EP2222962B1 - Deckscheibe für ein geschlossenes laufrad - Google Patents
Deckscheibe für ein geschlossenes laufrad Download PDFInfo
- Publication number
- EP2222962B1 EP2222962B1 EP09720229.5A EP09720229A EP2222962B1 EP 2222962 B1 EP2222962 B1 EP 2222962B1 EP 09720229 A EP09720229 A EP 09720229A EP 2222962 B1 EP2222962 B1 EP 2222962B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shroud plate
- radius
- front side
- impeller
- curvature
- 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.)
- Not-in-force
Links
- 230000007423 decrease Effects 0.000 claims description 4
- 239000012530 fluid Substances 0.000 description 3
- 210000001015 abdomen Anatomy 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000007704 transition Effects 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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2216—Shape, geometry
-
- 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 invention relates to a cover plate for a closed impeller of a radial or diagonal flow machine, for example a radial compressor or expander, in particular a turbo compressor, an impeller with such a cover plate and a turbomachine with such an impeller.
- Closed impellers in which a flow channel through the blades, an impeller wheel carrying them and a cover disk connected to the blades, are defined, for example, in US Pat DE 198 33 033 A1 known, which in Figures 8 to 13 covers with different meridian cross sections.
- the wall thickness above the profile center line of the meridian cross section of such cover disks generally decreases continuously from a suction mouth to a flow outlet.
- the DE 25 55 101 B and the US 2,344,444 A disclose cover bands which are formed of sheets with identical wall thicknesses, wherein an outer sheet has corrugated portions.
- the US 2,392,858 A shows an impeller of a centrifugal compressor with a shroud and a separate stiffening ring. Disadvantageous occur in known shrouds high voltages to unfavorable structural sites. Object of the present invention is therefore to provide an improved cover plate available.
- a cover plate according to the preamble of claim 1 is further developed by its characterizing features. Claim 7 provides a closed impeller with such a cover, claim 8 a Turbomachine with such an impeller under protection.
- the dependent claims relate to preferred developments.
- the present invention is based on the finding that a local bulging of the outer cover surface leads to an impeller geometry which, in conjunction with a corresponding curvature of the outer cover surface in the centrifugal forces occurring during operation, can reduce stresses on critical structural regions.
- the invention proposes to provide in the region of a local maximum of the wall thickness of the cover plate on the outer surface of a convex curvature having a radius whose ratio to an outer diameter of the impeller is in a range between 0.05 and 0.5.
- the maximum stresses are reduced by 20% and also advantageously no longer occur at the critical end of the cover plate, but in a central connecting portion between the impeller disc and blade.
- the convex curvature of the outer surface of the cover disc merges into a concave curvature towards the first and / or second end side, so that the outer edge of the meridian cross section has a point of inflection before and / or after the local maximum in which the curvature changes its sign.
- Such outer surfaces with one or more oppositely curved regions are particularly low stress and can be made well.
- a cover plate according to the invention is provided for a closed impeller of a radial or diagonal flow machine, for example a radial compressor or expander, in particular a turbocompressor, and can for this purpose be formed in one piece with a blading, for example, formed in an original shape or machined.
- a cover plate according to the invention can also be connected to the blading, for example riveted, soldered and / or welded.
- a combination of both versions, as they are from the DE 41 13 831 A1 with radially divided blades is known, wherein an impeller part formed integrally with the cover plate, another Laufradtteil is permanently connected to this, may be advantageous.
- the cover disc together with a 2 D or 3 D blading and impeller disc, defines a flow channel for a fluid to be pumped, compressed or expanded.
- the cover disc has a profiling means or skeleton line which is in the middle between that facing away from the flow channel Outer surface and a flow channel facing the inner surface of the cover plate extends.
- the cover disk has a local maximum between a first and a second end face.
- the first end face can be, for example, an inlet or suction side, while the second end side can be an outlet or pressure side.
- the cover plate according to the invention has a belly between its inlet and outlet on its outer surface.
- the outer surface has a convex, outwardly curved curvature with a radius whose ratio to the outer diameter of the impeller is in a range between 0.05 and 0.5.
- the outer diameter of the impeller is in particular the largest or the nominal diameter of the impeller referred to.
- the bulge leads to a more favorable mass distribution, so that the maximum stresses occurring during operation are reduced. As a result, higher impeller speeds, longer life and / or the use of less solid and thus cheaper material possible. Due to the convex curvature with the radius ratio according to the invention, moreover, the occurrence of maximum stresses at structurally unfavorable points, for example the outer circumference of the cover plate in the region of the connection with the rotor blading, which is often embodied as a welded seam, can be avoided or such stresses can be reduced.
- the ratio of the radius' to the outer diameter is in a range between 0.1 and 0.4, more preferably in a range between 0.15 and 0.3. This results in particularly low-tension wheels.
- the concave curvature may have, for the first end face, a radius which is smaller than the radius of the convex curvature in the region of the local maximum is.
- the wall thickness of the cover disc decreases continuously towards the second end face.
- the continuous reduction in particular a reduction with substantially constant radius of curvature provides for an advantageous stress distribution.
- the cover plate runs out towards its outer circumference in a concavely curved section, which adjoins the convexly curved section in the region of the local maximum. This of course includes embodiments in which the outer peripheral edge of the outer surface itself is broken or otherwise formed with a small convex radius.
- Fig. 2 shows in half section the meridian cross section of a cover plate 1 'of a radial impeller (not shown) according to the prior art, as for example, from FIG. 12 of DE 198 33 033 A1 is known.
- this cover disk 1 ' the wall thickness along the profile center line of the meridian cross-section between a first end face 2' of the cover disk (left in Fig. 2 ), which defines a suction mouth of a radial flow machine (not shown), and one of these axially opposite second end face 3 'of the cover disk (right in FIG Fig. 2 ), which has a flow outlet from through the Shroud 1 'defined flow channel forms, continuously from the suction mouth 2' to the flow outlet 3 'from.
- Fig. 1 shows in Fig. 2 corresponding representation of the meridian cross section of a cover plate 1 of a radial impeller (not shown) according to an embodiment of the present invention with a first end face 2 (left in Fig. 1 ), through which a radial flow machine (not shown) draws in fluid axially, and one of these axially opposite second end face 3 of the cover disk (right in FIG Fig. 1 ), from which the fluid exits radially from the through the cover plate 1 and (not shown) blades and an impeller carrying this impeller flow channel.
- An inner surface 1.1 facing the flow channel has three convexly curved regions with the radii of curvature R1.1, R1.2 and R1.3, wherein .alpha Fig. 1 the radius is indicated in each case by an arrow in the direction from a center of curvature to the surface.
- One of the inner surface 1.1 opposite outer surface 1.2 of the cover plate 1 has, starting from the first end face 2, first to a longitudinal axis of the impeller (dash-dotted lines in Fig. 1 ) parallel, non-curved area. This merges into a concave region with a relatively small radius of curvature R2.1, in the middle perpendicular of which the wall thickness of the cover plate 1 tapers to a local minimum.
- This concave region is followed by a section curved away from the flow channel and having a convex curvature with a radius R2.2 that is greater than the curvature radius R2.1. Due to the change from a concave to a convex curvature, the centers of curvature lie on opposite sides of the outer surface 1.2 as indicated by the various arrow directions in FIG Fig. 1 indicated.
- the convex region in turn, in the direction of the second end face 3, again passes into a concave region with a radius of curvature R2. 3 in which the wall thickness of the cover plate 1 continuously decreases towards the second end side.
- the wall thickness along the profile center line of the meridian cross section of the cover plate 1 between the first end face 2 and the second end face 3 has a local maximum on.
- the outer surface 1.2 has a convex curvature with the radius R2.2, the quotient of which contributes to an outer diameter D2 of the impeller R 2.2 / D 2 ⁇ 0.22
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008013432A DE102008013432A1 (de) | 2008-03-10 | 2008-03-10 | Deckscheibe für ein geschlossenes Laufrad |
PCT/EP2009/001722 WO2009112242A2 (de) | 2008-03-10 | 2009-03-10 | Deckscheibe für ein geschlossenes laufrad |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2222962A2 EP2222962A2 (de) | 2010-09-01 |
EP2222962B1 true EP2222962B1 (de) | 2017-12-27 |
Family
ID=40952901
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09720229.5A Not-in-force EP2222962B1 (de) | 2008-03-10 | 2009-03-10 | Deckscheibe für ein geschlossenes laufrad |
Country Status (6)
Country | Link |
---|---|
US (1) | US8469669B2 (ja) |
EP (1) | EP2222962B1 (ja) |
JP (1) | JP5175363B2 (ja) |
CN (1) | CN101970883B (ja) |
DE (1) | DE102008013432A1 (ja) |
WO (1) | WO2009112242A2 (ja) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN104564802B (zh) * | 2015-01-06 | 2017-02-22 | 浙江理工大学 | 一种带有减阻槽的无蜗壳离心通风机 |
JP7161424B2 (ja) * | 2019-02-26 | 2022-10-26 | 三菱重工コンプレッサ株式会社 | インペラ及び回転機械 |
JP2022011812A (ja) * | 2020-06-30 | 2022-01-17 | 三菱重工コンプレッサ株式会社 | 回転機械のインペラ及び回転機械 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2344444A (en) * | 1940-03-29 | 1944-03-14 | Malczewski Jeremi | Construction of turbomachines |
US2392858A (en) * | 1943-03-08 | 1946-01-15 | Gen Electric | High-speed rotor for centrifugal compressors and the like |
DE2555101B1 (de) * | 1975-12-08 | 1976-10-21 | Klein Schanzlin & Becker Ag | Kreiselpumpenlaufrad aus blech |
US20040136825A1 (en) * | 2001-08-08 | 2004-07-15 | Addie Graeme R. | Multiple diverter for reducing wear in a slurry pump |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB407633A (en) * | 1932-10-01 | 1934-03-22 | Hermann Foettinger | Improvements in or relating to blading for centrifugal pumps and other machines having rotors with blades co-operating with flowing fluids |
US2305136A (en) * | 1941-01-31 | 1942-12-15 | Wright Aeronautical Corp | Centrifugal blower construction |
US3887295A (en) * | 1973-12-03 | 1975-06-03 | Gen Motors Corp | Compressor inlet control ring |
CN86210682U (zh) * | 1986-12-29 | 1987-10-07 | 中国科学院工程热物理研究所 | 离心泵 |
DE3709518C2 (de) | 1987-03-23 | 1995-01-19 | Hilge Philipp Gmbh | Laufrad |
DE4113831A1 (de) | 1991-04-27 | 1992-10-29 | Klein Schanzlin & Becker Ag | Geteiltes laufrad |
JPH08219001A (ja) * | 1995-02-08 | 1996-08-27 | Hitachi Ltd | フランシス型ポンプ水車 |
EP1000247B1 (de) | 1997-07-26 | 2002-05-08 | Allweiler AG | Lagerung für einen rotor einer strömungsmaschine sowie deren verwendung |
JP2001329993A (ja) * | 2000-05-19 | 2001-11-30 | Matsushita Electric Ind Co Ltd | ポンプの羽根車 |
US20060280610A1 (en) * | 2005-06-13 | 2006-12-14 | Heyward John P | Turbine blade and method of fabricating same |
-
2008
- 2008-03-10 DE DE102008013432A patent/DE102008013432A1/de not_active Withdrawn
-
2009
- 2009-03-10 CN CN2009801093937A patent/CN101970883B/zh not_active Expired - Fee Related
- 2009-03-10 EP EP09720229.5A patent/EP2222962B1/de not_active Not-in-force
- 2009-03-10 WO PCT/EP2009/001722 patent/WO2009112242A2/de active Application Filing
- 2009-03-10 US US12/919,553 patent/US8469669B2/en not_active Expired - Fee Related
- 2009-03-10 JP JP2010541757A patent/JP5175363B2/ja not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2344444A (en) * | 1940-03-29 | 1944-03-14 | Malczewski Jeremi | Construction of turbomachines |
US2392858A (en) * | 1943-03-08 | 1946-01-15 | Gen Electric | High-speed rotor for centrifugal compressors and the like |
DE2555101B1 (de) * | 1975-12-08 | 1976-10-21 | Klein Schanzlin & Becker Ag | Kreiselpumpenlaufrad aus blech |
US20040136825A1 (en) * | 2001-08-08 | 2004-07-15 | Addie Graeme R. | Multiple diverter for reducing wear in a slurry pump |
Also Published As
Publication number | Publication date |
---|---|
WO2009112242A2 (de) | 2009-09-17 |
EP2222962A2 (de) | 2010-09-01 |
JP5175363B2 (ja) | 2013-04-03 |
CN101970883B (zh) | 2013-12-25 |
DE102008013432A1 (de) | 2009-09-17 |
WO2009112242A3 (de) | 2009-11-05 |
JP2011509373A (ja) | 2011-03-24 |
CN101970883A (zh) | 2011-02-09 |
US8469669B2 (en) | 2013-06-25 |
US20110008160A1 (en) | 2011-01-13 |
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