EP0081456B1 - Freistrompumpe - Google Patents

Freistrompumpe Download PDF

Info

Publication number
EP0081456B1
EP0081456B1 EP82810507A EP82810507A EP0081456B1 EP 0081456 B1 EP0081456 B1 EP 0081456B1 EP 82810507 A EP82810507 A EP 82810507A EP 82810507 A EP82810507 A EP 82810507A EP 0081456 B1 EP0081456 B1 EP 0081456B1
Authority
EP
European Patent Office
Prior art keywords
free
wheel chamber
limitation
tongue
casing
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
Application number
EP82810507A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0081456A1 (de
Inventor
Hagen Renger
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.)
EMILE EGGER AND CO AG
Original Assignee
EMILE EGGER AND CO 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 EMILE EGGER AND CO AG filed Critical EMILE EGGER AND CO AG
Priority to AT82810507T priority Critical patent/ATE12815T1/de
Publication of EP0081456A1 publication Critical patent/EP0081456A1/de
Application granted granted Critical
Publication of EP0081456B1 publication Critical patent/EP0081456B1/de
Expired 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/2244—Free vortex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous

Definitions

  • the present invention relates to a free-flow pump, in the housing of which, to the side of the impeller arranged in a wheel chamber, there is a free flow space with free passage between the suction and pressure ports, the largest diameter of which exceeds that of the outer, radial limitation of the wheel chamber, and a housing tongue being formed on the pressure port outlet is.
  • Known pumps of this type (US Pat. No. 3,171,357) generally show an unfavorable throttle curve profile, especially if they have a relatively large, free passage, ie if the condition is met:
  • the cause of this is malfunctions at partial load in an area that extends from the housing tongue to about 40 in the direction of rotation of the impeller, which influence the impeller flow.
  • the throttle curve can be stabilized somewhat by smaller impeller outlet angles, but due to the associated reduction in the blade load, losses in head and efficiency cannot be avoided.
  • This novel shape of the housing means that excess liquid escaping from the pressure port at partial load can be largely carried in the outer region of the housing and thus kept away from the impeller. In this way, the influences that lead to instability of the throttle curve and to losses in the head and efficiency can be contained. This also makes it possible to design the impeller with relatively large blade angles, as a result of which particularly good efficiencies can be achieved. In addition to stabilizing the throttle curve, it is possible to achieve improvements in the delivery head when the slide valve is closed and the efficiency in the partial load range.
  • the aforementioned, preferred wheel chamber limitation according to the invention can be formed by a solid housing part or else by a rib projecting axially into the flow space, the axial height of which decreases from the tongue area.
  • the wheel chamber delimitation is preferably drawn to the housing tongue, decreasing in the direction of rotation, into the free flow space.
  • the housing will be designed in such a way that the axial width of the part of the free flow space lying radially outside the wheel chamber boundary increases monotonously, continuously, from the tongue area to the pressure port outlet, for example of at least approximately 55% of the housing width in the tongue area.
  • the axial width of the part of the flow space lying radially outside the wheel chamber boundary can preferably increase continuously from at least approximately 55% of the housing width in the tongue area.
  • the stabilizing effect of the design of the housing allows greater freedom in the overall design of the pump, in particular in the design of the impeller. This makes it possible to use identical impellers with housings of different nominal sizes of the suction nozzle in a preferred use of the pump in a pump program. In addition to the advantages mentioned with regard to the pump characteristics, economic advantages can also be realized.
  • the pump housing 1 has a suction nozzle 2 with a narrowed point 3 at the entry into the free flow space 4 of the pump and a tangentially arranged pressure nozzle 5 on.
  • the free flow space 4 forms a free passage between the suction port and the pressure port, such that a ball that can enter through the suction port can pass through the free flow space to the pressure port 5 laterally of the impeller 6 with the blades 7.
  • Such free-flow pumps and their mode of operation are known per se and require no further explanation.
  • the impeller 6 is located in a wheel chamber, the radial boundary of which has a cylindrical region 9 in the region of the impeller disk and the rear blades 8 and a slightly frustoconical region 10 in the region of the blades or wheel channels.
  • the peculiarity of the design of this wheel chamber or of the free flow space is that the frustoconical region of the outer radial wheel chamber boundary is drawn into the flow space to an uneven extent over the circumference of the housing.
  • the region 10 of the wheel chamber delimitation is advanced much further into the free flow space at the top than at the bottom. This design is expressed even more clearly in FIGS. 3 to 6, in which the cross-sectional shapes of the housing wall in the four sectional planes 111 to VI according to FIG.
  • an outer part 4 'of the flow space remains radially outside the wheel chamber boundary, the axial width of which preferably increases continuously or monotonously from the housing tongue to the outlet of the pressure port.
  • the width of the outer part 4 'of the flow space can preferably be about 55% of the free housing width between the impeller and the opposite end wall of the housing in the tongue region.
  • the impeller 6 has relatively weakly curved blades 7, so that there is a relatively large blade outlet angle 82 of approximately 60 °.
  • a relatively large blade angle 82 of approximately 60 °.
  • Such relatively large blade angles between 40 and 90 ° can be selected, which allows an improvement in the efficiency and the head, without having to accept an unacceptable instability of the throttle curve.
  • This also applies to pumps with a relatively large free passage in accordance with the condition mentioned at the beginning. Thanks to the housing design described, efficiency improvements in the partial load range are achieved by around four points with an optimal impeller design and with a clearly improved course of the throttle curve. It will also be possible to use identical impellers for pumps of different sizes with the same diameter.
  • FIGS. 7 to 12 show the second embodiment of the pump, corresponding parts being identified in the same way as in FIGS. 1 and 2.
  • the difference is essentially that the advanced impeller limitation is not on a solid housing part, but on one away from the tongue area rib 12 projecting into the free flow space is formed. This creates an axially further part 4 'of the flow space, in particular in the tongue area outside of this rib 12, which brings certain additional advantages.
  • the impeller limitation which is drawn into the free flow space, is formed on a one-piece pump housing.
  • a curved, wedge-shaped insert in an otherwise rotationally symmetrical pump housing and thus to achieve the desired design of the wheel chamber delimitation or of the outer part of the free flow space.
  • Such an insert could possibly be formed by a suitably shaped sheet.
  • the cross-sectional change of the pump housing from the housing tongue to the pressure port outlet is essentially constant or monotonous.
  • this cross-sectional change could extend from the tongue area only over a certain part of the circumference, for example over 90 to 180 °.
  • the tongue area, in which the beginning of the advanced impeller limitation or the narrowing of the flow space begins should in any case be limited to the first half of the first quadrant from the housing tongue, preferably to an angular range of approximately 15 °.
  • the start of the preferred impeller limitation could be shifted by up to about 15 ° in the direction of rotation compared to that shown in the exemplary embodiments.
  • another, e.g. B. cylindrical or conical impeller limit can be provided over the entire axial depth. While in the illustrated preferred embodiments, the wheel chamber limitation completely surrounds the impeller, an embodiment would also be possible in which, for. B. the impeller in the area of the discharge port not completely, d. that is, not covered in its entire axial width.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Cyclones (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • Glass Compositions (AREA)
EP82810507A 1981-12-08 1982-11-26 Freistrompumpe Expired EP0081456B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82810507T ATE12815T1 (de) 1981-12-08 1982-11-26 Freistrompumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH7825/81A CH654628A5 (de) 1981-12-08 1981-12-08 Freistrompumpe.
CH7825/81 1981-12-08

Publications (2)

Publication Number Publication Date
EP0081456A1 EP0081456A1 (de) 1983-06-15
EP0081456B1 true EP0081456B1 (de) 1985-04-17

Family

ID=4331010

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82810507A Expired EP0081456B1 (de) 1981-12-08 1982-11-26 Freistrompumpe

Country Status (13)

Country Link
US (1) US4475868A (enrdf_load_stackoverflow)
EP (1) EP0081456B1 (enrdf_load_stackoverflow)
JP (1) JPS58104390A (enrdf_load_stackoverflow)
AT (1) ATE12815T1 (enrdf_load_stackoverflow)
AU (1) AU553254B2 (enrdf_load_stackoverflow)
CA (1) CA1215581A (enrdf_load_stackoverflow)
CH (1) CH654628A5 (enrdf_load_stackoverflow)
CS (1) CS238386B2 (enrdf_load_stackoverflow)
DD (1) DD203100A5 (enrdf_load_stackoverflow)
DE (1) DE3263170D1 (enrdf_load_stackoverflow)
ES (1) ES8400806A1 (enrdf_load_stackoverflow)
MX (1) MX157817A (enrdf_load_stackoverflow)
ZA (1) ZA828668B (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2683945B1 (en) 2011-03-08 2015-10-21 Egger Pumps Technology AG Free-flow pump

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1528035A1 (ru) * 1987-02-18 1994-10-30 А.И. Золотарь Центробежный насос
US4872809A (en) * 1987-03-06 1989-10-10 Giw Industries, Inc. Slurry pump having increased efficiency and wear characteristics
US5100288A (en) * 1990-06-15 1992-03-31 Atsco, Inc. Slurry pump apparatus
US5114312A (en) * 1990-06-15 1992-05-19 Atsco, Inc. Slurry pump apparatus including fluid housing
US5076758A (en) * 1990-07-18 1991-12-31 Ingersoll-Rand Company Centrifugal pumps
US5277232A (en) * 1992-04-21 1994-01-11 Borsheim Lewis A Positive discharge contaminant evacuator
SE9303475L (sv) * 1993-10-22 1994-11-28 Flygt Ab Itt Pumphus för virvelströmspump
US6428268B1 (en) * 1999-08-20 2002-08-06 Giw Industries, Inc. Pump with auxiliary impeller vane inlet device
US6361270B1 (en) 1999-09-01 2002-03-26 Coltec Industries, Inc. Centrifugal pump for a gas turbine engine
US6231311B1 (en) * 1999-09-17 2001-05-15 Fasco Industries, Inc. Method and apparatus for providing dilution air to a blower motor
US6398512B2 (en) * 1999-09-17 2002-06-04 Dale Stewart Method and apparatus for cooling and expelling exhaust gases from a water heater
US6579060B1 (en) * 1999-09-28 2003-06-17 Royal Appliance Mfg. Co. Impeller and housing assembly with reduced noise and improved airflow
US6171054B1 (en) * 1999-09-28 2001-01-09 Royal Appliance Mfg. Co. Impeller housing with reduced noise and improved airflow
US6629814B2 (en) * 2000-08-22 2003-10-07 Henry Filters, Inc. Low profile pump
US6602058B1 (en) 2000-09-12 2003-08-05 Fasco Industries, Inc. Vented backplate impeller water heater blower and method of mixing dilution air
US6966749B2 (en) * 2004-01-07 2005-11-22 California Acrylic Industries Pump with seal rinsing feature
US7093589B2 (en) * 2004-01-08 2006-08-22 Visteon Global Technologies, Inc. Apparatus for increasing induction air flow rate to a turbocharger
US20050265865A1 (en) * 2004-06-01 2005-12-01 Buzz Loyd Pump with turbulence inducing tab
CA2517743C (en) 2004-09-01 2013-07-23 Aos Holding Company Blower and method of conveying fluids
US8025478B2 (en) * 2005-06-16 2011-09-27 Egger Pumps Technology Ag Centrifugal pump
US20070036660A1 (en) * 2005-08-10 2007-02-15 Envirotech Pumpsystems, Inc. Low-profile impeller bolt
DE202006005073U1 (de) * 2006-03-28 2006-06-08 Ksb Aktiengesellschaft Kreiselpumpe mit Freistromlaufrad
JP2007270631A (ja) * 2006-03-30 2007-10-18 Japan Servo Co Ltd 遠心ファン
JP4822336B2 (ja) * 2006-07-27 2011-11-24 国土交通省中部地方整備局長 立軸ポンプの管理運転方法
NO332696B1 (no) * 2011-03-09 2012-12-10 Agr Subsea As Rotodynamisk pumpe for vekslende leveringsmengde
JP5866836B2 (ja) * 2011-07-13 2016-02-24 株式会社Ihi 遠心圧縮機
DE102021110936A1 (de) 2021-04-28 2022-11-03 Herborner Pumpentechnik Gmbh & Co Kg Pumpenlaufrad, Gehäuseelement und Pumpe hiermit

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3171357A (en) * 1961-02-27 1965-03-02 Egger & Co Pump

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1046502B (de) * 1955-02-15 1958-12-11 Roger Bert Zentrifugalpumpe, insbesondere fuer Waschmaschinen
DE1528684A1 (de) * 1965-06-24 1970-01-29 Eta Corp Kreiselpumpe
US3542496A (en) * 1968-06-19 1970-11-24 Maytag Co Dishwasher pump
US3547554A (en) * 1969-04-07 1970-12-15 Russell J Willette Centrifugal pump
BE757973A (nl) * 1969-11-03 1971-04-01 Robot Pompen Nv Rotatiepomp
US3741679A (en) * 1971-09-17 1973-06-26 Blue Co John Centrifugal pump
US3918829A (en) * 1974-06-19 1975-11-11 Warren Pumps Inc Low pressure-pulse kinetic pump
US4213742A (en) * 1977-10-17 1980-07-22 Union Pump Company Modified volute pump casing
FR2413571A1 (fr) * 1977-12-30 1979-07-27 Lab Perfectionnements aux machines dans lesquelles un fluide est mis en rotation
GB2057567A (en) * 1979-08-24 1981-04-01 Borg Warner Expanding scroll diffuser for radial flow impeller
US4307995A (en) * 1980-02-01 1981-12-29 Rockwell International Corporation Vaneless multistage pump

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3171357A (en) * 1961-02-27 1965-03-02 Egger & Co Pump

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"DIE KREISELPUMPEN" C. PFLEIDERER 4. AUFLAGE *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2683945B1 (en) 2011-03-08 2015-10-21 Egger Pumps Technology AG Free-flow pump

Also Published As

Publication number Publication date
DE3263170D1 (en) 1985-05-23
AU553254B2 (en) 1986-07-10
EP0081456A1 (de) 1983-06-15
CS238386B2 (en) 1985-11-13
ZA828668B (en) 1983-09-28
CH654628A5 (de) 1986-02-28
MX157817A (es) 1988-12-15
CA1215581A (en) 1986-12-23
JPS58104390A (ja) 1983-06-21
ES517773A0 (es) 1983-11-16
AU9085082A (en) 1983-06-16
CS864682A2 (en) 1984-03-20
ATE12815T1 (de) 1985-05-15
JPH0472079B2 (enrdf_load_stackoverflow) 1992-11-17
DD203100A5 (de) 1983-10-12
US4475868A (en) 1984-10-09
ES8400806A1 (es) 1983-11-16

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