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EP1573208B1 - Conduite d'aspiration - Google Patents

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Publication number
EP1573208B1
EP1573208B1 EP03813089A EP03813089A EP1573208B1 EP 1573208 B1 EP1573208 B1 EP 1573208B1 EP 03813089 A EP03813089 A EP 03813089A EP 03813089 A EP03813089 A EP 03813089A EP 1573208 B1 EP1573208 B1 EP 1573208B1
Authority
EP
European Patent Office
Prior art keywords
grooves
impeller
centrifugal pump
partial load
vortex
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03813089A
Other languages
German (de)
English (en)
Other versions
EP1573208A1 (fr
Inventor
Stephan Bross
Isabel Goltz
Peter Amann
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
Priority to SI200331836T priority Critical patent/SI1573208T1/sl
Publication of EP1573208A1 publication Critical patent/EP1573208A1/fr
Application granted granted Critical
Publication of EP1573208B1 publication Critical patent/EP1573208B1/fr
Priority to CY20101100699T priority patent/CY1110708T1/el
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04D29/406—Casings; Connections of working fluid especially adapted for liquid 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/688—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for liquid pumps

Definitions

  • the invention relates to a centrifugal pump, in whose housing one or more impellers of axial or semi-axial, closed or open design are arranged and a first impeller is preceded by a suction channel, in the wall surface a plurality of distributed over the circumference grooves are arranged.
  • Such characteristic curves are due to the formation of the so-called partial load vortex, which occurs when the volume flow in the outer region of a wheel impeller inlet is reduced.
  • a partial load vortex has a significant influence on the impeller inflow, which under its action experiences a blockage of the meridional flow cross section and high velocity components in the impeller rotation direction (constant rotation).
  • J-grooves which according to the reference “Improvement of Performance-Curve Instability in a Mixed-Flow Pump by J-Grooves", May 29-June 1, 2001, New La, Louisana, FEDSM 2001-18077, Proceedings of 2001 ASME Fluid Engineering Division Summer Meeting (FEDSM'01 ) , are commonly referred to as J-grooves due to their bent J-shaped course.
  • the J-grooves are flat, in other embodiments, also spatially curved grooves, which are mounted in the pump housing in the flow direction in front of and above the impeller blade open to be formed at the impeller inlet.
  • the grooves are crucial that they partially cover the outer diameter of the impeller.
  • the impeller In the area of impeller overlap, the impeller must be open to provide communication between a higher pressure fluid zone in the area of the open impeller blading and the overlying starts of the J-grooves. This constructive measure creates a fluid-conducting connection to the upstream inflow zone via the J-grooves.
  • the invention is based on the problem at specific high-speed centrifugal pumps with impellers semi-axial or axial, open or closed design to achieve a simple way to improve the NPSH behavior and to improve the partial load behavior.
  • the problem is to be solved in a simple way to be able to make a subsequent improvement in already in use centrifugal pumps, without affecting the performance in the normal driving range of the centrifugal pump in a negative way.
  • the solution to this problem provides that in the housing wall of the suction channel grooves are introduced and that between a Laufradeinstory the first impeller and the nearest ends of the grooves, a closed annular wall surface is formed, wherein the grooves are exclusively in operative connection with the suction channel.
  • a first impeller is designed as Sauglaufrad.
  • the closed annular wall surface formed in the housing wall of the suction channel is between the ends of the grooves upstream of the impeller inlet in the inflow direction and the impeller inlet arranged the first impeller.
  • Such a suction impeller may have a specific high speed nq ⁇ 70 min -1 .
  • the optimal operating point of a centrifugal pump remains unchanged and is, like the other operating points, in no way negatively affected.
  • a part-load vortices that form in part-load operation also called large prerotatory vertebrae, are weakened with the help of the elongated depressions.
  • the elongated grooves cause frictional energy transfer from the near-wall portion of the partial load vortex to many small eddies forming in the grooves.
  • the peripheral component and thus the intensity of the resulting partial load vortex are drastically reduced and as a result the partial load behavior of the centrifugal pump is improved.
  • An embodiment of the invention provides that the grooves between ridge-shaped formations of the housing wall of the suction channel are arranged. In those applications in which a processing of a suction channel is not possible or only with considerable difficulty, including the grooves or webs-containing annular insert can be inserted into an existing suction channel of a pump.
  • Such an insert allows easy machining of the grooves and can be easily installed in the suction channels newly manufactured or already delivered pumps. Due to the low, only a few millimeters amount of groove depths, which are formed only in the vicinity of the boundary layers close to the wall, such a design designed use is able to achieve an improvement of the partial load behavior even with already installed or installed in systems centrifugal pumps. For this purpose, only the, the use receiving suction duct may need to be slightly widened in inner diameter to accommodate a responsive diameter size of a grooved insert can.
  • kit used to allow using a skillful fürmesserabstufung in a variety of pump types, a use of such an insert.
  • the closed annular wall surface has a dependent on the intensity of a partial load vortex axial extent.
  • the length of the axial surface is at least so large that interference between the impeller blades at the impeller inlet and the groove ends arranged in front of it is reliably suppressed. Thus, the formation of disturbing noises and vibrations is prevented in the simplest way.
  • the length of the axial annular surface is chosen not larger than it corresponds to the extent of the slowly forming, yet harmless part-load vortex. Only when the training Partial load vortex receives a greater intensity, it is possible that its so-called detachment line separates from the impeller and skips the closed annular wall surface.
  • the partial load vortex completely exits the impeller. It is directed against the inflow and rotates in impeller rotation around the machine axis.
  • the tangential overflow of the depressions and the formation of many small vortices in the wells a large part of the energy contained in the partial load vortices is dissipated and the effect of the partial load vortices is drastically reduced.
  • the closed annular wall surface has a dependent on the intensity of a partial load vortex axial extent in the order of 0.005 - 0.02 times impeller inlet diameter.
  • the lengths of the grooves or ridges are in the order of 0.03 - 0.5 times impeller inlet diameter.
  • the depths of the grooves or the heights of the webs are on the order of 0.005-0.02 times the impeller inlet diameter.
  • Fig. 1 shows in a diagram by way of example and with dotted line a typical NPSH curve of centrifugal pumps with high-speed impellers of axial or semi-axial design.
  • the values for the flow rate Q are plotted.
  • the NPSH has a low value.
  • the NPSH curve is characterized by a local rise, the so-called NPSH peak, which limits the operating range at Q min at a predetermined, dashed maximum allowable NPSH A value of an associated system. Operation below this operating point is not permitted as otherwise cavitation-related conditions will occur inside the pump which will not permit continuous operation.
  • a further NPSH curve is drawn by a solid line, which corresponds to a centrifugal pump with the same operating points, in the suction channel but additionally arranged according to the invention grooves are mounted.
  • the one for one The curve curve determined in this way illustrates convincingly the considerably more favorable NPSH properties.
  • local NPSH surge is still present, it is at a significantly lower level than a pump without grooves.
  • Such an improved pump has a much wider operating range.
  • the Fig. 2 shows in the best point Q opt a centrifugal pump 1, the existing flow conditions using the example of an open axial wheel.
  • An impeller 2 rotates in a housing 3.
  • a circulating with the impeller backflow R in the form of a weak vortex.
  • This backflow R is due to the pressure exchange between the flow areas of adjacent blade channels and taking place in the region of free blade tips 4 pressure equalization between the suction and pressure side of blades 5.
  • Such with the impeller 2 rotating claimed about a zone which a blade width B equivalent.
  • This return flow region R has along the housing wall 6 a flow direction represented by arrows, which runs opposite to the impeller inlet LA.
  • a so-called detachment line SL is located at the point where the remindström with R reverses its direction of flow.
  • this line SL the energy of the impeller inlet LA is greater than the energy of the remindström responsiblees R, thereby causing its flow reversal.
  • a return flow region R exists over the entire operating range and is also present in the region of the best efficiency point.
  • Fig. 3 There is a similar Ragström which in two different types of closed wheels.
  • the upper illustration of the Fig. 3 shows the circumstances in a semi-axial pump construction, while in the lower illustration the conditions are shown in an axial pump.
  • cover plate 7 an exchange of energy through the blade tips 4 and between the suction and pressure side of a rotor blade 5.
  • For such wheels 2 has a small gap flow LF between the housing wall 6 and the cover plate 7, for the pressure difference before and behind the impeller is responsible.
  • By correspondingly low gap play between cover plate 7 and housing wall 6 such leakage is seriously reduced.
  • the Fig. 4 shows the example of an open impeller 2 in part-load operation adjusting formation of a partial load vortex PLV.
  • This and the following explanations also apply to a closed-type impeller.
  • Such a PLV part rotating with the impeller occurs in the region of the impeller outer diameter D at the impeller inlet edges 8 and against the impeller inlet LA out of the impeller 2 and flows back into the suction channel 9.
  • the rotating part-load vortex PLV there is a strong, transient interaction between the impeller inflow and the impeller flow, which manifests itself in particular by an abrupt increase in the NPSH values. The magnitude of this increase depends on the intensity of the forming part-load vortex.
  • the in the Fig. 4 circled positions X and Y are details and are used to represent the velocity triangles of Fig. 5 , A plurality of grooves 10 are distributed over the circumference and arranged in front of the impeller 2 in the wall surface 6 of the suction channel 9.
  • Fig. 5 shows the velocity ratios of a formed part-load vortex PLV at locations X and Y of FIG Fig. 4
  • the point X shows the speed ratios in the region close to the wall of the part-load vortex PLV emerging from the impeller 2 and the point Y the conditions in the part-distance vortex PLV which is remote from the wall and returns to the impeller 2.
  • the velocity triangles are drawn at the points X and Y, which are composed of the directional and the size of the eyes for the absolute velocity c, the relative velocity w and the peripheral velocity u.
  • the absolute velocity c x results from the peripheral circumferential velocity u x of a blade 5 and from the outflowing relative velocity w x of the partial load vortex PLV emerging from the impeller and is characterized by a high peripheral component c ux .
  • the arrows with the speed indication c ⁇ symbolize within the suction channel 9, the undisturbed inflow to the impeller with here drawn in section and having a profile blades 5.
  • a velocity triangle is drawn at Y, which is given at the point Y in the region of the entry point of the partial load vortex PLV in the impeller 2. Since the entry point Y is located on a smaller diameter, the peripheral speed u y is correspondingly lower. And as a result of the weakened in its energy partial load vortex PLV and its absolute velocity c y is correspondingly lower, resulting in a relative velocity w y results, which in this example to a certain extent offset by 90 ° to the relative velocity w x of an outgoing current thread of the partial load vortex PLV.
  • the reason for the weakening of the partial load vortex PLV is, in particular, the circumferential component c ux , which leads to a tangential overflow of the axially parallel grooves 10, as they are in Fig. 4 and in Fig. 6 , the plan view of a development of the housing wall 6, are shown. At this wall surface of the housing wall 6, the outer blade ends 4 run permanently past. In the housing wall 6, a plurality of distributed over the circumference arranged grooves 10 are mounted, which extend in the direction of the impeller inlet c ⁇ . Of the running in the inflow and in the wall surface 6 of the suction channel 9 grooves 10 whose groove ends 11 are arranged at a distance from the blade leading edge 8 on the outer diameter D of the impeller 2.
  • Fig. 6 shown in dashed lines different detachment lines SL 1 , SL 2 and SL 3 .
  • the detachment lines SL 1 , SL 2 show the suction-side boundaries of a forming Ragström whiches R at different operating conditions.
  • the detachment line SL 1 lies within the width of the impeller blades 5 and migrates with increasing part-load operation in front of the impeller or blade leading edge 8 up to the detachment line SL 2 .
  • the position of this detachment line SL 2 always remains in front of the impeller 2 in the region of a closed annular wall surface 12.
  • This wall surface 12 ensures that the fluid material flowing back from the region R can not enter the grooves 10.
  • the length L, considered counter to the impeller inlet direction LA, of the wall surface 12 reaching in front of the impeller inlet and up to the groove ends 11 is of the order of magnitude corresponding to the ratios of 0.005-0.02 x impeller inlet diameter.
  • the impeller inlet diameter usually corresponds to the impeller outer diameter D. In a semi-axial wheel, it is correspondingly smaller. And in a closed impeller, it corresponds to the diameter to the inner diameter of a cover plate. 7
  • the detachment line SL 2 skip over the closed annular wall surface 12 and reaches the wall surface 6 provided with grooves 10.
  • the limit of an axial expansion of the partial load vortex PLV which then adjusts itself is represented by the detachment line SL 3 .
  • FIG. 7 A section along the line A - A of Fig. 6 , within the grooves 10, the formation of many small energy dissipating vortex systems 13 is shown.
  • the reason for the many small vortices systems 13 is the circumferential component c ux part load vortex flow, the tangent to the groove direction.
  • FIG. 8 corresponds to the dot-dashed curve of the QH curve of a centrifugal pump without grooves in the suction channel. From the designated operating point Q PLV , the QH curve has a significant kink in the characteristic curve. The head goes down to smaller amounts. The reason for this is the effect of a developing part-load vortex PLV.
  • the continuous QH curve shown has a rising curve without a characteristic kick. This is the characteristic curve of a centrifugal pump whose suction channel is provided with channels or grooves 10 ending at a distance in front of the impeller. The dash-dotted curve with the characteristic curve is due to the formation of a partial load vortex and the resulting impairment of the impeller inlet.
  • Fig. 9 are drawn in the associated NPSH curves.
  • the dot-dashed NPSH curve corresponds to a pump in whose suction channel 9 no grooves are arranged.
  • the solid curve shows a pump in the suction channel 9 a plurality of grooves 10 are arranged. Due to the greatly reduced by the grooves 10 in its action partial load vortex PLV NPSH behavior of such a pump is significantly improved. This NPSH progression no longer exceeds the predefined plant value NPSH A and therefore does not provide any NPSH-related operating limit Q min there.
  • the type of energy reduction of the partial load vortex PLV and the resulting reduced transient interaction result in improved flow conditions, in particular in the operating range around PLV, as a result of which the NPSH behavior is improved and a pump characteristic is stabilized.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Branch Pipes, Bends, And The Like (AREA)
  • Characterised By The Charging Evacuation (AREA)
  • Massaging Devices (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Claims (7)

  1. Pompe centrifuge, dans le boîtier de laquelle sont disposées une ou plusieurs roues mobiles de construction axiale ou semi-axiale, ouverte ou fermée et une conduite d'aspiration est disposée avant une première roue mobile, dans la surface de paroi de laquelle sont réalisées plusieurs rainures réparties sur la périphérie et s'étendant dans la direction de l'écoulement, caractérisée en ce que dans la paroi de boîtier (3) de la conduite d'aspiration (9) entre une entrée de roue mobile de la première roue mobile (2) et les extrémités immédiatement suivantes (11) des rainures (10), est réalisée une surface de paroi annulaire fermée (12), les rainures (10) étant en liaison fonctionnelle exclusivement avec l'espace dans la conduite d'aspiration.
  2. Pompe centrifuge selon la revendication 1, caractérisée en ce que les rainures (10) sont disposées entre des réalisations en forme de nervures de la paroi de boîtier (3).
  3. Pompe centrifuge selon la revendication 1 ou 2, caractérisée par un insert, en particulier un élément à paroi mince, annulaire, présentant des rainures (10) ou des nervures.
  4. Pompe centrifuge selon la revendication 1, 2 ou 3, caractérisée en ce que la surface de paroi annulaire fermée (12) présente une étendue axiale dépendant de l'intensité d'un tourbillon de charge partielle (PLV) d'un ordre de grandeur de 0,005 à 0,02 fois le diamètre d'entrée de la roue mobile.
  5. Pompe centrifuge selon l'une quelconque des revendications 1 à 4, caractérisée en ce que les longueurs des rainures (10) ou des nervures sont d'un ordre de grandeur de 0,03 à 0,5 fois le diamètre d'entrée de la roue mobile.
  6. Pompe centrifuge selon l'une quelconque des revendications 1 à 5, caractérisée en ce que les profondeurs (t) des rainures (10) ou la hauteur (h) des nervures sont d'un ordre de grandeur de 0,005 à 0,02 fois le diamètre d'entrée de la roue mobile.
  7. Pompe centrifuge selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le produit de la largeur des rainures b par le nombre de rainures n correspond à un rapport de n * b = 0 , 45 - 0 , 65 * π * D .
    Figure imgb0004
EP03813089A 2002-12-17 2003-10-23 Conduite d'aspiration Expired - Lifetime EP1573208B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
SI200331836T SI1573208T1 (sl) 2002-12-17 2003-10-23 Sesalni kanal
CY20101100699T CY1110708T1 (el) 2002-12-17 2010-07-26 Αγωγος εισαγωγης

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10258922 2002-12-17
DE10258922A DE10258922A1 (de) 2002-12-17 2002-12-17 Saugkanal
PCT/EP2003/011721 WO2004055381A1 (fr) 2002-12-17 2003-10-23 Conduite d'aspiration

Publications (2)

Publication Number Publication Date
EP1573208A1 EP1573208A1 (fr) 2005-09-14
EP1573208B1 true EP1573208B1 (fr) 2010-04-28

Family

ID=32403856

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03813089A Expired - Lifetime EP1573208B1 (fr) 2002-12-17 2003-10-23 Conduite d'aspiration

Country Status (13)

Country Link
US (1) US7798772B2 (fr)
EP (1) EP1573208B1 (fr)
JP (1) JP4312720B2 (fr)
CN (1) CN100507282C (fr)
AT (1) ATE466197T1 (fr)
CY (1) CY1110708T1 (fr)
DE (2) DE10258922A1 (fr)
DK (1) DK1573208T3 (fr)
ES (1) ES2344942T3 (fr)
PT (1) PT1573208E (fr)
SI (1) SI1573208T1 (fr)
WO (1) WO2004055381A1 (fr)
ZA (1) ZA200504431B (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090263238A1 (en) * 2008-04-17 2009-10-22 Minebea Co., Ltd. Ducted fan with inlet vanes and deswirl vanes
MX2011002665A (es) 2008-09-10 2011-07-28 Pentair Pump Group Inc Bomba centrifuga de multiples etapas, de alta eficiencia y metodo para ensamblado.
CN119196051B (zh) * 2024-10-29 2025-09-26 珠海格力电器股份有限公司 风筒及具有其的轴流风机

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1693352A (en) * 1922-12-06 1928-11-27 Westinghouse Electric & Mfg Co Dredger pump
DE2558840C2 (de) * 1975-12-27 1983-03-24 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Einrichtung zur Verminderung des Kavitationsverschleisses
DE7924976U1 (de) * 1979-09-03 1981-05-27 Klein, Schanzlin & Becker Ag, 6710 Frankenthal Einrichtung zur verbesserung des kavitationsverhaltens von kreiselpumpen.
US4781530A (en) * 1986-07-28 1988-11-01 Cummins Engine Company, Inc. Compressor range improvement means
CZ48394A3 (en) * 1993-03-04 1994-09-14 Abb Management Ag Radial-flow compressor with a flow-stabilizing casing
DE19510811A1 (de) * 1995-03-24 1996-09-26 Klein Schanzlin & Becker Ag Faser abweisende Wandflächengestaltung
US6527509B2 (en) * 1999-04-26 2003-03-04 Hitachi, Ltd. Turbo machines
DE60036336T2 (de) * 1999-07-15 2008-06-12 Hitachi Plant Technologies, Ltd. Turbomaschinen
JP3862137B2 (ja) * 2000-09-20 2006-12-27 淳一 黒川 ターボ形水力機械
US6920458B1 (en) * 2000-09-22 2005-07-19 Sas Institute Inc. Model repository
AU2001293115A1 (en) * 2000-09-27 2002-04-08 The Times Picayune Publishing Corporation Apparatus for conveying printed products to a hopper
DE10105456A1 (de) * 2001-02-07 2002-08-08 Daimler Chrysler Ag Verdichter, insbesondere für eine Brennkraftmaschine
EP1247991B1 (fr) * 2001-04-05 2005-10-12 Hitachi, Ltd. Pompe centrifugale
JP3872966B2 (ja) * 2001-06-29 2007-01-24 株式会社日立プラントテクノロジー 軸流形流体機械
US6767185B2 (en) * 2002-10-11 2004-07-27 Honeywell International Inc. Turbine efficiency tailoring

Also Published As

Publication number Publication date
PT1573208E (pt) 2010-07-20
ZA200504431B (en) 2006-05-31
SI1573208T1 (sl) 2010-08-31
CN100507282C (zh) 2009-07-01
ATE466197T1 (de) 2010-05-15
WO2004055381A1 (fr) 2004-07-01
US7798772B2 (en) 2010-09-21
CN1726347A (zh) 2006-01-25
US20050265866A1 (en) 2005-12-01
DE50312675D1 (de) 2010-06-10
ES2344942T3 (es) 2010-09-10
JP4312720B2 (ja) 2009-08-12
CY1110708T1 (el) 2015-06-10
DK1573208T3 (da) 2010-08-16
JP2006509948A (ja) 2006-03-23
EP1573208A1 (fr) 2005-09-14
DE10258922A1 (de) 2004-07-01

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