EP0070530A1 - Pompe à canal latéral ayant des pales radiales de secours - Google Patents

Pompe à canal latéral ayant des pales radiales de secours Download PDF

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Publication number
EP0070530A1
EP0070530A1 EP82106382A EP82106382A EP0070530A1 EP 0070530 A1 EP0070530 A1 EP 0070530A1 EP 82106382 A EP82106382 A EP 82106382A EP 82106382 A EP82106382 A EP 82106382A EP 0070530 A1 EP0070530 A1 EP 0070530A1
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EP
European Patent Office
Prior art keywords
impeller
pump according
flow
radial
housing
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.)
Withdrawn
Application number
EP82106382A
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German (de)
English (en)
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0070530A1 publication Critical patent/EP0070530A1/fr
Withdrawn legal-status Critical Current

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    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more 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
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative 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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • F04D5/003—Regenerative pumps of multistage type

Definitions

  • the invention relates to a side channel pump with a housing and a shaft sealed therein and an impeller attached to the latter, and a suction opening in the housing, from which the delivery flow leads through an open or closed radial vane region to a downstream flow duct and then via at least one Side channel and this corresponding blade ring of the impeller reaches an outlet opening in the housing.
  • the pumping medium entering through the suction opening of the impeller with a low flow velocity reaches the rotating blades leading outwards in the radial direction, with energy being transferred to the pumping medium by the impeller torque.
  • the pumped medium is accelerated centrifugally and enters the subsequent mostly spiral flow channel and then the subsequent side channel or channels.
  • the centrifugal force field which forms in the blade cells of the rotating blade rings triggers a displacement flow which moves in a current path which is helically wound in the circumferential direction.
  • the pumped medium passes through the energy transfer area of the impeller blade cells several times from the start of the rare channel to the end of the side channel, which means that energy is transferred in the side channel by the exchange of impulses to the volume flow of lower energy.
  • centrifugal pumps work with liquid either according to the principle of normal suction centrifugal pumps with a low step head or the principle of gas-carrying, self-priming side channel pumps with a large step height. Both systems have advantages and disadvantages, which has led to different designs.
  • a normal suction stage within a centrifugal pump is preceded or followed by a side channel stage for the purpose of self-priming or self-venting, e.g. is shown in GB-PS 1 152 728 or DE-AS 1 152 887.
  • the side channel stage is preceded by a normal suction centrifugal stage in order to allow the pumped medium to enter the side channel area pre-accelerated.
  • This counteracts the acceleration surges that occur in the entry region of the side channel vane cells and the associated partial evaporation risk of the delivery medium.
  • This undesired partial evaporation particularly in the case of low-boiling media, leads to a considerable deterioration in the efficiency of the pump and increases the risk of cavitation.
  • This special version can only be evaluated as a partial solution of a combination of the two types of pumps, since it represents an unfavorable combination of the two systems - above all due to flow-related reasons.
  • the invention is therefore based on the object of developing a construction which is simple and uncomplicated, flow-efficient, self-priming centrifugal pump and which optimally combines both delivery systems in one housing unit with an impeller.
  • the impeller contains at least one circular row of axially or axially and radially open blade cells and carries on or between the impeller parts radial vanes which emanate from at least one suction opening coaxial to the impeller and that adjoin the radial vanes in the circumferential direction at least one flow channel is arranged, which is connected in the flow direction by at least one overhead line channel to the immediately following side channel or channels, to which or opposite a blade ring on the or the impeller parts is assigned.
  • the blade rings preferably have blade cells which are open in the axial direction. Blade rings with axially and radially open blade cells are also advantageous.
  • the flow channel following the radial blade region in the circumferential direction preferably has a spiral-shaped outer contour increasing cross section. A concentric contour of constant cross section is also advantageous.
  • the impeller can be provided, for example, with axial suction openings on both sides and a partition wall both in the radial blade region and in the region of the downstream flow channel.
  • the construction according to the invention has the advantage that a medium entering the axis at a very low flow velocity passes directly from the normally aspirating centrifugal part and into the side channel part in the most aerodynamic manner without leaving the impeller and housing unit. As a result, the friction and vortex losses, which occur markedly in the known pumps of this type, are kept low.
  • the radial impeller In order to keep this acceleration shock as low as possible, it is not sufficient to switch "any" radial impeller in front of a side channel impeller, as is shown in DE-OS 2 112 980.
  • the radial impeller must rather, as in the Invention pump, its diameter must be matched to the other conveyor system. Only then can such high degrees of filling of the side channel vane cells be achieved as are possible in the device shown. With the filling level, the efficiency of the pump naturally increases and its holding pressure level (NPSH value) decreases.
  • the diameter of the radial blade wheel is preferably larger than that of the blade cell ring.
  • a pump according to the invention can be operated at relatively high peripheral speeds of the impeller. After the delivery rate of the radial pump part also increases with increasing speed or diameter of the impeller, the above-mentioned acceleration shock with all its disadvantageous effects is avoided up to the relatively high peripheral speed. High delivery pressures can be achieved due to high peripheral speeds.
  • the pump according to the invention can therefore advantageously be used for high-pressure generation, which is otherwise only possible with multi-stage and therefore extremely complex production systems without their efficiency being significantly reduced.
  • the centrifugal pump shown in FIGS. 4 to 4 has a single-flow flow in its closed radial vane part and a double-flow flow in its side channel part and consists of a Housing 10, the flow housings 27 and 28 and the impeller 20, 20 '.
  • the housing is composed of an annular housing part 11 with a base part 12, the inlet opening 13 and the outlet opening 14, a bearing cover 15 which is sealed off from the housing part 11 by an O-ring 16.
  • the impeller 20, 20 ' is fastened to the free end of the shaft 18 by means of a threaded pin 19.
  • the blade rings 23, 23 ', which form the blade cells 24, are located in the impeller 20, 20', with a side channel 29, 29 'opposite them, which are incorporated in the flow channel housings 27 and 28.
  • an overhead line channel 34 is arranged which divides the delivery flow coming from the radial blades 25 and to the two side channels 29, 29 '.
  • the pumped medium enters the suction opening 26 coaxially with the impeller 20, 20 ′ at a low flow rate. Due to the centrifugal force of the rotating impeller 20, 20 'which forms in the radial blades 25, the delivery medium is increasingly accelerated radially to the periphery and flows into the immediately radially adjoining spiral flow channel 32.
  • the transfer channel 34 arranged at the end of the flow channel 32 divides the delivery flow into two parts and directs these two partial streams to the immediately adjacent side channels 29, 29 'and Blade rings 23, 23 'too.
  • a centrifugal force forms a displacer flow in the blade cells 24 of the blade rings 23, 23 ', which flows in a helically winding current path over the entire length of the side channel and alternately re-enters the blade cells 24 of the impeller 20, 20'.
  • the drive energy is transferred to the delivery flow, which flows more slowly in the side channel, i.e. has a lower energy state, by means of pulse exchange.
  • the pumped medium emerges from the side channel region via a connection opening 33 machined into the flow channel housings 27 and 28 and leaves the housing 10 through the outlet opening 14.
  • the redistribution channel 30 causes the delivery medium to be recompressed with a subsequent expansion process at the beginning of the side channel in the circumferential direction, thereby accelerating the formation of the displacer flow and thus increasing the momentum transfer.
  • the pump design according to FIG. 5 differs from the one described above in that the blade rings 23, 23 'are open radially and axially and the side channels 29, 29' are designed accordingly.
  • FIG. 6 shows a single-flow centrifugal pump with radial blades 25 open at the end with flow channel 32 and only one blade ring 23 with side channel 29.
  • the impeller 20, 20 ' is divided by a partition 58 so that two separate single-flow delivery systems, each with their own axial suction openings 26, 26', closed radial blades 25, 25 'and side channels 29, 29 'arise.
  • the media entering through the two radial inlet openings 13, 13 'in the housing 10 are sucked in through the axial suction openings 26, 26' of the impeller halves 20, 20 ', flow separately through the radial blades 25, 25' and reach the subsequent spiral flow channel, which is from the partition 58 is divided into two flow channel parts 32, 32 'and sealed by the sealing gap 59.
  • the two delivery media still pass separately through the adjoining side channels 29 and 29 'and leave them through the connecting opening 33, 33' in the flow housings 27 and 28.
  • the two delivery flows combine in an intermediate chamber 63 before they pass through the outlet opening 14 in the housing 10 emerge.
  • FIG. 8 shows a centrifugal pump which is single-flow in the low-pressure part and double-flow in the high-pressure part, in which the radial blades 25 are open at the end, and the two rocking rings 23, 23 'are separated from one another by a central web 77, are arranged radially and axially open.
  • the pumping medium entering through the axial inlet opening 13 in the housing 10 is sucked in by the radial blades 25 and after it has passed through the spiral-shaped fault channel 32 through an immediately adjacent overhead line channel 75 fed to the side channel 29. After the energy exchange has taken place, the medium leaves the side channel 29 via the radial outlet channel 79 and flows through the outlet opening 14 in the housing 10.
  • the conveyed medium flows from the radial vane region into the flow channel 32, 32 ', and reaches the first side channels 29, 29', which correspond to the vane rings 23, 23 'with the larger diameters, through transfer channels 34, 34'.
  • the medium reaches the inner side channels 29, 29 ′ further accelerated through upstream channels 35, which preferably have cross-sectional areas that are also larger than the outer ones, and the blade cells assigned to them also have larger volumes than the blade cells of the outer blade rings.
  • the medium then arrives from the inner delivery system via the connecting openings 33, 33 'to the outlet opening 14.
  • a pump construction is also possible in which the delivery medium coming from the xadial system is first supplied to the inner and then the outer side channel system.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP82106382A 1981-07-17 1982-07-15 Pompe à canal latéral ayant des pales radiales de secours Withdrawn EP0070530A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3128374 1981-07-17
DE19813128374 DE3128374A1 (de) 1981-07-17 1981-07-17 Radialschaufelunterstuetzte seitenkanalpumpe

Publications (1)

Publication Number Publication Date
EP0070530A1 true EP0070530A1 (fr) 1983-01-26

Family

ID=6137183

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82106382A Withdrawn EP0070530A1 (fr) 1981-07-17 1982-07-15 Pompe à canal latéral ayant des pales radiales de secours

Country Status (2)

Country Link
EP (1) EP0070530A1 (fr)
DE (1) DE3128374A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2134598A (en) * 1983-02-02 1984-08-15 Bosch Gmbh Robert Fuel pumps for internal- combustion engines
EP0170175A2 (fr) * 1984-07-23 1986-02-05 Friedrich Schweinfurter Pompe régénérative avec équilibrage des forces
GB2205357A (en) * 1987-06-03 1988-12-07 Stuart Turner Ltd Pump arrangement
EP0143684B1 (fr) * 1983-10-25 1989-12-20 Bertin & Cie Machine de compression d'un fluide, à plusieurs étages de compression en série
GB2257750A (en) * 1991-07-13 1993-01-20 Grosvenor Pumps Limited "rotary pumps"
EP1033493A2 (fr) * 1997-11-25 2000-09-06 Zakrytoe Aktsionernoe Obschestvo " Novomet-Perm" Etage de pompe immergee a plusieurs etages
WO2007115471A1 (fr) * 2006-03-28 2007-10-18 Wanzhi Jiang Pompe centrifuge à ailettes à canaux multiples
WO2012113700A1 (fr) * 2011-02-22 2012-08-30 Gardner Denver Deutschland Gmbh Configuration de machine à canaux latéraux
WO2019120550A1 (fr) * 2017-12-21 2019-06-27 Pierburg Gmbh Ventilateur à canal latéral, notamment ventilateur à aire secondaire pour moteur à combustion interne
CN110748504A (zh) * 2019-11-15 2020-02-04 四川省自贡工业泵有限责任公司 侧流道泵体的水力结构
WO2022253496A1 (fr) * 2021-06-04 2022-12-08 Robert Bosch Gmbh Dispositif d'acheminement pour système de pile à combustible, servant à acheminer et/ou à recycler un milieu gazeux, en particulier de l'hydrogène

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0567874B1 (fr) * 1992-04-27 1995-09-06 Gebrüder Becker GmbH & Co. Machine à courant pour la compression d'un gaz
DE4315448A1 (de) * 1992-05-19 1993-12-23 Lederle Pumpen & Maschf Peripheralrad-Pumpe
DE102018219995A1 (de) 2018-11-22 2020-05-28 Robert Bosch Gmbh Seitenkanalverdichter für ein Brennstoffzellensystem zur Förderung und/oder Verdichtung von einem gasförmigen Medium
DE102022001696A1 (de) 2022-05-13 2023-11-16 Truma Gerätetechnik GmbH & Co. KG Zweistufige Pumpe

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD4862A (fr) *
DE368715C (de) * 1923-02-09 Hermann Prang Kreiselpumpe
US1805765A (en) * 1928-03-31 1931-05-19 Ames Pump Company Inc Centrifugal pump
GB582355A (en) * 1944-06-30 1946-11-13 John Southern Improvements in and relating to self-priming centrifugal pumping plant
US2426539A (en) * 1945-08-21 1947-08-26 W H Martin Compound rotary pump
DE2112980A1 (de) * 1971-03-17 1972-09-21 Klein Schanzlin & Becker Ag Seitenkanalpumpe,insbesondere Wirbelpumpe

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD4862A (fr) *
DE368715C (de) * 1923-02-09 Hermann Prang Kreiselpumpe
US1805765A (en) * 1928-03-31 1931-05-19 Ames Pump Company Inc Centrifugal pump
GB582355A (en) * 1944-06-30 1946-11-13 John Southern Improvements in and relating to self-priming centrifugal pumping plant
US2426539A (en) * 1945-08-21 1947-08-26 W H Martin Compound rotary pump
DE2112980A1 (de) * 1971-03-17 1972-09-21 Klein Schanzlin & Becker Ag Seitenkanalpumpe,insbesondere Wirbelpumpe

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2134598A (en) * 1983-02-02 1984-08-15 Bosch Gmbh Robert Fuel pumps for internal- combustion engines
EP0143684B1 (fr) * 1983-10-25 1989-12-20 Bertin & Cie Machine de compression d'un fluide, à plusieurs étages de compression en série
EP0170175A2 (fr) * 1984-07-23 1986-02-05 Friedrich Schweinfurter Pompe régénérative avec équilibrage des forces
EP0170175A3 (en) * 1984-07-23 1987-06-03 Friedrich Schweinfurter Regenerative pump with force balancing
GB2205357A (en) * 1987-06-03 1988-12-07 Stuart Turner Ltd Pump arrangement
GB2257750A (en) * 1991-07-13 1993-01-20 Grosvenor Pumps Limited "rotary pumps"
EP1033493A2 (fr) * 1997-11-25 2000-09-06 Zakrytoe Aktsionernoe Obschestvo " Novomet-Perm" Etage de pompe immergee a plusieurs etages
EP1033493A4 (fr) * 1997-11-25 2004-03-31 Zakrytoe Aktsionernoe Obschest Etage de pompe immergee a plusieurs etages
WO2007115471A1 (fr) * 2006-03-28 2007-10-18 Wanzhi Jiang Pompe centrifuge à ailettes à canaux multiples
WO2012113700A1 (fr) * 2011-02-22 2012-08-30 Gardner Denver Deutschland Gmbh Configuration de machine à canaux latéraux
CN103403357A (zh) * 2011-02-22 2013-11-20 加德纳·丹佛德国股份有限公司 侧通道设备型装置
CN103403357B (zh) * 2011-02-22 2017-02-15 加德纳·丹佛德国股份有限公司 侧通道设备型装置
US9677561B2 (en) 2011-02-22 2017-06-13 Gardner Denver Deutschland Gmbh Side channel machine arrangement
KR101875797B1 (ko) * 2011-02-22 2018-07-06 가드너 덴버 도이칠란트 게엠베하 측면 채널 머신 장치
WO2019120550A1 (fr) * 2017-12-21 2019-06-27 Pierburg Gmbh Ventilateur à canal latéral, notamment ventilateur à aire secondaire pour moteur à combustion interne
CN110748504A (zh) * 2019-11-15 2020-02-04 四川省自贡工业泵有限责任公司 侧流道泵体的水力结构
WO2022253496A1 (fr) * 2021-06-04 2022-12-08 Robert Bosch Gmbh Dispositif d'acheminement pour système de pile à combustible, servant à acheminer et/ou à recycler un milieu gazeux, en particulier de l'hydrogène

Also Published As

Publication number Publication date
DE3128374A1 (de) 1983-02-17

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