle (white circle) of the numerical analysis result, and the vertical axis indicates the height (span) from the hub surface.
- a straight line H ⁇ b> 1 in FIG. 7 is a case where the leading edge blade angle ⁇ of the splitter blade 7 is the same as the flow direction F of the fluid flowing through the flow path 9 between the full blades 5 or the same as the inclination of the full blade 5. In the center of the height direction, it approximates the numerical analysis result, but in the range of approximately 70% or more, the numerical analysis result indicated by the white circles changes to the left and right (the inflow angle becomes large and small). Change). This is due to the effect of the vortex motion of the blade tip leakage flow, and due to the influence of the drift due to the blade tip leakage flow, the flow angle is biased toward the side where the average becomes larger than the straight line H1 in the vicinity of the blade tip. Yes.
- This range of about 70% or more depends on the range of the tip of the splitter blade 7 that the blade tip leakage flow W affects, and therefore changes depending on the positional relationship of the arrangement of the splitter blade 7 with respect to the full blade 5.
- the positional relationship with the full blade 5 is substantially constant (if the splitter blade 7 is too short with respect to the full blade 5, Therefore, even if other open type impellers are analyzed, it can be said that it is effective to incline in a range of approximately 70% or more.
- the leading edge blade angle ⁇ is gradually changed from the approximately 70% position of the span to the straight line H1 so as to follow the variation tendency of the analysis point. From the above relationship, ⁇ + ⁇ (h) is set so that ⁇ (h) changes according to the span height, and the tip of the splitter blade 7 is inclined at about 15 ° or more from the R point in FIG.
- the curve H2 is set as a characteristic of the leading edge blade angle ⁇ of the splitter blade 7.
- FIG. 8 shows the distribution of the blade angle ⁇ at a predetermined position in the cord direction of the splitter blade 7 and the full blade 5, that is, in the longitudinal direction of the blade.
- the vertical axis indicates the blade angle ⁇
- the horizontal axis indicates the total length of the blade, and each position is normalized.
- the zero point of the horizontal axis indicates the inlet side end of the full blade 5.
- the position of the leading edge 5a is shown.
- the line L1 in FIG. 8 indicates the upper end shape of the splitter blade 7, and the line L2 indicates the shape on the hub surface of the splitter blade 7. Therefore, the upper end portion of the splitter blade 7 is inclined to the plus side by 15 ° or more compared to the case of having the same shape as that of the conventional full blade 5, and is inclined to the minus side by 15 ° or more on the hub surface side. After that, the distribution of the blade angle ⁇ does not change suddenly so as to converge toward the conventional shape toward the outlet, and the shape (inclination) of the full blade 5 is reduced on the outlet side of the splitter blade 7. At the same time, the trailing edge 7b at the outlet side edge is set so that both the full blade 5 and the splitter blade 7 are in the same position.
- the first point is the compatibility with the tip leakage flow W.
- the drift M caused by the blade tip leakage vortex generated in the vicinity of the tip of the inlet end of the splitter blade 7 can be shaped along the drift M, thereby smoothly guiding the drift M to the outlet side. It is possible to increase the pressure ratio and efficiency.
- the second point is to avoid interference with the tip leakage vortex. Since the blade tip leakage vortex can be prevented from interfering with the tip end portion of the inlet end of the splitter blade 7, it is possible to prevent the impeller from deteriorating due to interference and the impediment efficiency from being lowered due to the generation of a further vortex flow. Can be
- the third point is suppression of surging by changing the reverse pressure gradient.
- the low energy fluid tends to accumulate on the blade tip side, that is, on the tip side in the height direction from the hub surface.
- This low-energy fluid is easily backflowed and surging by a reverse pressure gradient in the impeller, that is, a pressure gradient from the outlet side to the inlet side of the fluid (pressure gradient from the high pressure on the outlet side to the low pressure on the inlet side).
- a reverse pressure gradient in the impeller that is, a pressure gradient from the outlet side to the inlet side of the fluid (pressure gradient from the high pressure on the outlet side to the low pressure on the inlet side).
- the inlet end portion of the splitter blade 7 is inclined toward the suction surface side of the full blade, with the tip portion in the height direction from the hub surface approached.
- the direction of the reverse pressure gradient in the flow path is directed to the circumferential direction Y rather than the direction X in the normal case (when the front blade angle of the splitter blade is the same as the fluid flow direction or the same as the full blade), Backflow at the tip end in the height direction from the hub surface, that is, near the casing surface, is suppressed, and surging that tends to occur due to a pressure gradient from the outlet side to the inlet side is prevented. Di reduction can be achieved.
- the flow between the full blades 5 and 5 forms a secondary flow Z from the pressure surface side Sa to the suction surface side Sb.
- the region of the hub surface side portion Q in the height direction from the hub surface at the inlet end of the splitter blade 7 is inclined to the pressure surface side Sa of the full blade 5 so as to be adapted to the secondary flow Z.
- the fluid is smoothly guided to the outlet side with respect to the secondary flow Z formed in the vicinity of the hub surface.
- the fluid flow in the vicinity of the hub surface of the splitter blade 7 smoothly moves toward the outlet without being blocked by the splitter blade 7, and a high pressure ratio and high efficiency can be achieved.
- the leading edge blade angle ⁇ is gradually changed from the position of approximately 70% of the span to the straight line H1 within the range of approximately 70% or less of the span. It is shown that the influence of the secondary flow is generated because a tendency to decrease toward the minus side appears from the relationship.
- the leading edge blade angle ⁇ is gradually increased from approximately 70% of the span to a straight line so that the leading edge blade angle ⁇ of the splitter blade 7 follows the numerical analysis result. It is set to ⁇ (h) that is decreased from H1, and ⁇ (h) is set to change according to the height of the span, and is approximately ⁇ 15 from the point S in FIG. It has been found that it is preferable to incline at least, and the curved solid line H2 is set as the characteristic of the leading edge blade angle ⁇ of the splitter blade 7.
- the fluid can be smoothly guided to the outlet side with respect to the secondary flow Z formed in the vicinity of the hub surface, which leads to high pressure ratio and high efficiency. Can do. Further, since the inclination angle is gradually increased to an inclination angle of ⁇ 15 ° or more when the span is approximately 70% or less, it is possible to prevent the occurrence of peeling due to sudden change.
- the third embodiment includes both the first and second embodiments with respect to the leading edge portion of the inlet end of the splitter blade 7 and the leading edge blade angle ⁇ on the hub surface side.
- the leading edge blade angle ⁇ is gradually changed from approximately 70% of the span to the suction surface of the full blade 5.
- the tip end position of the splitter blade 7 is inclined approximately 15 ° or more than the R point position in FIG.
- This point R is a point indicating the upper end of a straight line H1 indicating a relationship having the same leading edge blade angle ⁇ as the flow direction F of the fluid flowing through the flow path 9 between the full blades 5 or the same as the full blades. Inclined by about 15 ° or more with respect to the position.
- the leading edge blade angle ⁇ is gradually inclined toward the pressure surface side Sa of the full blade 5, and on the hub surface of the splitter blade 7, S in FIG. It is inclined by about 15 ° or more from the point position.
- This S point is the S point at the lower end of the straight line H1, and is inclined by about 15 ° or more with this position as a reference. That is, the first embodiment and the second embodiment have a shape having both the characteristics of the leading edge blade angle of the splitter blade 7 inclined in opposite directions.
- the flow distribution of the passages 11 and 13 divided by the splitter blade 7 is obtained in addition to the operational effects of the first embodiment and the operational effects of the second embodiment. Can be made uniform.
- the tip portion in the height direction from the hub surface is inclined toward the suction surface side Sb of the full blade 5, and further, the hub surface side portion in the height direction from the hub surface.
- the throat width of the pressure surface side channel 11 and the suction surface side channel 13 divided by the splitter blade 7 is biased, although this causes non-uniform flow rates, by tilting the tip side and hub surface side in the height direction from the hub surface in opposite directions, these flow rate deviations are canceled and the flow rate distribution is made uniform. be able to.
- the present invention relates to an impeller of a centrifugal compressor comprising a full blade provided adjacent to each other from the fluid inlet to the outlet, and a splitter blade provided between the full blade from the middle of the flow path to the outlet.
- a single splitter blade is provided in the flow path between the full blades.
- the present invention is applied to a double splitter blade that is provided in the flow path between the single splitter blades and is shorter than the single splitter blade. Of course it is good.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
この一般的なスプリッタブレード03の場合は、図11(図10のA-A線断面図)のように、フルブレード01の入口端縁(LE1)より一定距離下流側にスプリッタブレード03の入口端縁(LE2)が位置され、出口端縁(TE)は一致して設けられ、スプリッタブレード03の前縁翼角θ(前縁の方向とインペラ05の軸方向Gとの成す角度として示す)は、フルブレード01間の流路を流れる流体の流れ方向Fと同一に設定されている。
また、スプリッタブレードの入口端部を、フルブレードの負圧面側に傾けたものとして特許文献2(特許3876195号公報)も知られている。
また、遠心圧縮機は複雑な三次元幾何形状を有することから、コリオリ力や遠心力や、流線曲率に起因した強い二次流れを生じ、特に、翼間隙間を有するオープン型インペラの場合には、翼端漏れ流れや、ケーシング面とインペラの相対運動による影響が現われ、流れ場は一層複雑になる。
従って、これらの複雑な内部流動に適合しない従来型の翼形状では、流量および翼負荷の不均一を想定通りに解消することができず、結果として十分なインペラ性能が得られていなかった。
すなわち、スプリッタブレードの入口端部について、ハブ面からの高さ方向の先端部分をフルブレードの負圧面側に傾斜させて寄せ、さらに、ハブ面からの高さ方向のハブ面側部分をフルブレードの圧力面側に傾斜させて寄せるため、それぞれ単独の場合には、スプリッタブレードで分割される流路のスロート幅に偏りが生じ、流量の不均一を生じる原因となるが、ハブ面からの高さ方向において先端側とハブ面側とを同時に実施することでこれら流量の偏りがキャンセルされて流量配分を均一化できる。
なお、高さ方向の前記上端部分と前記ハブ面側とはハブ面からの全高の略70%より上部と下部によって区分するとよい。
さらに、流路内の出口側から入口側への逆圧力勾配の方向が、図3に示すように、通常の場合の方向Xよりも周方向Yに向くことになり、ハブ面からの高さ方向における先端側、つまりケーシング面近傍での逆流が抑制され、出口側から入口側に向かう圧力勾配によって生じやすいサージングを防止して、圧縮機をワイドレンジ化できる。
図1は本発明のスプリッタブレードが適用される遠心圧縮機のインペラの要部を示す斜視図である。インペラ1は、図示しないローター軸に嵌着されたハブ3の上面に複数の互いに隣り合うフルブレード(全翼)5と、そのフルブレード5の間に設けられるスプリッタブレード(短翼)7とが、周方向に等ピッチで交互に立設されている。そして、スプリッタブレード7は、フルブレード5よりも流体の流れ方向に対して長さが短く、フルブレード5、5の間に形成される流路9の途中から出口部にかけて設けられている。
また、フルブレード5の圧力面側Saとフルブレード5の負圧面側Sbとの間に形成される流路9をスプリッタブレード7によって二分割され、スプリッタブレード7とフルブレード5の圧力面側Saの壁面との間に圧力面側流路11が形成され、負圧面側Sbの壁面との間に負圧面側流路13が形成されている。
この図8は、縦軸に翼角βをとり、横軸にブレードの全長を1として各位置を正規化した位置として示し、該横軸のゼロ点が、フルブレード5の入口側端部のリーディングエッジ5aの位置を示す。
この低エネルギー流体は、インペラ内の逆圧力勾配、つまり、流体の出口側から入口側に向かう圧力勾配(出口側の高圧力から入口側の低圧力への圧力勾配)によって容易に逆流してサージングに至る要因となっていたが、図3に示すように、スプリッタブレード7の入口端部について、ハブ面からの高さ方向の先端部分を、フルブレードの負圧面側に傾斜させて寄せたため、流路内の逆圧力勾配の方向が、通常の場合(スプリッタブレードの前端翼角が流体の流れ方向と同じ、またはフルブレードと同じ場合)の方向Xよりも周方向Yに向くことになり、ハブ面からの高さ方向における先端側、つまりケーシング面近傍での逆流が抑制され、出口側から入口側に向かう圧力勾配によって生じやすいサージングを防止して、圧縮機のワイドレンジ化を達成できる。
次に、スプリッタブレード7の入口端部のハブ面側における前縁翼角θについて説明する。
図4には、スプリッタブレード7とフルブレード5との関係を、ブレードの長手方向に沿った断面形状を示す(図10のA-A線断面図に相当)。ここでの形状はハブ3側位置における関係を示す。また、インペラ1は矢印方向に回転するものとする。
ハブ3の近傍の流体は境界層内の低エネルギー流体を形成するため、フルブレード5、5間の流路9内では、圧力勾配負けて、フルブレード5の圧力面側Saから負圧面側Sbと向かう二次流れZが形成される。
これによって、スプリッタブレード7のハブ面近傍における流体の流れが、スプリッタブレード7によって妨げられることなくスムーズに出口に向かい、高圧力比および高効率化が達成できる。
また、スパンが略70%以下で、-15°以上の傾斜角へと徐々に傾斜角度を増加させるため、急変による剥離の発生を防止できる。
第3実施形態は、スプリッタブレード7の入口端部の先端部分およびハブ面側における前縁翼角θについて、前記第1実施形態および第2実施形態をともに備えたものである。
また、上記ではフルブレード間流路に1つのシングルスプリッタブレードを有する場合について述べたが、シングルスプリッタブレード間流路に設けられた、シングルスプリッタブレードよりも更に短いダブルスプリッタブレードについて本発明を適用してももちろん良い。
Claims (6)
- ハブ面上に流体の入口部から出口部にかけて複数設けられるフルブレードと、互いに隣り合わせて設けられる前記フルブレードの間に形成される流路の途中から出口部にかけて設けられるスプリッタブレードとを備えた遠心圧縮機のインペラにおいて、
前記スプリッタブレードの入口端部における前縁翼角を、ハブ面からの高さ方向で異ならせるとともに、先端部分をその他部分より大きい傾斜角度をもって前記フルブレードの負圧面側に傾斜させたことを特徴とする遠心圧縮機のインペラ。 - 前記高さ方向の先端部分が全高の略70%以上であり、該略70%の位置を起点として先端に向かって一定角度まで徐々に傾斜角度を増加させたことを特徴とする請求項1記載の遠心圧縮機のインペラ。
- ハブ面上に流体の入口部から出口部にかけて複数設けられるフルブレードと、互いに隣り合わせて設けられる前記フルブレードの間に形成される流路の途中から出口部にかけて設けられるスプリッタブレードとを備えた遠心圧縮機のインペラにおいて、
前記スプリッタブレードの入口端部における前縁翼角を、ハブ面からの高さ方向で異ならせるとともに、ハブ面側部分をその他部分より大きい傾斜角度をもって前記フルブレードの圧力面側に傾斜させたことを特徴とする遠心圧縮機のインペラ。 - 前記ハブ面側部分が全高の略70%以下であり、該略70%の位置を起点としてハブ面に向かって一定角度まで徐々に傾斜角度を増加させたことを特徴とする請求項3記載の遠心圧縮機のインペラ。
- ハブ面上に流体の入口部から出口部にかけて複数設けられるフルブレードと、互いに隣り合わせて設けられる前記フルブレードの間に形成される流路の途中から出口部にかけて設けられるスプリッタブレードとを備えた遠心圧縮機のインペラにおいて、
前記スプリッタブレードの入口端部における前縁翼角を、ハブ面からの高さ方向で異ならせるとともに、ハブ面からの高さ方向の上端部分をフルブレードの負圧面側に傾斜させ、高さ方向のハブ面側部分をフルブレードの圧力面側に傾斜させたことを特徴とする遠心圧縮機のインペラ。 - 高さ方向の前記上端部分と前記ハブ面側部分とはハブ面からの全高の略70%より上部と下部によって区分することを特徴とする請求項5記載の遠心圧縮機のインペラ。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP19152296.0A EP3495666B1 (en) | 2009-10-07 | 2010-08-10 | Impeller of centrifugal compressor |
EP10821796.9A EP2392830B1 (en) | 2009-10-07 | 2010-08-10 | Impeller for centrifugal compressor |
US13/203,940 US9033667B2 (en) | 2009-10-07 | 2010-08-10 | Impeller of centrifugal compressor |
CN201080009428.2A CN102333961B (zh) | 2009-10-07 | 2010-08-10 | 离心压缩机的叶轮 |
KR1020117019768A KR101347469B1 (ko) | 2009-10-07 | 2010-08-10 | 원심 압축기의 임펠러 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009-233183 | 2009-10-07 | ||
JP2009233183A JP5495700B2 (ja) | 2009-10-07 | 2009-10-07 | 遠心圧縮機のインペラ |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011043125A1 true WO2011043125A1 (ja) | 2011-04-14 |
Family
ID=43856605
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2010/063581 WO2011043125A1 (ja) | 2009-10-07 | 2010-08-10 | 遠心圧縮機のインペラ |
Country Status (6)
Country | Link |
---|---|
US (1) | US9033667B2 (ja) |
EP (2) | EP2392830B1 (ja) |
JP (1) | JP5495700B2 (ja) |
KR (1) | KR101347469B1 (ja) |
CN (1) | CN102333961B (ja) |
WO (1) | WO2011043125A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2012081435A1 (ja) * | 2010-12-13 | 2012-06-21 | 三菱重工業株式会社 | 遠心圧縮機の羽根車 |
Families Citing this family (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012209832B3 (de) * | 2012-06-12 | 2013-09-12 | E.G.O. Elektro-Gerätebau GmbH | Pumpe und Verfahren zum Herstellen eines Impellers für eine Pumpe |
CN102889237B (zh) * | 2012-06-12 | 2015-04-22 | 中国科学院工程热物理研究所 | 一种应用带尖角前缘的大小叶片叶轮及压气机 |
US9976422B2 (en) | 2013-02-26 | 2018-05-22 | United Technologies Corporation | Variable span splitter blade |
KR101442805B1 (ko) * | 2013-08-16 | 2014-09-23 | 허태준 | 길이 연장이 용이한 공압식 원심 펌프 |
KR101493685B1 (ko) * | 2013-08-19 | 2015-02-16 | 한국에너지기술연구원 | 후향전곡 비틀림깃형 혼류 임펠러의 구조 |
WO2015048230A1 (en) * | 2013-09-30 | 2015-04-02 | Borgwarner Inc. | Vortex generator on a compressor blade of a turbocharger |
JP6133748B2 (ja) | 2013-10-09 | 2017-05-24 | 三菱重工業株式会社 | インペラ及びこれを備える回転機械 |
KR102280929B1 (ko) * | 2014-04-15 | 2021-07-26 | 삼성전자주식회사 | 진공청소기 |
KR102159581B1 (ko) * | 2014-04-15 | 2020-09-24 | 삼성전자주식회사 | 진공청소기 |
CN103939148B (zh) * | 2014-04-28 | 2015-09-30 | 哈尔滨工程大学 | 一种带有多分流叶片的径流式透平 |
JP6413980B2 (ja) * | 2014-09-04 | 2018-10-31 | 株式会社デンソー | ターボチャージャの排気タービン |
US20160160653A1 (en) * | 2014-12-08 | 2016-06-09 | Hyundai Motor Company | Turbine wheel for turbo charger |
US10221858B2 (en) | 2016-01-08 | 2019-03-05 | Rolls-Royce Corporation | Impeller blade morphology |
JP6746943B2 (ja) | 2016-02-23 | 2020-08-26 | 株式会社Ihi | 遠心圧縮機インペラ |
WO2017203641A1 (ja) | 2016-05-25 | 2017-11-30 | 三菱電機株式会社 | 電動送風機、電気掃除機およびハンドドライヤー |
US10641282B2 (en) * | 2016-12-28 | 2020-05-05 | Nidec Corporation | Fan device and vacuum cleaner including the same |
JP6740271B2 (ja) | 2018-03-05 | 2020-08-12 | 三菱重工業株式会社 | 羽根車及びこの羽根車を備えた遠心圧縮機 |
US10962021B2 (en) | 2018-08-17 | 2021-03-30 | Rolls-Royce Corporation | Non-axisymmetric impeller hub flowpath |
GB201813819D0 (en) * | 2018-08-24 | 2018-10-10 | Rolls Royce Plc | Turbomachinery |
GB2576565B (en) * | 2018-08-24 | 2021-07-14 | Rolls Royce Plc | Supercritical carbon dioxide compressor |
JP7140030B2 (ja) * | 2019-03-28 | 2022-09-21 | 株式会社豊田自動織機 | 燃料電池用遠心圧縮機 |
JP2020186649A (ja) * | 2019-05-10 | 2020-11-19 | 三菱重工業株式会社 | 遠心圧縮機のインペラ、遠心圧縮機及びターボチャージャ |
SE543329C2 (en) * | 2019-06-13 | 2020-12-01 | Scania Cv Ab | Centrifugal Compressor Impeller for a Charging Device of an Internal Combustion Engine |
WO2021234863A1 (ja) | 2020-05-20 | 2021-11-25 | 三菱重工エンジン&ターボチャージャ株式会社 | 遠心圧縮機のインペラ及び遠心圧縮機 |
CN114412831B (zh) * | 2022-01-24 | 2024-06-14 | 北京小狗吸尘器集团股份有限公司 | 一种叶轮、带有该叶轮的风机总成以及吸尘器 |
KR102617798B1 (ko) * | 2023-08-22 | 2023-12-27 | (주)그린텍 | 양정 및 효율을 향상시키는 임펠러 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS56110600A (en) * | 1980-02-06 | 1981-09-01 | Mitsubishi Heavy Ind Ltd | Double flow turbo machine |
JPH10213094A (ja) | 1997-01-31 | 1998-08-11 | Ishikawajima Harima Heavy Ind Co Ltd | 遠心圧縮機のインペラ |
JP2002516960A (ja) * | 1998-05-27 | 2002-06-11 | 株式会社荏原製作所 | ターボ機械の羽根車 |
JP2002332992A (ja) | 2001-05-11 | 2002-11-22 | Toyota Central Res & Dev Lab Inc | 遠心圧縮機のインペラ |
JP2004052754A (ja) * | 2002-05-10 | 2004-02-19 | Borgwarner Inc | チタン圧縮機翼車のためのハイブリッド製造法 |
JP3876195B2 (ja) | 2002-07-05 | 2007-01-31 | 本田技研工業株式会社 | 遠心圧縮機のインペラ |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4093401A (en) * | 1976-04-12 | 1978-06-06 | Sundstrand Corporation | Compressor impeller and method of manufacture |
JPS5644495A (en) * | 1979-09-20 | 1981-04-23 | Nissan Motor Co Ltd | Impeller for centrifugal compressor |
FR2550585B1 (fr) * | 1983-08-09 | 1987-01-16 | Foueillassar Jean Marie | Moyens d'uniformiser la vitesse d'un fluide a la sortie d'un rouet centrifuge |
US5061154A (en) * | 1989-12-11 | 1991-10-29 | Allied-Signal Inc. | Radial turbine rotor with improved saddle life |
US5002461A (en) * | 1990-01-26 | 1991-03-26 | Schwitzer U.S. Inc. | Compressor impeller with displaced splitter blades |
JP2002332993A (ja) * | 2001-05-09 | 2002-11-22 | Toyota Central Res & Dev Lab Inc | 遠心圧縮機のインぺラ |
JP4469370B2 (ja) * | 2004-05-28 | 2010-05-26 | 株式会社日立メタルプレシジョン | 過給機用羽根車およびその製造方法 |
CN100485194C (zh) * | 2007-07-30 | 2009-05-06 | 北京航空航天大学 | 一种离心叶轮 |
-
2009
- 2009-10-07 JP JP2009233183A patent/JP5495700B2/ja active Active
-
2010
- 2010-08-10 EP EP10821796.9A patent/EP2392830B1/en active Active
- 2010-08-10 EP EP19152296.0A patent/EP3495666B1/en active Active
- 2010-08-10 WO PCT/JP2010/063581 patent/WO2011043125A1/ja active Application Filing
- 2010-08-10 KR KR1020117019768A patent/KR101347469B1/ko active IP Right Grant
- 2010-08-10 US US13/203,940 patent/US9033667B2/en active Active
- 2010-08-10 CN CN201080009428.2A patent/CN102333961B/zh active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS56110600A (en) * | 1980-02-06 | 1981-09-01 | Mitsubishi Heavy Ind Ltd | Double flow turbo machine |
JPH10213094A (ja) | 1997-01-31 | 1998-08-11 | Ishikawajima Harima Heavy Ind Co Ltd | 遠心圧縮機のインペラ |
JP2002516960A (ja) * | 1998-05-27 | 2002-06-11 | 株式会社荏原製作所 | ターボ機械の羽根車 |
JP2002332992A (ja) | 2001-05-11 | 2002-11-22 | Toyota Central Res & Dev Lab Inc | 遠心圧縮機のインペラ |
JP2004052754A (ja) * | 2002-05-10 | 2004-02-19 | Borgwarner Inc | チタン圧縮機翼車のためのハイブリッド製造法 |
JP3876195B2 (ja) | 2002-07-05 | 2007-01-31 | 本田技研工業株式会社 | 遠心圧縮機のインペラ |
Non-Patent Citations (1)
Title |
---|
See also references of EP2392830A1 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2012081435A1 (ja) * | 2010-12-13 | 2012-06-21 | 三菱重工業株式会社 | 遠心圧縮機の羽根車 |
JP2012127217A (ja) * | 2010-12-13 | 2012-07-05 | Mitsubishi Heavy Ind Ltd | 遠心圧縮機の羽根車 |
US9683445B2 (en) | 2010-12-13 | 2017-06-20 | Mitsubishi Heavy Industries, Ltd. | Impeller for centrifugal compressor |
Also Published As
Publication number | Publication date |
---|---|
EP2392830B1 (en) | 2019-03-06 |
EP3495666B1 (en) | 2024-02-21 |
CN102333961A (zh) | 2012-01-25 |
CN102333961B (zh) | 2014-07-30 |
EP2392830A4 (en) | 2018-06-06 |
EP3495666A1 (en) | 2019-06-12 |
JP2011080411A (ja) | 2011-04-21 |
JP5495700B2 (ja) | 2014-05-21 |
US20120189454A1 (en) | 2012-07-26 |
KR20110106946A (ko) | 2011-09-29 |
US9033667B2 (en) | 2015-05-19 |
EP2392830A1 (en) | 2011-12-07 |
KR101347469B1 (ko) | 2014-01-02 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5495700B2 (ja) | 遠心圧縮機のインペラ | |
JP5308319B2 (ja) | 遠心圧縮機の羽根車 | |
JP5316365B2 (ja) | ターボ型流体機械 | |
JP5665535B2 (ja) | 遠心圧縮機 | |
JP5574951B2 (ja) | 遠心圧縮機の羽根車 | |
US7604458B2 (en) | Axial flow pump and diagonal flow pump | |
JP5680396B2 (ja) | 遠心圧縮機の羽根車 | |
WO2012090649A1 (ja) | 遠心圧縮機のスクロール構造 | |
WO2013073469A1 (ja) | 遠心式流体機械 | |
JP2009133267A (ja) | 圧縮機のインペラ | |
US11572890B2 (en) | Blade and axial flow impeller using same | |
JP5905059B2 (ja) | 渦巻ポンプ | |
JP5977508B2 (ja) | 水車ステーベーン及び水車 | |
WO2011065039A1 (ja) | 渦巻ポンプ | |
JP4893125B2 (ja) | 両吸込渦巻ポンプ | |
CN116398469A (zh) | 一种离心风机及应用有该离心风机的吸油烟机 | |
JP5589989B2 (ja) | 遠心送風機 | |
CN111022376A (zh) | 一种复合式叶片、一种压缩机叶片扩压器 | |
JP2008031938A (ja) | 遠心式ポンプ |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201080009428.2 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 10821796 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 20117019768 Country of ref document: KR Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2010821796 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13203940 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |