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EP0752066A1 - Dispositif pour reduire le bruit de pompes centrifuges - Google Patents

Dispositif pour reduire le bruit de pompes centrifuges

Info

Publication number
EP0752066A1
EP0752066A1 EP95913122A EP95913122A EP0752066A1 EP 0752066 A1 EP0752066 A1 EP 0752066A1 EP 95913122 A EP95913122 A EP 95913122A EP 95913122 A EP95913122 A EP 95913122A EP 0752066 A1 EP0752066 A1 EP 0752066A1
Authority
EP
European Patent Office
Prior art keywords
impeller
guide device
leading edge
edges
blade
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP95913122A
Other languages
German (de)
English (en)
Other versions
EP0752066B1 (fr
Inventor
Bernd Müller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KSB AG
Original Assignee
KSB AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by KSB AG filed Critical KSB AG
Publication of EP0752066A1 publication Critical patent/EP0752066A1/fr
Application granted granted Critical
Publication of EP0752066B1 publication Critical patent/EP0752066B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/428—Discharge tongues
    • 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
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps

Definitions

  • the invention relates to a guide device according to the preamble of the main claim.
  • WO 91/13259 provides for an inclined position of the trailing edges of the impeller blades and the use of additional intermediate blades. In the case of spatially curved impeller blades, this oblique course of the impeller blade ends, which inevitably occurs, has a known, more favorable pulsation behavior.
  • an inclined position was chosen, in which the transitions between the blade leading edge and the one impeller cover disc are offset by the distance to an adjacent blade on the opposite impeller cover disc.
  • the transition points between the blade leading edge and the cover plate lie axially parallel to the axis of rotation, while the course of the blade leading edge runs diagonally between the transition points by the offset of a blade spacing.
  • the opposite hydraulic and manufacturing limits are disadvantageous. This is because, for hydraulic reasons, the curvature, the outlet angle of the impeller blades and their inclination can only be changed in a relatively small angular range with respect to the axis of rotation, since otherwise a desired operating point of the pump cannot be reached. Such changes can lead to reduced efficiency.
  • the guide device arranged downstream of an impeller which converts the speed energy of the pumped medium generated by the impeller into pressure energy, can be a spiral with at least one leading edge or also a downstream guide wheel with the leading edges of the respective stator blades.
  • the leading edges of the guide device according to the invention have an oblique profile with respect to the axis of rotation of the impeller. Their inclination, irrespective of whether it is a spur of a spiral forming a leading edge or leading edges of stator blades, has no adverse effects on the function of the guiding device.
  • the wall surfaces of the stator blades within the stator have an oblique position that follows the inclined position of the leading edges.
  • the blade channel formed between them has a cross-sectional area that resembles a parallelogram.
  • the course of the leading edge is decisive.
  • the subsequent course of the vane surfaces of the guide device can correspond to customary practices or design rules. What is essential is a course that corresponds to the intended use of the guide device. In the same way, this applies to the spur of a volute casing, which is designed as a single blade.
  • the entry into the guide device can be designed for optimal noise reduction
  • the guide device itself can be designed for the desired pressure conversion
  • the outlet of the guide device can be designed for the most favorable inflow conditions of a downstream impeller.
  • the guide device itself should enable the desired pressure conditions between its delimiting wall surfaces.
  • the inventive design of the leading edges of a guide device arranged downstream of an impeller can also be explained with the help of another example.
  • the assumption is that the vanes of a stator arranged between two annular wall surfaces or the leading edge or the spur of a spiral can be changed telescopically in width and are articulated to the wall surfaces along their length.
  • the leading edges according to the invention can then be produced by rotating one wall surface relative to the other wall surface and around its center axis.
  • the course of the blade or spur surfaces downstream of the inflow edges changes accordingly.
  • any other possible blade surface profile can also be implemented in a constructive manner, which causes an intended energy conversion by means of a diffuser-like enlargement of the guide channel cross section.
  • leading edges of a guiding device has surprisingly been found in practical trials to be its significantly improved cavitation behavior.
  • leading edge according to the invention had no cavitation damage.
  • conventional leading edge showed material removal due to cavitation.
  • a further advantage has been found to be that those blades of a guide device which were designed according to the invention had a significantly lower dynamic blade load during operation. This provides the possibility of exposing the control devices according to the invention to higher loads or to equip high-load centrifugal pumps with a safety advantage by reducing the loads on their leading edges.
  • Claims 2 to 8 describe further refinements of the invention.
  • a significant advantage of the invention is the possibility of making the radial distance between one or more leading edges of the guide device and the impeller smaller than was previously the case. This results in hydraulic advantages. Larger forces that may result from the inclination of the leading edges can be used for axial thrust compensation.
  • a large number of possible inclined positions of the leading edge are possible depending on the size of the impeller-guide device combinations used and the number of blades used.
  • the leading edge or edges can also be arranged, for example, in such a way that they run from the same to an opposite oblique position to the impeller blade outlet edges.
  • the blade edges of the impeller outlet and the guide device inlet are arranged with an inclination in the same direction, an angular offset must be observed in order to rule out a linear passage between the leading edge and the impeller blade.
  • the wall surface following the leading edge of a spur has a streamlined transition into the subsequent, unchanged spiral space.
  • noise reductions of the pressure pulsations of the order of magnitude of up to 20 dB could be determined.
  • the sloping leading edges have a length that corresponds to 0.1 to 1.2 times the impeller blade division at the impeller outlet. Accordingly, in the circumferential direction, the ends of the leading edges merging into the delimiting wall surfaces are arranged offset to one another.
  • a non-linear profile for the leading edges can also be useful when using impellers whose blade trailing edges have a course which makes a non-linear leading edge of a guide device appear reasonable.
  • An arrow-shaped design which can have a positive or negative sweep comparable to an arrow wing, can be attached to both the leading edge and the blade leading edge of the impeller. Appropriate combinations enable a significant reduction in noise behavior for a wide variety of applications.
  • An arrowing of the leading edges can be useful, for example, in the case of double-flow impeller designs, in order not to give rise to axial thrust forces.
  • the chosen course of an inclination can have an influence on the axial thrust of an impeller. This can depend on the pressure distribution at an impeller outlet at the respective design point. This is because, depending on the design principles used in an impeller, the resulting pressure component can be displaced toward the suction or pressure side cover plate of the impeller. With the help of an appropriately selected inclined position of the leading edge It is then also possible to influence the pump characteristic. The point of optimal efficiency can then be shifted to a smaller or larger amount. With this inclination, the freedom of design when designing a centrifugal pump can be increased as a positive side effect.
  • the guide device according to the invention is independent of an impeller. It thus offers the possibility of retrofitting already installed systems if they are provided with an exchangeable control device or can be adapted accordingly.
  • a further embodiment provides that the distance between the cylinder planes, on which the leading edges of the guide device and the trailing edges of the moving blades lie, is different. This feature offers several advantages. So with a stator different distances between the impeller outlet diameter and
  • Guide vane leading edges are provided. A different distance between successive guide vanes could equally well be provided, ie every second leading edge would then have the same distance. On the one hand, this enables direct influences on the noise emissions produced by the impeller and guide device, and on the other hand the forces acting on the guide device can be better absorbed.
  • the general design rule that the number of blades of an impeller should not be identical to the number of blades of a guide device for reasons of noise no longer needs to be observed in a centrifugal pump with a guide wheel device designed according to the invention.
  • Fig. 1 a guide device as a perspective view of a stator
  • Fig. 2 shows a section through a centrifugal pump with a spiral as a guide device
  • FIG. 1 A perspective view of a stator is shown in FIG. 1 as the guide device 1. For better visibility, the idler was shown open.
  • a guide wheel usually consists of two wall surfaces, between which connecting guide vanes are arranged.
  • the stator shown here has a wall surface 2, with which several stator blades 3 are firmly connected.
  • the leading edges 4 of the guide blades 3 lie on a cylinder surface which is concentric with the axis of rotation of the impeller is arranged. On this cylinder surface the leading edges follow the curvature of the cylinder surface and extend crossing to the axis of rotation.
  • the leading edges 4 and the trailing edges 5 run axially parallel.
  • the meridian cut marks the surface that a blade sweeps over as it rotates around the axis of rotation of the impeller.
  • the leading edges have an inclination or overlap, which is equal to the blade pitch t of the guide device 1.
  • the leading edge 4 extends from its one end point 6, which is located on the wall surface 2, to its other, here freely standing end point 7.
  • the inclined position of the leading edge 4 was chosen so that the end point 7, in the direction seen the axis of rotation standing on the plane of the drawing, is located above the end point 6 of an adjacent guide vane 3.
  • the mutual offset of the end points 6, 7 of a leading edge 4 corresponds here to the simple one of a blade division.
  • the inclination can correspond to 0.1 to 1.2 times a blade pitch t of an impeller.
  • an inclined position is selected which corresponds to a maximum of one blade division at the impeller outlet.
  • the bevel in such impellers will correspond to a smaller value in order to maintain the inlet cross section of a correspondingly narrow guide device in a manner favorable in terms of production technology.
  • an oblique position can be used which extends up to 1.2 times a blade pitch.
  • the guide device 1 shown here is shown as a so-called open guide wheel for better visibility. It could be installed directly and z. B. in a multi-stage pump with the open side on a stage housing wall. However, it is also easily possible to design this stator as a so-called closed stator. The blades would then be arranged between two wall surfaces.
  • Fig. 2 shows a sectional view of a housing 8 of a centrifugal pump.
  • the guide device 1 is designed here as a spiral 9.
  • An impeller 10 is arranged within the housing 8. Whose blade leading edges 11 pass through the leading edge 12 during operation. This extends between the cutting lines H 1 - H 3 and runs obliquely to the axis of rotation 13 perpendicular to the plane of the drawing and partly in the spiral 9 headed.
  • the leading edge and the spiral have a more or less pronounced shape or groove 16.
  • it has been shown enlarged for reasons of better clarity. This change in cross-section of the spiral is designed according to the desired operating conditions. At the beginning of the leading edge 12, the formation or groove 16 develops like a guide channel into the spiral.
  • the inclined position of the leading edge 12 located on the spur can extend up to a blade division of the impeller or, in the case of wide impeller exit surfaces, can also extend beyond it. It is also essential here to maintain an approximately uniform gap between the impeller outlet and the beginning of the spiral.
  • a view along the section line H 1 shows a view of the leading edge 12, which runs obliquely to the plane of the drawing, and which guides medium emerging from the spiral 9 into the pressure port 15.
  • FIG. 4 A section behind line H 2 in the direction of flow is shown in FIG. 4.
  • Medium emerging from the impeller 10 flows on the one hand into the groove 16 and there further into the spiral 9. Another part reaches the pressure port 15 along the shape 14.
  • this can be for the duration of the passage of a respective blade channel of an impeller 10 along the leading edge 12, a small part of the conveyed medium from the impeller 10 directly into the pressure port 15.
  • a Loss of efficiency is not to be expected from this and can be eliminated if necessary by simply adjusting the impeller.
  • the course of a leading edge 4, 12 can, as shown in the developments of FIGS. 6-9 using the example of individual leading edges 4, 12, also have a shape deviating from a straight line. These can be continuous or discontinuous courses, sudden changes or the like. Depending on the pressure distribution profile prevailing at an impeller outlet, a course of a leading edge 4, 12 can be selected if necessary, which offers the most favorable conditions with regard to stability, noise reduction and axial thrust behavior.
  • the courses shown in FIGS. 6-9 are only exemplary and the subject matter of the invention is not limited to them. Here too, the chosen course does not have any adverse effects on the behavior of a stator channel or spiral space. Because its ability to convert energy is largely determined by its cross-sectional relationship.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un dispositif permettant de réduire le bruit dû au fonctionnement hydraulique de pompes centrifuges. A cet effet, les arêtes d'écoulement d'un dispositif de guidage, situées en aval d'une roue à aubes, sont disposées en biais. Les arêtes d'écoulement peuvent être en l'occurrence linéaires ou non linéaires.
EP95913122A 1994-03-19 1995-03-15 Dispositif pour reduire le bruit de pompes centrifuges Expired - Lifetime EP0752066B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4409475 1994-03-19
DE4409475 1994-03-19
PCT/EP1995/000963 WO1995025895A1 (fr) 1994-03-19 1995-03-15 Dispositif pour reduire le bruit de pompes centrifuges

Publications (2)

Publication Number Publication Date
EP0752066A1 true EP0752066A1 (fr) 1997-01-08
EP0752066B1 EP0752066B1 (fr) 2000-03-01

Family

ID=6513282

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95913122A Expired - Lifetime EP0752066B1 (fr) 1994-03-19 1995-03-15 Dispositif pour reduire le bruit de pompes centrifuges

Country Status (5)

Country Link
US (1) US6017187A (fr)
EP (1) EP0752066B1 (fr)
JP (1) JPH09510527A (fr)
DE (2) DE59507918D1 (fr)
WO (1) WO1995025895A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29920373U1 (de) * 1999-11-19 2000-01-13 Motoren Ventilatoren Landshut Gmbh, 84030 Landshut Gehäuse für einen Lüfter, insbesondere einen Radiallüfter
DE10051223A1 (de) 2000-10-16 2002-04-25 Alstom Switzerland Ltd Verbindbare Statorelemente
US7238164B2 (en) * 2002-07-19 2007-07-03 Baxter International Inc. Systems, methods and apparatuses for pumping cassette-based therapies
JP2008019752A (ja) * 2006-07-12 2008-01-31 Hitachi Plant Technologies Ltd 多段ディフューザポンプ
WO2010030802A2 (fr) 2008-09-10 2010-03-18 Pentair Pump Group, Inc. Pompe centrifuge multi-étages à haut rendement et procédé de montage
CN101929465B (zh) * 2009-06-19 2013-12-11 德昌电机(深圳)有限公司 排水泵
KR101270899B1 (ko) * 2010-08-09 2013-06-07 엘지전자 주식회사 임펠러 및 이를 포함하는 원심 압축기
US8951009B2 (en) * 2011-05-23 2015-02-10 Ingersoll Rand Company Sculpted impeller
WO2014074204A1 (fr) * 2012-11-10 2014-05-15 Carrier Corporation Pompe centrifuge avec avant-bec incliné anticavitation
US9581034B2 (en) 2013-03-14 2017-02-28 Elliott Company Turbomachinery stationary vane arrangement for disk and blade excitation reduction and phase cancellation
JP6117658B2 (ja) * 2013-09-06 2017-04-19 本田技研工業株式会社 遠心ポンプ
ES2973382T3 (es) * 2017-05-09 2024-06-19 Sulzer Management Ag Carcasa de voluta para bomba centrífuga y bomba centrífuga
CN112879341B (zh) * 2021-01-22 2022-04-08 兰州理工大学 一种高抗空化进口后掠及分流偏置式螺旋离心式叶轮
US11852162B2 (en) 2021-12-17 2023-12-26 Robert Bosch Llc Centrifugal pump assembly

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE319721C (de) * 1920-03-15 Ludwig Hartwagner Fliehkraftluefter mit Schneckengehaeuse
DE1071888B (fr) * 1959-12-24
DE157924C (fr) *
FR352787A (fr) * 1905-03-28 1905-08-21 Turbine Pump Company Pompe à turbine
FR361986A (fr) * 1905-12-13 1907-01-23 Sautter Harle & Cie Soc Dispositif assurant la continuité du mouvement du fluide dans les pompes centrifuges multicellulaires
GB112292A (en) * 1916-12-29 1917-12-31 Alfred Ernest Lole Improvements in or relating to Rotary Pumps and the like.
US2018092A (en) * 1934-12-24 1935-10-22 Charles H Rickert Liquid pump
US2362514A (en) * 1941-06-03 1944-11-14 Gen Electric Centrifugal compressor
US2405283A (en) * 1941-08-19 1946-08-06 Fed Reserve Bank Elastic fluid mechanism
FR1091307A (fr) * 1953-03-17 1955-04-12 Ratier Aviat Marine Machine à circulation de fluide
US3628881A (en) * 1970-04-20 1971-12-21 Gen Signal Corp Low-noise impeller for centrifugal pump
SE376640B (fr) * 1973-05-14 1975-06-02 Sonesson Pumpind Ab
JPS5545760B2 (fr) * 1975-02-07 1980-11-19
CH626954A5 (en) * 1977-09-14 1981-12-15 Sulzer Ag Centrifugal pump
JPS59231199A (ja) * 1983-06-11 1984-12-25 Kobe Steel Ltd 圧縮機用羽根付デイフユ−ザ
JPS61169696A (ja) * 1985-01-24 1986-07-31 Kobe Steel Ltd 多翼送風機における風切音低減装置
JPS6210495A (ja) * 1985-07-08 1987-01-19 Matsushita Electric Ind Co Ltd 送風装置
FI87009C (fi) * 1990-02-21 1992-11-10 Tampella Forest Oy Skovelhjul foer centrifugalpumpar
DE9006171U1 (de) * 1990-05-31 1991-10-10 Siemens AG, 8000 München Spiralgebläse
WO1993010358A1 (fr) * 1991-11-15 1993-05-27 Moskovskoe Obschestvo Soznaniya Krishny Procede de formation d'un flux d'air dans le systeme de sortie d'un compresseur centrifuge et compresseur centrifuge
DE4309479A1 (de) * 1993-03-24 1994-09-29 Wilo Gmbh Radialkreiselpumpe
DE4313617C2 (de) * 1993-04-26 1996-04-25 Kreis Truma Geraetebau Radialgebläse
JP3482668B2 (ja) * 1993-10-18 2003-12-22 株式会社日立製作所 遠心形流体機械

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9525895A1 *

Also Published As

Publication number Publication date
DE59507918D1 (de) 2000-04-06
WO1995025895A1 (fr) 1995-09-28
US6017187A (en) 2000-01-25
EP0752066B1 (fr) 2000-03-01
DE19509255A1 (de) 1995-09-21
JPH09510527A (ja) 1997-10-21

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