US3394876A - Drum motor blade construction - Google Patents

Drum motor blade construction Download PDF

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Publication number
US3394876A
US3394876A US577090A US57709066A US3394876A US 3394876 A US3394876 A US 3394876A US 577090 A US577090 A US 577090A US 57709066 A US57709066 A US 57709066A US 3394876 A US3394876 A US 3394876A
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Prior art keywords
blades
blade
rotor
fluid
curvature
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US577090A
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Bruno Eck
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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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis

Definitions

  • FIG. 4 DRUM MOTOR BLADE CONSTRUCTION Original Filed Aug. 26, 1963 2 Sheets-Sheet 1 3 6) FIG FIG. 4
  • Rotor blades elongated in axial direction have inner portions with a small radius of curvature, and outer portions with a larger radius of curvature forming tangential angles of less than degrees.
  • the present invention relates to a drum rotor blade construction, and more particularly to a drum impeller rotor of the type in which blades which are substantially longer in axial direction than in radial direction are disposed in a circular row between axially spaced end walls.
  • drum impeller rotors of this type have blades curved in planes perpendicular to the axis of rotation to have a circular, or substantially circular curvature.
  • the prior art constructions have the disadvantage that they require a comparatively great number of blades for a desired given volume of fluid transported by the 1mpeller rotor.
  • Another disadvantage of prior art constructions is the great loss of efliciency of drum impeller rotors having small dimensions, as compared with corresponding drum impeller rotors having larger dimensions.
  • Another object of the invention is to provide a drum impeller rotor with blades constructed and disposed in such a manner that no turbulence is created in the conveyed fluid.
  • Another object of the invention is to shape and dispose the outer discharge portions of the rotor blades in such a manner that the fluid passes the outer edges of the blades in a smooth laminar flow without any turbulence in this region.
  • a drum impeller rotor comprises two walls located in parallel planes perpendicular to the axis of rotation, and a set of spaced blades secured to the walls and disposed in a circular row equidistant from the axis.
  • Each blade is elongated in axial direction and has inner and outer edges parallel to the axis of rotation.
  • the blades are curved in planes perpendicular to the axis, and preferably form passages which gradually narrow in outward direction.
  • the fluid flows during rotation of the rotor parallel to the walls in the passages between the same and the blades, and leaves the passages at an increased pressure.
  • each blade includes an inner intake portion bounded by the inner 3,394,876 Patented July 30, 1968 ICC edge of the blade and having a first radius of curvature, and an outer discharge portion bounded by the outer edge and having a second different radius of curvature.
  • the outer discharge portion of each blade is constructed and disposed in such a manner that a plane passing through the outer edge tangentially to the discharge portion is located within an angle of plus 20 degrees outwardly, and within an angle of minus 15 degrees inwardly of another plane passing through the outer edge perpendicularly to a radial plane through the same.
  • the blade construction of the present invention produces very high pressures by a very simple, but unobvious improvement of the known blade constructions, and such pressure increase, and the corresponding greater efliciency of the present invention, is decisive for permitting the use of drum impeller rotors for certain tasks for which the prior art constructions have been considered unsuitable.
  • the tangential plane of the blade discharge portion defines a positive angle with a corresponding tangential plane on the periphery of the rotor.
  • the tangential plane of the discharge portion forms a negative angle with a chord perpendicular to the radial plane passing through the outer edge of the blade, and this construction produces particularly high pressure.
  • the streams of fluid between adjacent blades have no axial component, and all parts of the fluid within each passage move parallel to each other so that when the discharge angle of the fluid is selected in accordance with the present invention, no turbulence develops at the outer edges of the blades.
  • FIG. 1 is a side elevation, partially in section, illustrating a blower provided with a drum impeller rotor according to one embodiment of the invention
  • FIG. 2 is a sectional view illustrating the blower of FIG. 1;
  • FIG. 3 is a fragmentary schematic cross sectional View illustrating a blade construction according to the prior art
  • FIG. 4 is a fragmentary schematic cross sectional view illustrating a blade construction according to one embodiment of the invention.
  • FIG. 5 is a fragmentary schematic cross sectional view illustrating on an enlarged scale the construction and position of the discharge portion of a blade according to the embodiment of FIG. 4;
  • FIG. 6 is a fragmentary schematic cross sectional view illustrating on an enlarged scale the construction and position of the discharge portion of the blade according to another embodiment of the invention.
  • FIG. 7 is a fragmentary schematic cross sectional view illustrating a modified arrangement according to the present invention.
  • FIG. 8 is a fragmentary schematic cross sectional view illustrating another modified construction of the invention.
  • a drum impeller rotor is mounted within a spiral-shaped casing 1 and includes two circular walls 2 and 3, and a set of blades 6 whose ends are secured to walls 2 and 3 in the region of the outer circular periphery of the same.
  • the end wall 3 is secured to a drive shaft 4 which extends through an opening in one side wall of easing 1 and carries a pulley 5 which is driven by a belt from a suitable motor, not shown.
  • the other end wall 2 has a central opening registering with a corresponding opening in the other side wall of easing 1, and an inlet tube 7 is provided for guiding the fluid into the central cavity of the rotor.
  • a known drum rotor construction provides circular blades having a single radius of curvature R, as shown in FIG. 3. This construction causes cavitation in the gron A, and great turbulence in the region of the outer axially extending edges of the blades.
  • the inner intake portion 611 has a smaller radius of curvature R than the outer discharge portion 6b which has a greater radius of curvature R.
  • the inner intake portion 6a has a greater radius of curvature than the outer discharge portion 6b.
  • the angle 5 is characteristic of the shape and position of the discharge portion 612. This angle is defined by a tangential plane r on the periphery of the rotor and passing through the outer edge A of the blade, and the tangential plane r on the discharge portion 6b of the blade passing through the outer edge A
  • the outer edges A5 of all blades are located along an imaginary cylinder 1, and it is evident that the tangential plane t on this cylinder is perpendicular to a radial plane r passing through the axis of the rotor and through the outer edge A of the respective blade.
  • the angle 8 is not greater than and since this angle is located outwardly of the tangential plane 1 it will be referred to hereinafter as a positive angle.
  • the angle ⁇ 3' is characteristic for the shape and position of the outer discharge portion 6b. This angle is formed between a tangential plane t on the discharge portion 6b through the outer edge A6, and a plane t passing through the outer edge A perpendicularly to the radial plane r which extends through the axis of the rotor and the outer edge A
  • the plane z extends along a chord of the imaginary cylinder along which the outermost portions of the blades move, and is at the same time a tangential plane on an imaginary cylinder 1, along which the outer edge A of each blade moves during rotation of the rotor. Since the angle ,8 is located inwardly of plane r it will be referred to hereinafter as a negative angle.
  • the angle 3' is not greater than 15".
  • fluid discharge from the passages between adjacent blades will move without any turbulence in the regions of the outer edges A
  • the passages between adjacent blades are wider at the inner ends of the passages, and gradually narrow in the region between the outer discharge portions of the blades to that the pressure of the discharge fluid is increased.
  • the embodiment of FIG. 6 results in particularly high pressure.
  • the super-curvature of the blades causes a high diversion of the fluid in circumferential direction so that a high pressure for a rotor with a very small number of blades is achieved in a very simple manner and with very moderate expenses.
  • the efficiency is indeed a little smaller, but there are many uses where this is not important while the high pressure is very desirable.
  • FIG. 7 illustrates a modified embodiment according to which auxiliary blades 8 are provided between two adjacent blades 6 of the type described with reference to FIG. 5.
  • Each auxiliary blade 8 has an inner edge spaced the same distance from the axis as the inner edges of the blades 6, and an outer edge which is located in the region where the inner intake portions 6a join the outer discharge portions 6b of blades 6.
  • the curvature of the auxiliary blades 8 corresponds to the curvature of the inner intake portion 6a of the blades 6.
  • the auxiliary blades 8 are shown in combination with the blades 6 of the embodiment of FIG. 5, the embodiment of FIG. 6 is preferably provided with correspondingly arranged auxiliary blades 8 whose shape and curvature corresponds to the shape and curvature of the inner intake portions 6a.
  • FIG. 8 Another modified embodiment is illustrated in FIG. 8, and includes a preferably honey-comb mesh 9 bent to the shape of the inner intake portions of the blades, and guiding the fluid in the inner passage portions between the blades 6.
  • auxiliary blades 8 of FIG. 7, and the mesh of FIG. 8 have the effect of initially deflecting the fluid entering between the blades, and thereby relieve the blades 6 of a considerable part of the load which tends to bend the blades.
  • the efficiency of the blade construction is improved, and a number of blades 6 may be reduced without causing any speed differences between fluid streams discharged by the rotor.
  • the streams of discharged fluid have a substantially smaller circumferential width than in the embodiment of FIG. 5, since the discharged streams are bounded by the edges A and by the outermost peripheral portions of the next leading blade, whereas in the embodiments of FIG. 5, the streams are bounded by the outer edge A and the outer edge of the next leading blade.
  • the circumferential spacing of the blades can be selected to produce the optimal turbulence free flow conditions. Streams of the width of the streams in the embodiment of FIG. 5 can be obtained in the embodiment of FIG. 6 by blades which are farther spaced from each other, so that a lesser number of blades need be provided in the embodiment of FIG. 6 than in the embodiment of FIG. 5, assuming that the same pressure is to be produced by the two constructions.
  • a drum impeller rotor having an axis of rotation and comprising two supports spaced along said axis; and a set of spaced blades secured to said supports and disposed in a circular row equidistant from said axis, each blade being elongated in axial direction and having inner and outer edges, each blade being curved in planes perpendicular to said axis whereby a fluid flows during rotation of said rotor between said blades in outward direction, each blade including a curved inner intake portion bounded by said inner edge and having a first smaller radius of curvature, a curved outer discharge portion bounded by said outer edge and having a second greater radius of curvature, and between said inner intake portion and said outer discharge portion a portion having a radius of curvature greater than said first radius but not greater than said second radius, said discharge portion being disposed in such a position that a plane passing through said outer edge tangentially to said discharge portion defines an angle of less than degrees with another plane passing through said outer edge perpendicular
  • a drum impeller rotor having an axis of rotation and comprising two walls located in parallel planes perpendicular to said axis; a set of spaced blades secured to said walls and disposed in a circular row equidistant from said axis, each blade being elongated in axial direction and having inner and outer edges parallel to said axis, each blade being curved in planes perpendicular to said axis whereby a fluid flows during rotation of said rotor parallel to said walls between the same and said blades in outward direction, each blade including an inner intake portion bounded by said inner edge and having a first smaller radius of curvature, an outer discharge portion bounded by said outer edge and having a second greater radius of curvature, and between said inner intake portion and said outer discharge portion a portion having a radius of curvature greater than said first radius but not greater than said second radius, said discharge portion being disposed in such a manner that a plane passing through said outer edge tangentially to said discharge portion defines an angle less than 15
  • a drum impeller rotor according to claim 4 wherein said guide means includes at least one auxiliary blade disposed between each pair of adjacent blades of said blades, each auxiliary blade having an outer edge located in the region where said inner intake portion and said outer discharge portions of said adjacent blades join, each auxiliary blade being curved and substantially parallel with said inner intake portions of said adjacent blades.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US577090A 1959-07-24 1966-09-02 Drum motor blade construction Expired - Lifetime US3394876A (en)

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Application Number Priority Date Filing Date Title
DEE0018014 1959-07-24

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US (1) US3394876A (de)
BE (1) BE593292A (de)
CH (1) CH377975A (de)
DE (1) DE1403034B2 (de)
GB (1) GB954369A (de)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3751179A (en) * 1971-07-26 1973-08-07 Westinghouse Electric Corp Bi-directional centrifugal pump
US4165950A (en) * 1976-09-06 1979-08-28 Hitachi, Ltd. Fan having forward-curved blades
US4202296A (en) * 1976-12-21 1980-05-13 Suddeutsche Kuhlerfabrik Julius Fr. Behr GmbH & Co. K.G. Cooling system for internal combustion engines
EP0807760A3 (de) * 1996-05-17 1998-10-07 Calsonic Corporation Mehrschaufelrotor für Kreisellüfter
US5988979A (en) * 1996-06-04 1999-11-23 Honeywell Consumer Products, Inc. Centrifugal blower wheel with an upwardly extending, smoothly contoured hub
US6461103B2 (en) * 2000-05-16 2002-10-08 Lg Electronics Inc. Siroco fan of a window type air conditioner
US20030012649A1 (en) * 2001-07-16 2003-01-16 Masaharu Sakai Centrifugal blower
US20030101985A1 (en) * 2001-12-04 2003-06-05 Chiang Chao Cheng Smoke exhauster having an improved fan device
US6695038B2 (en) * 1999-09-02 2004-02-24 Advanced Rotary Systems, Llc Heat exchanger type fan
US20040131468A1 (en) * 2003-01-02 2004-07-08 Chao-Cheng Chiang Ventilator having an optimum fan structure
US20140007859A1 (en) * 2007-11-06 2014-01-09 Regal Beloit America, Inc. High Efficiency Furnace/Air Handler Blower Housing with a Side Wall Having an Exponentially Increasing Expansion Angle
CN104165158A (zh) * 2014-08-06 2014-11-26 宁波方太厨具有限公司 一种吸油烟机的离心风机
US9546668B2 (en) 2007-06-14 2017-01-17 Regal Beloit America, Inc. Extended length cutoff blower
US10527054B2 (en) * 2016-05-24 2020-01-07 Mohammad Hassan Orangi Impeller for centrifugal fans
CN114962325A (zh) * 2022-06-20 2022-08-30 太仓欣华盈电子有限公司 一种高效能扇叶及离心风扇

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3245611A (en) * 1964-08-17 1966-04-12 American Radiator & Standard Fluid mover
US3536416A (en) * 1968-05-14 1970-10-27 Dov Z Glucksman Squirrel-cage rotor for fluid moving devices
TW201441489A (zh) * 2014-05-26 2014-11-01 Yang Bo Sheng 流體泵浦低紊流動葉輪
CN105298907A (zh) * 2014-06-19 2016-02-03 杨博胜 流体泵浦低紊流动叶轮
CN119982636B (zh) * 2025-04-11 2025-11-25 南通旋风机械有限公司 一种可调式离心通风机

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US867874A (en) * 1906-07-11 1907-10-08 George Marie Capell Centrifugal fan and pump-wheel.
GB191006700A (en) * 1910-03-17 1911-03-02 William Mulholland Improvements in Fans or Blowers.
GB115070A (en) * 1917-04-21 1918-04-22 Gwynnes Ltd Improvements relating to Centrifugal Pumps and Fans.
DE338436C (de) * 1921-06-18 Alexander Varga Beiderseitig durch Kegelmaentel abgeschlossene Schaufeltrommel fuer Kreiselgeblaese
US2394214A (en) * 1944-06-05 1946-02-05 Verner E Sprouse Blower
FR1033790A (fr) * 1951-03-09 1953-07-15 Perfectionnements apportés aux machines du genre des compresseurs rotatifs
US2833464A (en) * 1955-05-02 1958-05-06 Vernco Corp Strip formed blower wheel
FR1193452A (fr) * 1957-03-25 1959-11-03 Paul Pollrich & Comp Ventilateur radial à roue mobile en forme de tambour

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE338436C (de) * 1921-06-18 Alexander Varga Beiderseitig durch Kegelmaentel abgeschlossene Schaufeltrommel fuer Kreiselgeblaese
US867874A (en) * 1906-07-11 1907-10-08 George Marie Capell Centrifugal fan and pump-wheel.
GB191006700A (en) * 1910-03-17 1911-03-02 William Mulholland Improvements in Fans or Blowers.
GB115070A (en) * 1917-04-21 1918-04-22 Gwynnes Ltd Improvements relating to Centrifugal Pumps and Fans.
US2394214A (en) * 1944-06-05 1946-02-05 Verner E Sprouse Blower
FR1033790A (fr) * 1951-03-09 1953-07-15 Perfectionnements apportés aux machines du genre des compresseurs rotatifs
US2833464A (en) * 1955-05-02 1958-05-06 Vernco Corp Strip formed blower wheel
FR1193452A (fr) * 1957-03-25 1959-11-03 Paul Pollrich & Comp Ventilateur radial à roue mobile en forme de tambour

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3751179A (en) * 1971-07-26 1973-08-07 Westinghouse Electric Corp Bi-directional centrifugal pump
US4165950A (en) * 1976-09-06 1979-08-28 Hitachi, Ltd. Fan having forward-curved blades
US4202296A (en) * 1976-12-21 1980-05-13 Suddeutsche Kuhlerfabrik Julius Fr. Behr GmbH & Co. K.G. Cooling system for internal combustion engines
EP0807760A3 (de) * 1996-05-17 1998-10-07 Calsonic Corporation Mehrschaufelrotor für Kreisellüfter
US6007300A (en) * 1996-05-17 1999-12-28 Calsonic Corporation Centrifugal multiblade fan
US5988979A (en) * 1996-06-04 1999-11-23 Honeywell Consumer Products, Inc. Centrifugal blower wheel with an upwardly extending, smoothly contoured hub
US6695038B2 (en) * 1999-09-02 2004-02-24 Advanced Rotary Systems, Llc Heat exchanger type fan
US6461103B2 (en) * 2000-05-16 2002-10-08 Lg Electronics Inc. Siroco fan of a window type air conditioner
US20030012649A1 (en) * 2001-07-16 2003-01-16 Masaharu Sakai Centrifugal blower
US20030101985A1 (en) * 2001-12-04 2003-06-05 Chiang Chao Cheng Smoke exhauster having an improved fan device
US20040131468A1 (en) * 2003-01-02 2004-07-08 Chao-Cheng Chiang Ventilator having an optimum fan structure
US6866481B2 (en) 2003-01-02 2005-03-15 Chao-Cheng Chiang Ventilator having an optimum fan structure
US9546668B2 (en) 2007-06-14 2017-01-17 Regal Beloit America, Inc. Extended length cutoff blower
US20140007859A1 (en) * 2007-11-06 2014-01-09 Regal Beloit America, Inc. High Efficiency Furnace/Air Handler Blower Housing with a Side Wall Having an Exponentially Increasing Expansion Angle
US9513029B2 (en) * 2007-11-06 2016-12-06 Regal Beloit America, Inc. High efficiency furnace/air handler blower housing with a side wall having an exponentially increasing expansion angle
CN104165158A (zh) * 2014-08-06 2014-11-26 宁波方太厨具有限公司 一种吸油烟机的离心风机
US10527054B2 (en) * 2016-05-24 2020-01-07 Mohammad Hassan Orangi Impeller for centrifugal fans
CN114962325A (zh) * 2022-06-20 2022-08-30 太仓欣华盈电子有限公司 一种高效能扇叶及离心风扇

Also Published As

Publication number Publication date
DE1403034B2 (de) 1971-07-08
DE1403034A1 (de) 1969-01-30
BE593292A (fr) 1960-11-14
CH377975A (de) 1964-05-31
GB954369A (en) 1964-04-08

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