US3804547A - Lateral canal pump - Google Patents

Lateral canal pump Download PDF

Info

Publication number
US3804547A
US3804547A US00248549A US24854972A US3804547A US 3804547 A US3804547 A US 3804547A US 00248549 A US00248549 A US 00248549A US 24854972 A US24854972 A US 24854972A US 3804547 A US3804547 A US 3804547A
Authority
US
United States
Prior art keywords
lateral canal
pump
lateral
groove
canal
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
US00248549A
Other languages
English (en)
Inventor
W Hagemann
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.)
Sihi GmbH and Co KG
Original Assignee
Sihi GmbH and Co KG
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 Sihi GmbH and Co KG filed Critical Sihi GmbH and Co KG
Application granted granted Critical
Publication of US3804547A publication Critical patent/US3804547A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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

Definitions

  • a typical feature of lateral canal pumps is the fact that, at an output of zero, i.e., with a closed pressure plate, the operating level and the power requirement are at their highest. Under operating conditions, the operating level of the pump can many times not be checked so that its motor must be set at a general level which may be relatively high for a low flow. In addition, the pump normally works at low power for a high flow and operation at low flow'with closed pressure plates occurs only seldomly.
  • An object of this invention is to provide a lateral canal pump with grooves along the interior structure of the canal that influence a circular flow and which are easier to produce and which require no additional power.
  • the present invention makes use of the fact that, with regard ,to influencing the desired flow, it is sufficient, and, concerning the production and power requirements it is moreover more advantageous, if in the present method, only the utmost range of circular flow be influenced by the grooved indentations.
  • the indentations preferably take the form of one or more grooves which suitably extend over the greater part of the internal circumference of the lateral canal, if necessary, even over the entire surface area. It is thereby not necessary to have a continuous unbroken indentation even though such a continuous indentation can in many cases beadvantageous.
  • the circumferential surface canbedivided into many more suchindentations.
  • This effect isreinforced by placing two or more channel-like indentationsnext to each other (viewedin a radial direction) in the lateral canal.
  • the effect can frequently be further strengthenedwhen the channel-like indentations are sloped more .or less opposite the circumferential direction of thelateral canal.
  • the indentations can have any crosssectional formas long as at least one groove is present which issuitable for directing the circular flow along the walls of the lateral canal.
  • a crosssection will preferably be chosen, which, as a casting modeLis found to take shapeingood order. This will very frequently become the grooveform.
  • Thearea of the groove cross-section should generally not be under about 3 percentof the area for the lateral canal cross-section, because cross-sections of under about 3 percent cause a sharp decrease in the desired effect. On the other hand, it is preferred that the area of the groove-cross-section not exceed 15 percentof the lateral canal area, because in this case as well, the
  • the area of the groove cross-section amount from 3 percent to about 15 percent of the area of the lateral canal cross-section. The same is valid for groove-like indentation crosssections.
  • the groove width measured perpendicular to the direction of the groove, amounts to about one tenth toabout one third of the average cross-measurement of the lateral canal (height, width).
  • edges of the indentations are left as sharp as possible. This is possible only to a limited degree in finishing the pump part of the lateral canal as a cast part. However, this principal effect caused by the sharpened edges, is nevertheless still sufficiently present during the inevitable slight rounding of the edges which is inevitable during finishing.
  • the design of the indentation bed plays no part in this conducting effect.
  • the effect of the inventions lateral canal grooves is greatest when they are located in the part of the lateral canal wall opposite the rotor.
  • this does not rule out that such indentations can also be placed in other arrangrnents on' the lateral canal.
  • the effect of the indentations is in its conducting of the circular flow in the lateral canal, it is advantageous to place the indentations so that the flowinfluencing edges find themselves in the same cross-section range of the lateral canal in which the flow lines of the circular flow (corresponding to the hypothetical cross-section flow focus) are radially at their greatest concentration in the wall region. This is most often the case wherethe wall of the lateral canal approaches the hypothetical flow focus of the circular flow to the greatest degree.
  • the indentations are preferably placed in the middle zone of the longer right angle side facing the rotor. 1 a
  • FIGS. 1 and 2 show a view of apressure-plate control disc as seen from the rotor side and an axial section of this control disc; i 1 i i y FIGS. 3-10 show corresponding illustrations of other embodiments in accordance with this invention;
  • FIGS. 13 and 14 show lateral canal cross-sections of two other embodiments of this invention.
  • FIGS. 15 and 16 are diagrams showingthe relationof operational level and power requirement to output in accordance with this invention.
  • control disc regulator of the lateralcanal which consists of an inner hub (1),an outer flange (.2), which, with the corresponding flanges of the adjacent housing fits tightly, and a part of the wall (3), located between them which forms the lateral canal (4) and the current cross-section (5).
  • the pressure opening (6) is located also in this part of the wall which marks the end of the lateral canal.
  • the lateral canal is located actually to the side of the screwxwheel.
  • a round rather than an oval cross-section is chosen for the lateral canal.
  • the lateral canal is actually located to the side of the screw wheel and/or that it has a cross-sectional form that is suitable for the hypothetical circular flow.
  • Other crosssectional forms of the lateral canal especially those in which the lateral canal is found partially outside the radial reach of the screw wheel, and in which the crosssectional form of the lateral canal has somewhat of a right-angle shape, should not be thereby excluded. Examples of such other forms which are within the scope of the invention are shown in FIGS. 13 and 14, where the lateral canal of FIG. 13 is in the form of a right angle, and the lateral canal of FIG. 14 lies with a certain portion of its cross-section surface outside the radial reach of the rotor.
  • the groove (3) forms at the beginning (7) of the lateral canal and continues unbroken to the pressure opening (6) where it ends.
  • the groove (8) runs within the average reach of the part (4) of the lateral canal wall situated opposite the rotor.
  • the groove (8) is actually a right angle crosssection. Its side walls form a right angle corner with the adjacent wall surfaces of the lateral canal.
  • the groove bed at this corner could be rounded as well.
  • FIG. Sand FIG. 4 show a similar groove (9) which continues over the greater part of the lateral canal sur-' face.
  • the distance between the beginning of the lateral canal(7) and the beginning of the groove (10) as well as between the end of the groove (11) and the end of the lateral canal (12) is about between 30 and 90.
  • a small displacement-of the groove radially outward is illustrated'further, in comparison with that of FIGS. 1 and2, a small displacement-of the groove radially outward. Yet'even in this case, it remains within the average reach of the part of the wall opposite the rotor.
  • FIGS. 7 and 8 are similar to the above-described in that a majority of comparatively short groove sections are arranged behind one another in the lateral canal center opposite the rotor; however, in this case, the groove sections opposite the rotary direction are inclined, so that the incline of the first groove section in the rotary direction (13) is relatively large, amounting to about 90, while the incline of the last groove'section (14) in the rotary direction is slight, only about The incline of the groove sections lying between them is within these two figures and declines in the rotary direction. Varying from the illustrated form, the slopes of the combined groove sections are the same opposite the rotary direction.
  • the groove sections opposite the rotary direction can be inclined in the opposite direction, in which case, the incline is about the same.
  • two grooves (15) are placed beside one another along the greater length of the lateral canal. The effect is thereby enhanced.
  • indentations may have many possible forms only in their use as grooves. Number, length, position and direction of the grooves are chosen from one case to the next according to the degree of desired effect, as well as for the desired power requirements.
  • the indentations need not lie absolutely and exclusively in the part of the lateral canal opposite the rotor, as is shown in FIG. 14, where, beside the groove (16) opposite the rotor, two additonal grooves (17) and (18) are located radially within and outside the part of the wall of the lateral canal respectively. Practically speaking, such arrangements are, for technical reasons, of little importance.
  • FIG. 13 shows a groove design in which both groove walls are of the same height, so that a step results which is situated against the direction of the circular flow which would be expected in this part of the wall.
  • FIGS. 15 and 16 illustrate the power characteristics obtainable with and without the inventions indentations; in both figures O-designated curves illustrate the typical operation without the inventions indentations, while the remaining curves coordinate the above design forms by the above noted figures and numbers.
  • a lateral canal pump having an open screw wheel in communication with an open lateral canal
  • the improvement which comprises means defining indentations in the walls of said lateral canal and forming edge surfaces in said walls in order to influence a circular flow in parallel directionto the rotary direction.
  • a lateral canal pump having an open screw wheel operating in communication with a lateral canal located at the side of said screw wheel the improvement which comprises, means defining at least one groove in said canal and running in the rotary direction, the area of the groove cross-section being between about 3 percent and 15 percent of the lateral canal cross-section and the groove width measured perpendicular to the direction of the groove being about one tenth to one third the average cross measurement of the lateral canal, in order to influence a circular flow in a parallel direction to the rotary direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
US00248549A 1971-04-30 1972-04-28 Lateral canal pump Expired - Lifetime US3804547A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2121280A DE2121280C3 (de) 1971-04-30 1971-04-30 Seitenkanalpumpe

Publications (1)

Publication Number Publication Date
US3804547A true US3804547A (en) 1974-04-16

Family

ID=5806441

Family Applications (1)

Application Number Title Priority Date Filing Date
US00248549A Expired - Lifetime US3804547A (en) 1971-04-30 1972-04-28 Lateral canal pump

Country Status (9)

Country Link
US (1) US3804547A (de)
CA (1) CA959342A (de)
CH (1) CH545918A (de)
DE (1) DE2121280C3 (de)
FR (1) FR2139272A5 (de)
GB (1) GB1360721A (de)
IT (1) IT957285B (de)
NL (1) NL168910C (de)
SE (1) SE371865B (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4408952A (en) * 1980-04-15 1983-10-11 Friedrich Schweinfurter Lateral channel pump
US5163810A (en) * 1990-03-28 1992-11-17 Coltec Industries Inc Toric pump
US20040223841A1 (en) * 2003-05-06 2004-11-11 Dequan Yu Fuel pump impeller
US20040258545A1 (en) * 2003-06-23 2004-12-23 Dequan Yu Fuel pump channel
US6890144B2 (en) 2002-09-27 2005-05-10 Visteon Global Technologies, Inc. Low noise fuel pump design
US11143201B2 (en) * 2019-03-15 2021-10-12 Pratt & Whitney Canada Corp. Impeller tip cavity
US11268536B1 (en) 2020-09-08 2022-03-08 Pratt & Whitney Canada Corp. Impeller exducer cavity with flow recirculation

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT397994B (de) * 1989-05-18 1994-08-25 Elin Union Ag Selbstfördereinrichtung für die schmierung eines auf einer welle oder achse angeordneten lagers
JP3107438B2 (ja) * 1992-01-14 2000-11-06 三菱電機株式会社 電動燃料ポンプ
DE102019120410A1 (de) 2019-07-29 2021-02-04 Schwäbische Hüttenwerke Automotive GmbH Fördervorrichtung mit einem Seitenkanal- oder Peripheralgebläse

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1640591A (en) * 1923-10-19 1927-08-30 Westcochippewa Pump Company Centrifugal pump
DE636394C (de) * 1935-01-31 1936-10-08 Arendt & Weicher Werkzeug Und Wasserringpumpe mit kreisender Hilfsfluessigkeit
US2282569A (en) * 1938-04-21 1942-05-12 Fabig Georg Automatic suction circulating pump
GB621691A (en) * 1946-06-03 1949-04-14 John William Ernest Ives Improvements in or relating to deep suction pumps
US2696789A (en) * 1951-09-11 1954-12-14 Alexander S Sugar Self-priming centrifugal pump
US2814434A (en) * 1952-11-07 1957-11-26 Mcculloch Motors Corp Diffuser
US3280752A (en) * 1963-10-31 1966-10-25 Siemen & Hinsch Gmbh Pumps

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1640591A (en) * 1923-10-19 1927-08-30 Westcochippewa Pump Company Centrifugal pump
DE636394C (de) * 1935-01-31 1936-10-08 Arendt & Weicher Werkzeug Und Wasserringpumpe mit kreisender Hilfsfluessigkeit
US2282569A (en) * 1938-04-21 1942-05-12 Fabig Georg Automatic suction circulating pump
GB621691A (en) * 1946-06-03 1949-04-14 John William Ernest Ives Improvements in or relating to deep suction pumps
US2696789A (en) * 1951-09-11 1954-12-14 Alexander S Sugar Self-priming centrifugal pump
US2814434A (en) * 1952-11-07 1957-11-26 Mcculloch Motors Corp Diffuser
US3280752A (en) * 1963-10-31 1966-10-25 Siemen & Hinsch Gmbh Pumps

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4408952A (en) * 1980-04-15 1983-10-11 Friedrich Schweinfurter Lateral channel pump
US5163810A (en) * 1990-03-28 1992-11-17 Coltec Industries Inc Toric pump
US6890144B2 (en) 2002-09-27 2005-05-10 Visteon Global Technologies, Inc. Low noise fuel pump design
US20040223841A1 (en) * 2003-05-06 2004-11-11 Dequan Yu Fuel pump impeller
US6984099B2 (en) 2003-05-06 2006-01-10 Visteon Global Technologies, Inc. Fuel pump impeller
US20040258545A1 (en) * 2003-06-23 2004-12-23 Dequan Yu Fuel pump channel
US11143201B2 (en) * 2019-03-15 2021-10-12 Pratt & Whitney Canada Corp. Impeller tip cavity
US11268536B1 (en) 2020-09-08 2022-03-08 Pratt & Whitney Canada Corp. Impeller exducer cavity with flow recirculation

Also Published As

Publication number Publication date
DE2121280B2 (de) 1973-09-06
CH545918A (de) 1974-02-15
GB1360721A (en) 1974-07-24
CA959342A (en) 1974-12-17
DE2121280A1 (de) 1972-11-16
SE371865B (de) 1974-12-02
IT957285B (it) 1973-10-10
NL168910C (nl) 1982-05-17
NL7205915A (de) 1972-11-01
NL168910B (nl) 1981-12-16
DE2121280C3 (de) 1974-04-11
FR2139272A5 (de) 1973-01-05

Similar Documents

Publication Publication Date Title
US3804547A (en) Lateral canal pump
EP0100078B1 (de) Axialventilator
US5320493A (en) Ultra-thin low noise axial flow fan for office automation machines
US7201076B2 (en) Ball screw
US4221546A (en) Axial fan
US4877373A (en) Vaned diffuser with small straightening vanes
EP0886070A1 (de) Kreiselverdichter sowie diffusor für kreiselverdichter
EP0964635B1 (de) Elektromotor mit einem gebläserad
DE102005015821B4 (de) Laufrad und Kraftstoffpumpe, die dieses verwendet
KR850003923A (ko) 회전자 집합체
KR101981922B1 (ko) 프리-팁형 축류 팬 조립체
JPH1078034A (ja) 焼結含油ベアリング
US4832564A (en) Pumps
DE19908174B4 (de) Fluidpumpe mit einem Kanal zur Reduzierung einer Druckschwingung
KR100743115B1 (ko) 터보분자펌프
US5257910A (en) Centrifugal pump impeller with a low specific speed of rotation
US3924962A (en) Molecular pumps of the drum type
US4006998A (en) Ring compressor
US4376613A (en) Side channel compressor
KR100272199B1 (ko) 디퓨저 펌프의 디퓨저 베인
US3639791A (en) Hydrostatic air bearing
JP2007051551A (ja) 両吸込渦巻ポンプ
US4322185A (en) Staggered hob
JPS63228951A (ja) セグメント磁石
CN212251137U (zh) 一种带有副堰区的机械密封端面结构