EP0118027A2 - Pompe auto-amorçante à canal périphérique - Google Patents

Pompe auto-amorçante à canal périphérique Download PDF

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Publication number
EP0118027A2
EP0118027A2 EP84101022A EP84101022A EP0118027A2 EP 0118027 A2 EP0118027 A2 EP 0118027A2 EP 84101022 A EP84101022 A EP 84101022A EP 84101022 A EP84101022 A EP 84101022A EP 0118027 A2 EP0118027 A2 EP 0118027A2
Authority
EP
European Patent Office
Prior art keywords
impeller
cells
side channel
channels
blade cells
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
EP84101022A
Other languages
German (de)
English (en)
Other versions
EP0118027A3 (en
EP0118027B1 (fr
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.)
Assunzione O Variazione Mandato marchi & Mittler S
Original Assignee
Individual
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 Individual filed Critical Individual
Priority to AT84101022T priority Critical patent/ATE23910T1/de
Publication of EP0118027A2 publication Critical patent/EP0118027A2/fr
Publication of EP0118027A3 publication Critical patent/EP0118027A3/de
Application granted granted Critical
Publication of EP0118027B1 publication Critical patent/EP0118027B1/fr
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
    • 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
    • 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 self-priming side channel pump, which is suitable for generating high pressures with a high suction head.
  • side channel pumps are suitable, the vane cells of which are at least axially, in addition often also radially open, and to which side channels are assigned which completely cover the openings of the vane cells.
  • optimal energy transfer is possible by exchanging impulses from the faster rotating blade fluid to the slower volume flow in the side channel.
  • care is taken to ensure that the volume flow conveyed in the side channel undergoes as little change of direction as possible when it enters and exits from the side channel.
  • the inlet and in particular the outlet are guided outwards in the circumferential direction directly at the beginning or end of the side channel.
  • a special version of a side channel pump in which the blade cells are provided in an alternating length to the impeller hub, so that shorter and longer blade blades alternate (seen in the radial direction).
  • These alternatingly long vane cells are opposed by a side channel with a decreasing cross-section, which covers the long and short vane cells at the beginning, but only the short vane cells at the end.
  • This construction improves the air delivery of the side channel pump, but the suction and venting times are still quite long.
  • the long suction times especially in the case of long suction lines, lead to heating which can cause defects.
  • the heating increases the vapor pressure of the liquid required for the self-priming process within the pump, which results in a decrease in the suction height that can actually be achieved.
  • a self-priming centrifugal pump is known, the rotor of which has two impeller rings. Opposite the outer impeller ring is a side channel that completely covers the impeller cells and is directly connected to the pressure opening of the pump.
  • This outer side channel is, as is generally known in peripheral wheel pumps, only over part of the Guided circumferentially and has an overflow channel at its input end, which is connected to an inner housing space assigned to the inner blade cells.
  • the impeller is in a constructional unit both with star-shaped blade cells, with long blade cells extending from the impeller hub and extending in the circumferential direction and with at least one larger-diameter, preferably double-sided blade cell ring with axially or axially and radially open blade cells and short ones Shovels trained.
  • the star-shaped inner blade cells either open continuously in the axial direction on both sides, or else are separated from one another by a central wall.
  • the blade cells are side channels each with an interrupter, which only partially cover the long blades in the direction of the hub and completely cover the short blade cells.
  • the inner blade ring with associated side channels which acts as a liquid ring “preliminary stage”, is connected upstream of several pump stages of blade cells connected in series and completely covering side channels with interrupters.
  • the following blade rings are thus arranged with increasing diameters in the impeller, which results in a particularly compact design with a very high final head and still good sowing behavior.
  • the construction according to the invention has the advantage that by combining the delivery elements of a directly self-priming liquid ring side channel pump with the delivery elements of a side channel system which is considerably better in terms of efficiency and pressure, but not self-priming in one construction unit, a particularly compact, material-saving high-pressure pump with good self-priming properties and good efficiency arises. Since all the pump elements are arranged on only one impeller, the adjustment of the impeller in the housing is not nearly as critical as in the case of the conventional pumps with a suction stage upstream, which are designed to achieve the pressure figure achieved here.
  • the Design of the pump according to the invention improves the efficiency compared to conventional pumps, in particular by virtue of the fact that the inner side channel pump, which operates as a liquid ring pump, in this multi-stage version as a feed pump, accelerates the volume flow entering the housing at a relatively low flow velocity through the inlet opening into the next stage rotating at a greater peripheral speed . In this way, the acceleration shock which otherwise leads to considerable losses when the blade enters the "pressure stage" is reduced to a minimum.
  • FIGS. 1 to 6 shows a double-flow side channel pump with a liquid ring preliminary stage and consists of a housing 10 and an impeller 32.
  • the housing 10 is constructed in several parts and consists of a housing ring 11 with an inlet opening 12 and an outlet opening 13 , an end housing cover 14, a drive-side bearing cover 15 and the two side channel parts 16 and 16 '.
  • the side channel parts 16 and 16 ' are the pre-stage side channels 17 and 17', the pre-stage inlet openings 18 and 18 ', the pre-stage outlet openings 19 and 19', re-displacement channels 20 and 20 'with ventilation holes 21 and 21', transfer channels 22 and 22 ' Pressure stage side channels 23 and 23 ', pressure stage inlet openings 24 and 24', pressure stage outlet openings 25 and 25 ', and interrupters 26 and 26' are arranged.
  • the housing cover 14 and the bearing cover 15 are sealed in the housing ring 11 by round cord rings 27 and screwed to the housing ring 11 with housing screws 42.
  • a shaft 30, which is sealed by packing rings 29, is mounted and is rotated in the direction of the arrow (FIG. 2) by a drive motor, not shown, for example an electric motor.
  • the impeller 32 is fastened to the free end of the shaft 30 by means of a feather key 31.
  • the two-stage impeller 32 consists of blade cells 33 arranged in a star shape, the blades 34 of which have a roof-shaped backing for reinforcement and form the impeller preliminary stage, and of the axially and radially open blade rings 35 and 35 ', which form the impeller compression stage.
  • the rotating blade cells 33 of the impeller preliminary stage form a liquid ring from the liquid content in the housing, which fluid ring fills the annular preliminary stage side channel 17 and at the same time the blade cells 33 to the wheel circumference.
  • the rotating vane cells reach the area of the side channel beginning, part of the vane cell content belonging to the liquid ring is forced into the side channel 17 by the centrifugal force.
  • the liquid ring thus moves away from the impeller hub and sucks in air through the preliminary stage inlet opening 18. Due to the steady increase in pressure in the side channel 17, caused by the exchange of impulses between the liquid content of the blade cells 33 and the volume flow in the side channel 17, liquid is pushed back from the side channel 17 into the blade cells 33.
  • the air flow i.e. the self-priming process, continues until the suction line and the inside of the pump are vented.
  • the volume flow entering through the inlet opening 12 in the housing 10 and the pre-stage inlet opening 18 into the pre-stage side channel 17 experiences an energy transfer through the exchange of impulses between the higher flow energy state and the volume flow lower from the vane cells 33 formed by centrifugal force Energy state in the side channel 17.
  • the conveyed medium flows through the side channel 17 from the beginning of the side channel to its outlet opening 19 and passes through the transfer channel 22 into the inlet opening 24 and thus into the pressure stage side channel 23.
  • FIGS. 7 to 9 show a further preferred embodiment of the pump according to the invention.
  • the preliminary stage feed cells 33 of the impeller 32 are arranged on one side, that is to say in one flow, and are open in the axial direction.
  • the pressure equalization between both sides of the impeller 32 takes place through pressure equalization bores 40 which are only provided in part of the blade cells 33.
  • the inner blades 34 are arranged flush with the impeller end face, as was also shown in the embodiments according to FIGS. 1 to 6.
  • the inner blades 34 stand from the impeller 32 with which they. are integrally connected, and are open in both the axial and radial directions.
  • the side channel assigned to them accordingly comprises the inner blade cells partially in the radial direction and entirely in the axial direction. In this way, a further increase in the efficiency of the pump can be achieved.
  • the inner step is only single-flow, but a double-flow design is also possible.
  • FIGS. 11 and 12 Further details of the impeller can be seen in FIGS. 11 and 12, in which the roof-shaped stiffeners of the inner blades 34 are also shown.
  • FIGS. 13 and 14 show the impeller of a further preferred embodiment of the pump according to the invention.
  • the inner blade cells 33 are designed to be open on both sides, with side channels opposite them on both sides.
  • the subsequent pressure stage is formed by the blade cells 38 and 38 'with associated side channels, these outer blade cells 38 and 38' only being open in the axial direction.
  • FIGS. 15 to 18 show further preferred embodiments of the pump according to the invention based on its impellers.
  • the impeller according to FIGS. 15 and 16 has inner vane cells 33 and 33 'which are separated by a central wall 36 and which are flush with the impeller 32.
  • the inner blade cells 33 and 33 ' are followed by two further pressure stages 38a, 38b and 38'a, 38'b, also connected in series.
  • the blade cells of the pressure stages are designed to be radially and axially open, opposite them are the correspondingly shaped side channels which completely cover the blade cells.
  • the first pressure stage is designed with only axially open blade cells 38a, 38'a.
  • the depth and arrangement of the blade cells of the various blade cell rings is selected in accordance with the required funding conditions, as well the one- or two-flow formation of the different pressure levels.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP84101022A 1983-02-02 1984-02-01 Pompe auto-amorçante à canal périphérique Expired EP0118027B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84101022T ATE23910T1 (de) 1983-02-02 1984-02-01 Selbstansaugende seitenkanalpumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19833303460 DE3303460A1 (de) 1983-02-02 1983-02-02 Selbstansaugende seitenkanalpumpe
DE3303460 1983-02-02

Publications (3)

Publication Number Publication Date
EP0118027A2 true EP0118027A2 (fr) 1984-09-12
EP0118027A3 EP0118027A3 (en) 1984-10-10
EP0118027B1 EP0118027B1 (fr) 1986-11-26

Family

ID=6189825

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84101022A Expired EP0118027B1 (fr) 1983-02-02 1984-02-01 Pompe auto-amorçante à canal périphérique

Country Status (3)

Country Link
EP (1) EP0118027B1 (fr)
AT (1) ATE23910T1 (fr)
DE (2) DE3303460A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2401408A (en) * 2003-05-06 2004-11-10 Visteon Global Tech Inc Fuel pump impeller with staggered vanes
DE102007026533A1 (de) * 2007-06-08 2008-12-11 Continental Automotive Gmbh Kraftstoffpumpe

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3437021A1 (de) * 1984-10-09 1986-04-10 Robert Bosch Gmbh, 7000 Stuttgart Aggregat zum foerdern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges
DE3509374A1 (de) * 1985-03-15 1986-09-25 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zum foerdern von kraftstoff aus einem vorratstank zur brennkraftmaschine eines kraftfahrzeuges
US5017086A (en) * 1989-05-08 1991-05-21 Vickers Incorporated Hydraulic periphery pumps
DE8908579U1 (de) * 1989-07-14 1990-11-15 Robert Bosch Gmbh, 7000 Stuttgart Aggregat zum Fördern von Kraftstoff
JPH0330596U (fr) * 1989-07-31 1991-03-26
DE69621868T2 (de) * 1995-03-31 2003-01-30 Bitron S.P.A., Nichelino Seitenkanalbrennstoffpumpe für Kraftfahrzeug
DE10019911A1 (de) * 2000-04-20 2001-10-25 Mannesmann Vdo Ag Förderpumpe
US9249806B2 (en) 2011-02-04 2016-02-02 Ti Group Automotive Systems, L.L.C. Impeller and fluid pump
DE102022001696A1 (de) 2022-05-13 2023-11-16 Truma Gerätetechnik GmbH & Co. KG Zweistufige Pumpe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1973669A (en) * 1931-01-12 1934-09-11 Spoor Willem Lodewijk Joost Rotary pump
US2321810A (en) * 1941-09-08 1943-06-15 John W Gurley Rotary pump
DE3014425A1 (de) * 1980-04-15 1981-10-22 Friedrich 8541 Röttenbach Schweinfurter Seitenkanalpumpe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1973669A (en) * 1931-01-12 1934-09-11 Spoor Willem Lodewijk Joost Rotary pump
US2321810A (en) * 1941-09-08 1943-06-15 John W Gurley Rotary pump
DE3014425A1 (de) * 1980-04-15 1981-10-22 Friedrich 8541 Röttenbach Schweinfurter Seitenkanalpumpe

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2401408A (en) * 2003-05-06 2004-11-10 Visteon Global Tech Inc Fuel pump impeller with staggered vanes
US6984099B2 (en) 2003-05-06 2006-01-10 Visteon Global Technologies, Inc. Fuel pump impeller
DE102007026533A1 (de) * 2007-06-08 2008-12-11 Continental Automotive Gmbh Kraftstoffpumpe

Also Published As

Publication number Publication date
EP0118027A3 (en) 1984-10-10
DE3461498D1 (en) 1987-01-15
DE3303460A1 (de) 1984-08-02
EP0118027B1 (fr) 1986-11-26
ATE23910T1 (de) 1986-12-15

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