US3421446A - Suction bend for centrifugal pumps - Google Patents

Suction bend for centrifugal pumps Download PDF

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Publication number
US3421446A
US3421446A US652836A US65283667A US3421446A US 3421446 A US3421446 A US 3421446A US 652836 A US652836 A US 652836A US 65283667 A US65283667 A US 65283667A US 3421446 A US3421446 A US 3421446A
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United States
Prior art keywords
bend
funnel
suction
runner
flow
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Expired - Lifetime
Application number
US652836A
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English (en)
Inventor
Michael Strscheletzly
Heinz-Bernd Matthias
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JM Voith GmbH
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JM Voith GmbH
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Publication date
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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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/688—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for liquid 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F04D29/4273—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps suction eyes
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/10—Stators
    • F05B2240/12—Fluid guiding means, e.g. vanes
    • F05B2240/121—Baffles or ribs

Definitions

  • the present invention relates to a suction bend for centrifugal pumps with inclined bend portion and With front and rear walls and with another bend portion merging with said inclined bend portion, said other bend portion being co-axial with the runner axis, while a funnel is provided which extends into said inclined bend portion and decreases in diameter in the direction toward the runner.
  • a suction bend according to the invention is characterized primarily in that the lateral wall portions which are located in spaced relationship to and opposite said funnel are on that funnel side which faces away from the inlet into the inclined bend portion to designed as to meet each other and to form a spur-shaped formation while together with said funnel defining fluid passages around a portion of said funnel.
  • the present invention concerns a suction bend for centrifugal pumps with a bend portion inclined preferably by 90 with regard to the runner axis and with a bend portion arranged c-oaxially with regard to said runner axis and merging with the inclined bend portion.
  • one of the goals consists in so designing the suction conduit that at the entrance into the runner there will be assured a speed distribution of the flow as uniform as possible. More specifically, the local speeds over the entire entrance cross'section of the runner should have, as far as possible, uniform magnitude and uniform direction because any deviation from the rotation symmetry of the admission of fluid to the runner will result in an increased danger of cavitation and higher energy losses in the working flow.
  • suction conduits With bent or curved suction conduits, i.e. with suction bends in which the admission of fluid has to be deviated shortly ahead of the runner by a certain angle, in most instances by 90, it is particularly difiicult to realize a locally and temporary uniform constant velocity distribution over the entrance cross-section of the runner.
  • the flow When passing through a suction bend of heretofore known construction, the flow not only changes its direction but also its mean velocity because the maximum velocity in the suction conduit admissible for avoiding too high frictional losses is in most instances considerably lower than the required entrance velocity into the runner.
  • an object of the present invention to provide an improved suction bend which will increase its efficiency and bring about a stable and uniform admission of fluid to the runner.
  • FIGURE 1 is a section through the longitudinal central plane f0 a suction pump bend according to the present invention
  • FIGURE 2 is a section along the line II--II of FIG- URE 1;
  • FIGURE 3 is a portion of a section similar to that of FIGURE 2 of a modified suction bend.
  • a suction bend for centrifugal pumps with a suction bend portion inclined to the runner axis preferably by and provide-d with lateral wall portions and with front and rear wall portions penetrated by the runner shaft and having a bend portion concentrically arranged to the runner axis and merging with the inclined bend portion while said bend portion which is concentrically arranged to the runner axis has a funnel tapering in the direction toward the runner, is characterized, according to the present invention, in that the lateral wall portions which are located opposite and in spaced relationship to said funnel meet with each other on that funnel side which is remote from the entrance to the bend, so that a spur or lobe formation is formed which extends at least within the marginal area of the large funnel opening to the outer wall thereon while defining a flow passage extending over a portion of the circumference of the funnel.
  • the flow passages are preferably spirally designed, and the flow cross-sections of said passages decrease in flow direction at that funnel side which is remote from the flow admission to the bend.
  • the decrease in the cross-section of the spiral-shaped flow passages is approximately proportional to the looping angle around the funnel.
  • suction bends having a continuous runner shaft it is advantageous to provide a rib on that side of the runner shaft which is remote from the inlet of the bend, said rib representing a radial extension of the lobe or spur.
  • the said rib extends to the runner shaft or the protective sleeve therefor and also extends into the funnel in axial direction up to the narrowest portion thereof. In this way, the formation of turbulence and losses during intermixing of the partial flows will be avoided.
  • a partition is pro vided on that side of the runner shaft which is located radially opposite the runner shaft or the protective sleeve therefor, and extends in the direction toward the inlet to the bend.
  • the flow passages are arranged symmetrically with regard to each other, and the ribs and/or the partition are arranged in the spiral plane of the bend.
  • the flow passages are advantageously non-symmetrically arranged with regard to the longitudinal central plane of the suction bend.
  • the plane of the largest funnel opening and the wall located opposite said largest funnel opening and pertaining to the inclined bend portion converge in the intermediate meridian section of the bend while forming an angle of from to 20, preferably 12, in the direction toward the lobe or spur portion.
  • the axial funnel length is from 0.6 to 1.0, preferably 0.8 times as long as the smallest funnel diameter and if, furthermore, the funnel wall is reinforced by a bead while the rounding of the marginal head has a radius of from 0.05 to 0.15, preferably 0.1 times the smallest funnel diameter.
  • the suction bend illustrated therein comprises a bend portion 5 which is inclined approximately by 90 with regard to the axis 4 of the runner 3 mounted on the shaft 2.
  • the suction bend furthermore comprises a bend portion 6 which is coaxial with the runner axis 4 and merges with the bend portion 5.
  • the bend portion 6 has a funnel extending into the inclined bend portion 5, said funnel tapering in the direction toward the runner 3.
  • the lateral walls 9 and 10 (FIG. 2) of the bend portion 5 which are located opposite the funnel 7 in spaced relationship thereto meet each other on that side of the funnel 7 which is remote from the inlet 19 to the bend while forming a lobe or spur 11.
  • the said lobe or spur 11 extends to the bead reinforcement 12 of the funnel 7 and within the range of the funnel is in the form of a rib-shaped extension 13 extended to the outer funnel wall.
  • the walls 9 and 10 confine spirally shaped flow passages 14 and 15 which extend around a portion of the funnel periphery while the cross-sections of said flow passages 14 and 15 decrease in flow direction on that side which is remote from the inlet of the bend.
  • a rib 17 extending to the shaft protective sleeve 16 forms an extension of the spur 11 and extends within the funnel 7 approximately to the narrowest portion thereof. On that side of the shaft protective sleeve 16 which is located radially opposite said rib 17 there is provided a partition 18.
  • the wall 20 (FIG. 1) of the bend portion 5, which wall is located opposite the funnel opening, and the plane 21 of the funnel opening converge in the illustrated intermediate meridial section of the bend while forming an angle a of approximately 5.
  • the length L of the funnel 7 amounts in the present instance to about 0.8 times the smallest diameter D of the funnel, whereas the radius r of the bead-shaped funnel rim 12 amounts to about 0.07 times the diameter D.
  • said passages may also be designed non-symmetrically in order to obtain a prerotation with regard to the longitudinal central plane 22 of the suction bend.
  • Such an arrangement is shown in FIG. 3 with the flow passages 23 and 24.
  • the rib-shaped spur extension 13, which is not visible in this figure, and the rib 17 will in this instance extend from the spur 11 radially with regard to the central axis 4 of the runner while forming an angle with regard to the longitudinal central plane 22.
  • the partition 18 illustrated in FIGS. 1 and 3 is not necessary under all circumstances. At any rate, it is dispensed with in the non-symmetrical design of the How passages 23 and 24 of FIG. 3.
  • the bend portion 5 may also, for reasons of space, be curved away from the runner or toward the runner as indicated by the dot-dash lines 25 and 26 in FIG. 1.
  • a bend according to the invention is applicable not only for centrifugal pumps but may advantageously also be used for blowers or pump turbines.
  • pump turbines With pump turbines, the advantages of the invention, especially when operating the device as pump, are obvious, but also when operating the device as turbine, the design of the bend according to the invention will not be disadvantageous.
  • a suction bend for centrifugal pumps which comprises: housing means having a first section with front and rear walls and also having lateral walls, said front and rear walls being provided with axially aligned bores for receiving therein the runner shaft of a centrifugal pump, the bore in said front Wall having a greater diameter than the bore in said rear wall, said housing means also comprising a second section including a suction opening having its axis arranged at an angle with regard to the axis of said bores, funnel-shaped tubular means extending through the bore in said front wall and flaring from said front wall in the direction toward said rear wall, said lateral walls within the area of said funnel-shaped means meeting each other approximately at the largest diameter area of said funnel-shaped means on that side thereof which faces away from said inlet opening while creating a spur-shaped formation and together with a portion of said funnel-shaped means respectively defining flow passage means extending on opposite sides of and partially around said funnel-shaped means.
  • a suction bend according to claim 1 which includes: shaft means extending through the bores in said front and rear walls and in spaced relationship to and through said funnel-shaped means, and rib means extending from said spur-shaped formation in radial direction with regard to said funnel-shaped means into the vicinity of the outer periphery of said shaft means and in axial direction of said funnel-shaped means to the narrower portions thereof.
  • a suction bend according to claim 4 which includes partition means located on that side of said shaft means which is radially opposite said rib means and extending from an area in the vicinity of the periphery of said shaft means in the direction toward said suction opening.
  • a suction bend according to claim 4 in which said flow passage means are symmetrically arranged with regard to each other, and in which said rib means is located in the central plane of said suction bend.
  • a suction bend according to claim 1 in which the plane of the largest opening of said funnel-shaped means and the respective rear and front walls of said suction bend which are located opposite said palne define in the median meridial section of the bend an angle of from 5 20 while conveying in the direction toward said spurshaped formation.
  • a suction bend according to claim 1 in which the axial funnel length equals approximately from 0.6-1.0 the smallest diameter of said funnel.
  • a suction bend according to claim 1 in which the larger diameter end portion of said funnel-shaped means is reinforced by a rounded bead having a rounding radius of from 0.05-0.15 times the smallest diameter of said funnel-shaped means.
  • suction bend according to claim 1 in which said suction opening has a cross section at least approximating an ellipse.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US652836A 1966-07-15 1967-07-12 Suction bend for centrifugal pumps Expired - Lifetime US3421446A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEV0031515 1966-07-15

Publications (1)

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US3421446A true US3421446A (en) 1969-01-14

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Country Status (4)

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US (1) US3421446A (de)
AT (1) AT272847B (de)
CH (1) CH469907A (de)
DE (1) DE1528883A1 (de)

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3859008A (en) * 1971-07-06 1975-01-07 Andritz Ag Maschf Pump with offset inflow and discharge chambers
JPS5471208U (de) * 1977-10-28 1979-05-21
US4799857A (en) * 1986-11-29 1989-01-24 Klein, Schanzlin & Becker Aktiengesellschaft Casing for fluid flow machines
US4828457A (en) * 1986-08-20 1989-05-09 Klein, Schanzlin & Becker Aktiengesellschaft Elbow casing for fluid flow machines
US4880352A (en) * 1987-11-23 1989-11-14 Sundstrand Corporation Centrifugal liquid pump
US5257901A (en) * 1990-12-28 1993-11-02 Whirlpool Corporation Quick-priming centrifugal pump
US5297930A (en) * 1991-12-31 1994-03-29 Cornell Research Foundation, Inc. Rotating stall suppression
US5388970A (en) * 1993-01-22 1995-02-14 Pierburg Gmbh Electrically driven air pump
US5405106A (en) * 1992-07-20 1995-04-11 The Boeing Company Apparatus for providing increased fluid flow turning vane efficiency
US20020154179A1 (en) * 2001-01-29 2002-10-24 Lawrence Wilcock Distinguishing real-world sounds from audio user interface sounds
US6520738B2 (en) * 2001-03-15 2003-02-18 Honeywell International, Inc. Plenum entry bulk swirl generator
US20100172753A1 (en) * 2009-01-08 2010-07-08 Frank Lin Compressor side inlet with improved aerodynamic performance and reduced manufacturing complexity
CN102444617A (zh) * 2010-09-30 2012-05-09 上海凯士比泵有限公司 多级离心泵的吸水室
US8272836B1 (en) 2008-01-25 2012-09-25 Lynx Product Group, LLC Pump suction assembly
EP2520782A4 (de) * 2009-12-29 2014-11-05 Kawasaki Heavy Ind Ltd Einlasskanal für einen superlader
US20160108930A1 (en) * 2013-06-20 2016-04-21 Mitsubishi Hitachi Power Systems, Ltd. Gas guiding device and facility including the same
US20180073504A1 (en) * 2015-04-14 2018-03-15 Magna Powertrain Bad Homburg GmbH Pump device
IT202000010297A1 (it) * 2020-05-08 2021-11-08 Nuovo Pignone Tecnologie Srl Compressore centrifugo e metodo di funzionamento del compressore centrifugo per produrre un flusso d'ingresso uniforme del gas di processo
US20230272743A1 (en) * 2022-02-25 2023-08-31 Doosan Enerbility Co., Ltd. Air inlet manifold and gas turbine including the same
RU2810285C1 (ru) * 2020-05-08 2023-12-25 НУОВО ПИНЬОНЕ ТЕКНОЛОДЖИ - С.р.л. Центробежный компрессор и способ работы центробежного компрессора для получения однородного входного потока технологического газа
WO2024210988A1 (en) * 2023-04-06 2024-10-10 Siemens Energy Global GmbH & Co. KG Turning inlet duct
US20250361876A1 (en) * 2024-05-23 2025-11-27 Pratt & Whitney Canada Corp. Plenum closure panel with integrated airflow direction device
EP4707539A1 (de) * 2024-08-26 2026-03-11 Pratt & Whitney Canada Corp. Radialeinlassverdichter

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2635078A1 (de) * 1975-08-04 1977-02-24 Pitstock Pty Ltd Fuehrungselement zum ablenken eines luftstroms

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE217495C (de) *
US820439A (en) * 1905-05-06 1906-05-15 Henry R Worthington Centrifugal, turbine, and similar pump.
US1269063A (en) * 1915-06-02 1918-06-11 Henry R Worthington Centrifugal pump.
DE455092C (de) * 1928-01-25 Samuel Maroger Kreiselpumpe, bei der die Saugwirkung durch den Unterdruck hervorgebracht wird, der sich an der Rueckseite in einer Fluessigkeit umlaufender Duesen bildet
GB307399A (en) * 1928-03-06 1930-07-04 Condensation Application Mec Improvements in or relating to centrifugal pumps
DE869779C (de) * 1944-10-28 1953-03-09 Escher Wyss Maschinenfabrik G Regelbare Wasserablassvorrichtung, die sich als Druckregler und Synchronauslass bei Rohrleitungsturbinen und als Wasserenergie-vernichter verwenden laesst

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE217495C (de) *
DE455092C (de) * 1928-01-25 Samuel Maroger Kreiselpumpe, bei der die Saugwirkung durch den Unterdruck hervorgebracht wird, der sich an der Rueckseite in einer Fluessigkeit umlaufender Duesen bildet
US820439A (en) * 1905-05-06 1906-05-15 Henry R Worthington Centrifugal, turbine, and similar pump.
US1269063A (en) * 1915-06-02 1918-06-11 Henry R Worthington Centrifugal pump.
GB307399A (en) * 1928-03-06 1930-07-04 Condensation Application Mec Improvements in or relating to centrifugal pumps
DE869779C (de) * 1944-10-28 1953-03-09 Escher Wyss Maschinenfabrik G Regelbare Wasserablassvorrichtung, die sich als Druckregler und Synchronauslass bei Rohrleitungsturbinen und als Wasserenergie-vernichter verwenden laesst

Cited By (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3859008A (en) * 1971-07-06 1975-01-07 Andritz Ag Maschf Pump with offset inflow and discharge chambers
JPS5471208U (de) * 1977-10-28 1979-05-21
US4828457A (en) * 1986-08-20 1989-05-09 Klein, Schanzlin & Becker Aktiengesellschaft Elbow casing for fluid flow machines
US4799857A (en) * 1986-11-29 1989-01-24 Klein, Schanzlin & Becker Aktiengesellschaft Casing for fluid flow machines
US4880352A (en) * 1987-11-23 1989-11-14 Sundstrand Corporation Centrifugal liquid pump
US5257901A (en) * 1990-12-28 1993-11-02 Whirlpool Corporation Quick-priming centrifugal pump
US5297930A (en) * 1991-12-31 1994-03-29 Cornell Research Foundation, Inc. Rotating stall suppression
US5405106A (en) * 1992-07-20 1995-04-11 The Boeing Company Apparatus for providing increased fluid flow turning vane efficiency
US5388970A (en) * 1993-01-22 1995-02-14 Pierburg Gmbh Electrically driven air pump
US20020154179A1 (en) * 2001-01-29 2002-10-24 Lawrence Wilcock Distinguishing real-world sounds from audio user interface sounds
US6520738B2 (en) * 2001-03-15 2003-02-18 Honeywell International, Inc. Plenum entry bulk swirl generator
US8272836B1 (en) 2008-01-25 2012-09-25 Lynx Product Group, LLC Pump suction assembly
US20100172753A1 (en) * 2009-01-08 2010-07-08 Frank Lin Compressor side inlet with improved aerodynamic performance and reduced manufacturing complexity
EP2520782A4 (de) * 2009-12-29 2014-11-05 Kawasaki Heavy Ind Ltd Einlasskanal für einen superlader
CN102444617A (zh) * 2010-09-30 2012-05-09 上海凯士比泵有限公司 多级离心泵的吸水室
DE112013007175B4 (de) 2013-06-20 2022-06-30 Mitsubishi Power, Ltd. Gasleitvorrichtung und diese aufweisende Anlage
US20160108930A1 (en) * 2013-06-20 2016-04-21 Mitsubishi Hitachi Power Systems, Ltd. Gas guiding device and facility including the same
US10113560B2 (en) * 2013-06-20 2018-10-30 Mitsubishi Hitachi Power Systems, Ltd. Gas guiding device and facility including the same
US20180073504A1 (en) * 2015-04-14 2018-03-15 Magna Powertrain Bad Homburg GmbH Pump device
AU2021266564B2 (en) * 2020-05-08 2024-09-05 Nuovo Pignone Tecnologie - S.R.L. Centrifugal compressor and method of operating the centrifugal compressor to produce a uniform inlet flow of process gas
US12320366B2 (en) 2020-05-08 2025-06-03 Nuovo Pignone Tecnologie—S.R.L. Centrifugal compressor and method of operating the centrifugal compressor to produce a uniform inlet flow of process gas
CN115485480A (zh) * 2020-05-08 2022-12-16 诺沃皮尼奥内技术股份有限公司 离心式压缩机和操作离心式压缩机以产生工艺气体的均匀入口流的方法
KR20230005980A (ko) * 2020-05-08 2023-01-10 누보 피그노네 테크놀로지 에스알엘 공정 가스의 균일한 유입구 유동을 생성하기 위한 원심 압축기 및 원심 압축기 작동 방법
JP2023525718A (ja) * 2020-05-08 2023-06-19 ヌオーヴォ・ピニォーネ・テクノロジー・ソチエタ・レスポンサビリタ・リミタータ 遠心圧縮機、及びプロセスガスの均一な入口流を生み出すように遠心圧縮機を動作させる方法
CN115485480B (zh) * 2020-05-08 2025-10-10 诺沃皮尼奥内技术股份有限公司 离心式压缩机和操作离心式压缩机以产生工艺气体的均匀入口流的方法
IT202000010297A1 (it) * 2020-05-08 2021-11-08 Nuovo Pignone Tecnologie Srl Compressore centrifugo e metodo di funzionamento del compressore centrifugo per produrre un flusso d'ingresso uniforme del gas di processo
RU2810285C1 (ru) * 2020-05-08 2023-12-25 НУОВО ПИНЬОНЕ ТЕКНОЛОДЖИ - С.р.л. Центробежный компрессор и способ работы центробежного компрессора для получения однородного входного потока технологического газа
WO2021223912A1 (en) * 2020-05-08 2021-11-11 Nuovo Pignone Tecnologie - S.R.L. Centrifugal compressor and method of operating the centrifugal compressor to produce a uniform inlet flow of process gas
US11976591B2 (en) * 2022-02-25 2024-05-07 Doosan Enerbility Co., Ltd. Air inlet manifold and gas turbine including the same
US20230272743A1 (en) * 2022-02-25 2023-08-31 Doosan Enerbility Co., Ltd. Air inlet manifold and gas turbine including the same
WO2024210988A1 (en) * 2023-04-06 2024-10-10 Siemens Energy Global GmbH & Co. KG Turning inlet duct
US20250361876A1 (en) * 2024-05-23 2025-11-27 Pratt & Whitney Canada Corp. Plenum closure panel with integrated airflow direction device
US12553450B2 (en) * 2024-05-23 2026-02-17 Pratt & Whitney Canada Corp. Plenum closure panel with integrated airflow direction device
EP4707539A1 (de) * 2024-08-26 2026-03-11 Pratt & Whitney Canada Corp. Radialeinlassverdichter
US12577909B2 (en) 2024-08-26 2026-03-17 Pratt & Whitney Canada Corp. Radial inlet compressor

Also Published As

Publication number Publication date
DE1528883A1 (de) 1971-06-03
CH469907A (de) 1969-03-15
AT272847B (de) 1969-07-25

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