EP0170175B1 - Seitenkanalpumpe mit Kräfteausgleich - Google Patents

Seitenkanalpumpe mit Kräfteausgleich Download PDF

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Publication number
EP0170175B1
EP0170175B1 EP85109082A EP85109082A EP0170175B1 EP 0170175 B1 EP0170175 B1 EP 0170175B1 EP 85109082 A EP85109082 A EP 85109082A EP 85109082 A EP85109082 A EP 85109082A EP 0170175 B1 EP0170175 B1 EP 0170175B1
Authority
EP
European Patent Office
Prior art keywords
impeller
lateral
channels
housing
inlet
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
EP85109082A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0170175A3 (en
EP0170175A2 (de
Inventor
Friedrich Schweinfurter
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.)
Intrasco Sa International Trading And Shipping C
Original Assignee
Schweinfurter Friedrich
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 Schweinfurter Friedrich filed Critical Schweinfurter Friedrich
Priority to AT85109082T priority Critical patent/ATE64772T1/de
Publication of EP0170175A2 publication Critical patent/EP0170175A2/de
Publication of EP0170175A3 publication Critical patent/EP0170175A3/de
Application granted granted Critical
Publication of EP0170175B1 publication Critical patent/EP0170175B1/de
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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/003—Regenerative pumps of multistage type
    • F04D5/005—Regenerative pumps of multistage type the stages being radially offset

Definitions

  • the invention relates to a side channel pump with a housing with a housing inlet and a housing outlet, in which the radial forces generally acting on the impeller shaft in side channel pumps are compensated, so that the pump is suitable for generating high and very high pressures.
  • Multi-stage side channel pumps are particularly well suited for achieving high pressures with relatively low flow rates.
  • Multi-stage side channel pumps are particularly easy to set up if only one impeller is used which has a plurality of differently sized vane cell rings with relatively short blades on each side of the impeller.
  • the blade cells arranged on the outer circumference are separated from one another in the axial direction by a central web and work in a common side channel. Since the pressure in the pumped medium increases steadily from the inlet of the side channel to its outlet in the running direction, the resultant force component in the radial direction results from the pressure acting on the impeller. This radial force takes on considerable dimensions at high delivery pressures.
  • a side channel pump in which pressure pockets are arranged in the housing in order to compensate for these radial forces are connected to the suction and pressure sides of the pump.
  • the arrangement of the pressure pockets and the connecting lines is such that the pressure prevailing in the pressure pockets acts on a special part of the impeller provided for this purpose in such a way that the forces acting radially inward on the impeller are compensated for by the pumping process.
  • this solution requires additional regulating elements in the connecting lines in order to match the pressure conditions built up in the pressure pockets to the respective delivery head or the delivery pressure of the pump.
  • a side channel pump is known, the impeller of which has a blade ring with closed blade cells on each side, separate side channels being arranged opposite these blade rings, each having an inlet opening and an outlet opening and an interrupter.
  • the pumped medium flows in this pump in two separate feed streams via the side channels from the respective side channel inlet to the respective side channel outlet.
  • the radial forces mentioned at the outset also occur in this pump.
  • two-rotor side channel pumps are known in each case, in which the channels of one rotor are offset in the circumferential direction in relation to those of the other rotor in such a way that there is a radial force compensation between the rotors.
  • they are single-stage, double-flow pump units.
  • the two-stage process results from the axial series connection of two separate rotors with assigned working channels.
  • the present invention has for its object to improve a single-rotor high-pressure side channel pump so that the shaft of the impeller essentially only has to transmit or absorb torques.
  • a side channel pump with a housing with a housing inlet and a housing outlet, with an impeller on a shaft, with at least one blade ring with radially and axially open blade cells on the first and on the second side of the impeller, with side channels separated from one another by sealing gaps , each with inlet opening, outlet opening and interrupter, the inlet openings being connected to the housing inlet and the outlet opening being connected to the housing outlet for dividing and reuniting the conveying flows, and the side channels being arranged opposite the blade rings in such a way that a conveying medium is in two essentially from one another separate flow flows through the side channels from the respective side channel inlet to the respective side channel outlet with increasing pressure, which is characterized in that the inlet openings, the outlet openings and the breaker (s) of the first impeller side are (are) offset in the circumferential direction of the impeller by 180 ° to the corresponding elements of the other impeller side, that the two impeller sides and the associated side channels in the are essentially
  • the bearing of the shaft with the associated seal can be made smaller in a cost-effective manner without reducing the service life of the pump.
  • the smaller dimensions of the impeller shaft mean that an inner blade ring with a small diameter and correspondingly low peripheral speed can be provided during operation. Because the peripheral speed is low, the efficiency-reducing acceleration impact on the medium is reduced when entering the pump.
  • the arrangement according to the invention makes it possible to mount a large number of blade rings of different diameters with corresponding side channels, that is to say a large number of pumping elements connected in series, on a single impeller, which is because of the previously radial forces occurring was not possible and was avoided by dividing the pressure stages over several separately mounted impellers.
  • the solution according to the invention results in a further advantage in multi-stage impellers in that the individual blade rings can each be constructed with axially and radially open blade cells, the sealing between the conveying stages being effected by radial sealing gaps, so that the blade cell rings are at the theoretical minimum distances can be graduated.
  • This minimum gradation in turn reduces the above-described acceleration impact on the conveying medium from the entry of the one into the subsequent stage with its disadvantageous effects.
  • This option has also not been able to be used so far, since this construction results in very wide impellers which lead to undesirably large bearing distances.
  • the two impeller and side channel sides which are separated from one another in a sealing manner, have an inverse effect, i.e. the respective pressure build-up along the side channel circumference of one side is offset by 180 ° about the shaft axis, i.e. opposite to the other side channel side.
  • radial forces of equal magnitude are juxtaposed at each point on the side channel circumference, so that the radial forces which arise on both sides of the impeller are automatically compensated for without loss and without additional devices at each operating point of the pump.
  • the overturning moment which is generated by the opposite axial forces on the two impeller sides, runs opposite to the overturning moment, which acts on the two wheel sides due to the radial forces. If the depth of the impeller is dimensioned accordingly, torque can be equalized and thus an essentially force-free shaft (except for the torques).
  • the preferred embodiment of the pump shown in FIGS. 1 to 8 shows a two-stage, double-flow side channel pump with a radial final stage sealing gap 36 and consists of a housing 10 and an impeller 30.
  • the housing 10 is constructed in several parts and consists of a housing ring 11 with a housing inlet opening 12 and outlet opening 13 (Fig. 2), an end housing cover 14, a drive-side bearing cover 15 and the two side channel parts 16 and 16 '.
  • the side channels 17 and 17' are arranged with side channel inlet openings 18 and 18 ', side channel outlet openings 19 and 19', transfer channels 21 and 21 ', and the side channel breakers 20 and 20'.
  • the housing cover 14 and the bearing cover 15 are sealed in the housing ring 11 by round cord rings 24 and screwed to the housing ring 11 with housing screws 26 (indicated by center lines).
  • the side channel parts 16 and 16 ′ arranged in the housing 10 are sealed off from one another by a round cord ring 25 and are fixed in the axial direction by the housing cover 14 and bearing cover 15.
  • a shaft 28, which is sealed by packing rings 27, is mounted, which is set in rotation in the direction of the arrow (FIG. 2) by a drive motor, not shown, for example an electric motor.
  • the impeller 30 is fastened to the free end of the shaft 28 by means of a feather key 29.
  • the two-stage impeller 30 has blade cell rings 31, 31a on its first side, and blade cell rings 31 ', 31'a on its second side, which are formed from radially and axially open blade cells 32, 32a and 32', 32'a, respectively.
  • the conveying medium entering through the housing inlet opening 12 of the housing 10 divides in a distribution channel 23, which is incorporated into the housing 10, into two conveying streams which are separated into the side channel inlet openings 18 and 18 'via feed channels 37, 38 in the side channel parts 16 and 16'. reach.
  • the Side channel inlet openings 18 on one side of the impeller are offset by 180 ° about the shaft axis to the side channel inlet openings 18 'on the other side of the impeller.
  • the conveying medium entering the side channels 17, 17 'of the first stage reaches the blade cells 32, 32' of the blade cell rings 31, 31 'of the rotating impeller 30.
  • centrifugal forces form displacer flows, each in flow in a helically wound current path over the entire length of the side channels and alternately reenter the blade cells 32 and 32 'of the impeller 30.
  • energy of the blade cells 32, 32 'of the impeller 30 is transferred to the lower flow energy flow (pressure, speed), which flows more slowly in the side channel.
  • the conveyed medium enters the side channels 17a and 17'a of the second stage via transfer channels 21, 21', where the blade cell rings 31a and 31'a of the impeller 30 enter via the blade cells 32a and 32'a further pulse exchange, as described above for the first stage, takes place.
  • the conveyed medium passes via the side channel outlets 19 and 19 'in the side channel parts 16 and 16' into a feed channel 22 in the housing 10 and from there out of the housing through the outlet opening 13.
  • the pressure build-up in the side channels 17 and 17a of the side channel part 16 takes place inversely due to the angular offset (by 180 °) to the side channel part 16 'with side channels 17' and 17'a. This means that at any point on the circumference of the side channels 17 and 17a of the side channel part 16 in radial force acting on the shaft counteracts an amount of equal magnitude counterforce from each point of the circumference of the side channels 17 'and 17'a of the side channel part 16'.
  • the two impeller outer rings 31a and 31'a on the outside of the impeller are separated from one another by a relatively wide web, which thus forms a cylindrical outer surface of the impeller.
  • the two side channel parts 16, 16 ' together form an equally wide "web" between the two outer side channels 17a, 17'a, so that the two flow rates of the output stages are sealed from one another via a radial output stage sealing gap 36.
  • the sealing between the steps on the respective impeller sides takes place by means of axial intermediate step sealing gaps 33, 33.
  • FIGS. 9 and 10 only half cross-sections through impellers of further preferred embodiments are shown, the associated side channel parts having side channels, overflow channels, sealing gaps, etc. being designed in accordance with the embodiment described above, unless otherwise stated.
  • vane cell rings 31, 31a, 31b are arranged on one side of the impeller and vane cell rings 31 ', 31'a and 31'b are arranged on the other side, which side channels (indicated by dash-dotted lines) 17, 17a, 17b and 17 ', 17'a, 17'b are opposite.
  • the separating seal between the output stages 17b, 17'b on the two impeller sides takes place via axial output stage sealing gaps 34 and 34 ', which are arranged between the impeller 30 and the side channel parts 16, 16'.
  • the delivery flows are sealed both from stage to stage and from the two output stages to one another via radial sealing gaps 35, 35a, 35 ', 35'a and 36.
  • the diameters increase the blade cell rings only by the minimum possible amount, since the sealing from step to step is carried out essentially exclusively by radial gaps.
  • the fact that the peripheral speed of the blade cells only increases by a small amount from stage to stage results in only a small acceleration shock which reduces the efficiency of the pump when the conveying medium enters the next side channel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)
  • Cephalosporin Compounds (AREA)
  • Centrifugal Separators (AREA)
  • Paper (AREA)
  • Float Valves (AREA)
  • Fertilizing (AREA)
EP85109082A 1984-07-23 1985-07-19 Seitenkanalpumpe mit Kräfteausgleich Expired - Lifetime EP0170175B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85109082T ATE64772T1 (de) 1984-07-23 1985-07-19 Seitenkanalpumpe mit kraefteausgleich.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843427112 DE3427112A1 (de) 1984-07-23 1984-07-23 Seitenkanalpumpe mit kraefteausgleich
DE3427112 1984-07-23

Publications (3)

Publication Number Publication Date
EP0170175A2 EP0170175A2 (de) 1986-02-05
EP0170175A3 EP0170175A3 (en) 1987-06-03
EP0170175B1 true EP0170175B1 (de) 1991-06-26

Family

ID=6241341

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85109082A Expired - Lifetime EP0170175B1 (de) 1984-07-23 1985-07-19 Seitenkanalpumpe mit Kräfteausgleich

Country Status (7)

Country Link
US (1) US4678395A (cs)
EP (1) EP0170175B1 (cs)
JP (1) JPH0631634B2 (cs)
AT (1) ATE64772T1 (cs)
CS (1) CS258472B2 (cs)
DD (1) DD237533A5 (cs)
DE (2) DE3427112A1 (cs)

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6238891A (ja) * 1985-08-10 1987-02-19 Nippon Denso Co Ltd 再生ポンプ装置
JPH0762478B2 (ja) * 1987-12-28 1995-07-05 愛三工業株式会社 ウエスコ型ポンプ機構
JPH0330596U (cs) * 1989-07-31 1991-03-26
EP0465626A1 (de) * 1990-01-31 1992-01-15 Reihansl Maschinen + Pumpen Maschinen- U. Pumpenbau Gmbh Seitenkanalpumpe
DE4243225A1 (de) * 1992-12-19 1994-06-23 Pierburg Gmbh Brennstoffpumpe
US5310308A (en) * 1993-10-04 1994-05-10 Ford Motor Company Automotive fuel pump housing with rotary pumping element
ES2179152T3 (es) * 1995-03-31 2003-01-16 Bitron Spa Bomba de combustible periferica para vehiculos automoviles.
US5580213A (en) * 1995-12-13 1996-12-03 General Motors Corporation Electric fuel pump for motor vehicle
US5596970A (en) * 1996-03-28 1997-01-28 Ford Motor Company Fuel pump for an automotive fuel delivery system
US5702229A (en) * 1996-10-08 1997-12-30 Walbro Corporation Regenerative fuel pump
JPH11218087A (ja) * 1997-11-03 1999-08-10 Walbro Corp 力均衡横みぞ型燃料ポンプ
US6280157B1 (en) 1999-06-29 2001-08-28 Flowserve Management Company Sealless integral-motor pump with regenerative impeller disk
DE10013907A1 (de) * 2000-03-21 2001-09-27 Mannesmann Vdo Ag Förderpumpe
DE10019911A1 (de) 2000-04-20 2001-10-25 Mannesmann Vdo Ag Förderpumpe
DE10030604A1 (de) 2000-06-21 2002-01-03 Mannesmann Vdo Ag Seitenkanalpumpe
DE10048695A1 (de) 2000-09-30 2002-04-11 Leybold Vakuum Gmbh Pumpe als Seitenkanalpumpe
DE10062451A1 (de) * 2000-12-14 2002-06-20 Siemens Ag Förderpumpe
US7037066B2 (en) * 2002-06-18 2006-05-02 Ti Group Automotive Systems, L.L.C. Turbine fuel pump impeller
GB0215709D0 (en) * 2002-07-05 2002-08-14 Boc Group Plc A regenerative fluid pump and stator for the same
DE102004057991B4 (de) * 2004-12-01 2018-03-29 Tni Medical Ag Gehäuseschale, Laufrad sowie Seitenkanalverdichter
US7632060B2 (en) * 2005-01-24 2009-12-15 Ford Global Technologies, Llc Fuel pump having dual flow channel
DE102006053933A1 (de) * 2006-11-15 2008-05-21 Siemens Ag Seitenkanalpumpe
DE102007026533A1 (de) * 2007-06-08 2008-12-11 Continental Automotive Gmbh Kraftstoffpumpe
CN101368578B (zh) * 2007-08-17 2011-05-18 简焕然 再生式泵的流道结构
US9249806B2 (en) 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump
US20140072425A1 (en) * 2012-09-10 2014-03-13 Delphi Technologies, Inc. Multi-channel fuel pump
CN110748504B (zh) * 2019-11-15 2025-01-24 四川省自贡工业泵有限责任公司 侧流道泵体的水力结构
GB2594145B (en) * 2020-03-04 2024-07-31 Eaton Intelligent Power Ltd Single wheel multi-stage radially-layered regenerative pump

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US2340787A (en) * 1941-04-11 1944-02-01 Linde Air Prod Co Means for balancing rotary pumps
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DE967363C (de) * 1951-07-24 1957-11-07 Siemens Ag Mehrstufige Fluegelradpumpe
JPS4517966Y1 (cs) * 1969-11-25 1970-07-22
DE2105121A1 (de) * 1971-02-04 1972-08-10 Klein Schanzlin & Becker Ag Wirbelpumpe
DE2112762A1 (de) * 1971-03-17 1972-10-12 Klein Schanzlin & Becker Ag Seitenkanalpumpe,insbesondere Wirbelpumpe
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DE3014425C2 (de) * 1980-04-15 1986-06-12 Friedrich 8541 Röttenbach Schweinfurter Seitenkanalpumpe
DE3118533A1 (de) * 1981-05-09 1982-12-02 Robert Bosch Gmbh, 7000 Stuttgart Aggregat zum foerdern von fluessigkeiten
DE3128374A1 (de) * 1981-07-17 1983-02-17 Friedrich 8541 Röttenbach Schweinfurter Radialschaufelunterstuetzte seitenkanalpumpe
JPS58222997A (ja) * 1982-06-21 1983-12-24 Nippon Denso Co Ltd ポンプ装置
DE3321241A1 (de) * 1983-06-11 1984-12-13 Robert Bosch Gmbh, 7000 Stuttgart Aggregat zum foerdern von kraftstoff aus einem vorratstank zur brennkraftmaschine, insbesondere eines kraftfahrzeugs
JPH119991A (ja) * 1997-06-23 1999-01-19 Nippon Gasket Co Ltd 耐熱性多孔質シート及びその製造方法
JPH119990A (ja) * 1997-06-24 1999-01-19 Daido Hoxan Inc 窒素吸着剤およびその使用方法

Also Published As

Publication number Publication date
DE3583312D1 (de) 1991-08-01
ATE64772T1 (de) 1991-07-15
CS536285A2 (en) 1988-01-15
DE3427112A1 (de) 1986-01-23
JPS6187996A (ja) 1986-05-06
EP0170175A3 (en) 1987-06-03
DD237533A5 (de) 1986-07-16
CS258472B2 (en) 1988-08-16
EP0170175A2 (de) 1986-02-05
US4678395A (en) 1987-07-07
JPH0631634B2 (ja) 1994-04-27

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