EP0021435A1 - Moteur à air et son rotor - Google Patents

Moteur à air et son rotor Download PDF

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Publication number
EP0021435A1
EP0021435A1 EP80103626A EP80103626A EP0021435A1 EP 0021435 A1 EP0021435 A1 EP 0021435A1 EP 80103626 A EP80103626 A EP 80103626A EP 80103626 A EP80103626 A EP 80103626A EP 0021435 A1 EP0021435 A1 EP 0021435A1
Authority
EP
European Patent Office
Prior art keywords
air
rotor
turbine
bucket
buckets
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Withdrawn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
EP80103626A
Other languages
German (de)
English (en)
Inventor
Stanley Joseph Rodowsky Jr.
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.)
Black and Decker Inc
Original Assignee
Black and Decker Inc
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 Black and Decker Inc filed Critical Black and Decker Inc
Publication of EP0021435A1 publication Critical patent/EP0021435A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L9/00—Details or accessories of suction cleaners, e.g. mechanical means for controlling the suction or for effecting pulsating action; Storing devices specially adapted to suction cleaners or parts thereof; Carrying-vehicles specially adapted for suction cleaners
    • A47L9/02—Nozzles
    • A47L9/04—Nozzles with driven brushes or agitators
    • A47L9/0405—Driving means for the brushes or agitators
    • A47L9/0416—Driving means for the brushes or agitators driven by fluid pressure, e.g. by means of an air turbine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/34—Non-positive-displacement machines or engines, e.g. steam turbines characterised by non-bladed rotor, e.g. with drilled holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • 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

Definitions

  • the present invention is directed to an air-powered motor and a rotor therefor and, in particular, to an air-powered motor and rotor therefor which can be used to drive small power tools, such as a floor tool for a vacuum cleaner, a sander or a grinder, wherein the air-powered motor uses a source of power such as a vacuum cleaner.
  • Prior art air-powered motors, driven by a vacuum cleaner, for example, are known in the art, such as those shown in U.S. Patent 2,963,270, U.S. Patent 2,962,748 (which is a CIP of U.S. Patent 2,963,270), and U.S. Patent 3,005,224. Yet another example of such a device is shown in U.S. Patent 3,004,100.
  • These prior art devices have turbines which comprise a housing, which forms the turbine chamber and a rotor rotatably mounted within the chamber.
  • the rotor includes a plurality of blades mounted between two side members, the blades and the side members forming turbine buckets which are open on the periphery of the rotor and are closed at their rear ends by a bottom wall member. This rear wall member may be semi-circular, as is illustrated in U.S. Patent 2,963,270.
  • the rotors have been constructed without consideration of characteristics such as bucket angle, bucket radius ratio, blade inlet angle, and dynamic balancing, which are significant factors which affect the motor efficiency.
  • the operation of the prior art devices, espec. known floor tools is unsatisfactory because the turbine motor does not generate enough power to drive a rotary brush to which it is coupled in order for the rotary brush to properly perform.
  • This unit has an efficiency of 25%.
  • a vacuum source such as a vacuum cleaner
  • small power tools such as a vacuum cleaner floor tool, a sander or a Grinder.
  • the present invention is directed to an air-powered. motor and a turbine rotor therefor which can be used to dri ve small power tools, such as a vacuum cleaner floor tool, a sander or a grinder, and in which the motor can be coupled to a vacuum cleaner to provide a source of vacuum or forced air to drive the turbine rotor.
  • the turbine rotor has a structure which substantially increases the efficiency of the motor as compared to prior art devices and, in particular, the motor comprises a housing having a turbine chamber, an air inlet and an air outlet.
  • the turbine rotor is rotatably mounted in the chamber, the turbine rotor having a plurality of turbine blades extending from the outer surface of the rotor towards the interior thereof.
  • a plurality of turbine buckets are formed in the rotor, the top and bottom of the buckets being formed by the turbine blades, the sides of the buckets being formed by the sides of the rotor and the rear wall or bottom of the buckets being formed by a semicircular wall.
  • the structural elements which form the buckets are positioned-with respect to one another such that the bucket angle of the bucket ⁇ ⁇ 60° , the bucket radius and the blade inlet angle ⁇ ⁇ 27°.
  • the turbine rotor is dynamically balanced about its rotational axis to further enhance the efficiency of the motor.
  • the air-powered motor of the present invention includes a housing 1 which has an air inlet in the form of a nozzle 3, the nozzle has a constant width W and a decreasing height H.
  • the housing further includes an air outlet 5 which may be connected to a source of vacuum 6, such as a vacuum cleaner.
  • a source of forced air 8 such as a fan or vacuum cleaner exhaust, can be connected to the air inlet 3 of the housing.
  • the centers of the air inlet and the air outlet are offset with respect to one another.
  • a turbine chamber 7 is formed within the housing 1, and air enters the turbine chamber 7 through nozzle opening 9 and exits therefrom through port 11 of the air outlet 5.
  • Turbine rotor 13 is positioned within the turbine chamber 7 in the housing 1, the turbine rotor 13 being rotatably mounted on shaft 15, which is supported on bearing 19 in the wall 17 of housing 1.
  • the shaft 15 passes through the center of rotor 13 and may extend from the other side thereof, and be supported by a suitable bearing structure (not shown) in wall 21 of housing 1.
  • Shaft 15 is coupled to a tool or other device 10, which the motor drives by means of the rotation of shaft 15.
  • rotor 13 includes a plurality of turbine blades 23 which extend inwardly from the rotor periphery 25. Adjacent blades are connected together by means of rear walls or bottoms 27.
  • the turbine blades 23, rear walls 27 and the sides 29 of the rotor 13 form a plurality of turbine buckets which are open at their top and are positioned around the periphery of the turbine rotor 13.
  • point 31 is located on rear wall 27 at a point equidistant between adjacent blades 23.
  • Point 33 is located on the periphery of the turbine rotor at a point midway between the tips of the adjacent rotor blades 23.
  • a line 35 is drawn between these two points, and a line 37 is drawn tangential to the periphery of the rotor 13 at the point at which line 35 intersects the periphery.
  • the angle between lines 35 and 37 is defined as the bucket angle The bucket angle ⁇ ⁇ 60°.
  • the bucket angle ⁇ is significant in that it is related to the tangential nature of the turbine blades. Since radial air flow into buckets does not perform any useful work in the sense-of rotating the bucket and,in fact, has an adverse effect on performance in that is creates drag, the forming of buckets which are tangential in nature is a significant factor in enhancing the efficiency of the motor and thus is a critical factor in the turbine bucket strcture.
  • R 0 is the radius from the center of the turbine rotor to the periphery thereof
  • R 8 is the radius from the center of the turbine bucket to the point 38 which is the innermost point of the interior of the bucket.
  • the turbine bucket radius ratio is defined as The turbine bucket radius ratio
  • the radius ratio is also significant in that it is also related to the tangential nature of the turbine blades. Since radial air flow into the buckets does not perform any useful work in the sense or rotating the bucket and in fact, has an adverse effect on performance in that it creates drag, the forming of buckets which are tangential in nature is a significant factor in enhancing the efficiency of the motor and thus is a critical factor in the turbine bucket structure. For optimum efficiency, the turbine buckets should be tangential.
  • the turbine nozzle 3 has an inlet area Al and an outlet area A2. Since the volume of air flowing into the nozzle through area Al is the same as the volume of air flowing out of the nozzle through area A2, the ratio of the velocity of the air in VI to the air out V2 is inversely proportional to the ratio of the area in Al to the area out A2.
  • Figure 6 is a diagram for determining the blade inlet angle oC of the turbine rotor blades.
  • One leg of the triangle is proportional to the velocity VI and the other leg of the triangle is proportional to the velocity V2.
  • the nozzle angle 9 is the angle formed by the hypotenuse of the triangle and the leg proportional to the velocity V1. Referring to Figure 9, it can be seen that maximum efficiency occurs as 1/2 of the maximum rotor speed.
  • a second triangle is formed which defines the blade inlet anale ⁇ for optimizing the turbine motor efficiency.
  • the blade inlet angle ⁇ is defined by line 39 extending tangentially from the tip of the blade 23 and by line 41 which is tangent to the periphery of the rotor at the point at which line 39 intersects the rotor.
  • the rotor is constructed so that the blade inlet angle ⁇ as defined in Figure 5B is that which optimizes efficiency in accordance with the determination made in Figure 6. Therefore, blade inlet angle ⁇ ⁇ 27° and is preferably in the range of 15° ⁇ ⁇ ⁇ 27° the 15° angle corresponding to the nozzle angle 9.
  • the blade inlet angle is another critical factor which effects turbine efficiency.
  • Still another significant factor in enhancing the turbine efficiency is to provide a dynamically balanced turbine rotor.
  • the rotor is dynamically balanced about its axis of rotation, thus being dynamically balanced in the circumferential direction to thereby maintain a constant output, reducing drag and enhancing overall reliability by eliminating wear at particular points resulting from an unbalanced rotor through a wide range of operating speeds.
  • the maximum out-of-balance limit is 0.055 gram-centimeters.
  • the rear wall 27 of the turbine bucket should have a shape and relationship to nozzle width which optimizes efficiency.
  • the centerline radius ratios between 1.0 and 7.5 provide minimal losses in square cross-section ducts. Assuming that the losses due to inlet air turning in the turbine buckets are related to the Tosses occuring in curved ducts, then the same range of centerline radius ratios would be applicable to the turbine rotor buckets.
  • the bucket radius of curvature R CB W + r, where W it the width of the nozzle 3, and r is the centerline of air flow through the turbine bucket.
  • Area 43 shown in Figure 7 is a dead air space.
  • Figures 8A-8F illustrate the flow of air through the turbine rotor 13 in relationship to the rotation of the turbine rotor. Since Figures 8A-8F are schematic in nature, the various elements have been designated with the letter "a". As can be seen from Figures 8A-8F, air from nozzle 3a enters a bucket 29a and is turned through 180° by the rear wall 27a. The momentum transferred from the flowing air to the rotor moves the bucket to the right as illustrated. Since the buckets are on the periphery of the turbine rotor, the movement of the bucket to the right causes a rotation of the rotor in the direction of arrow A.
  • Figure 9 is a graph showing the relationship of the torque on rotor 13 in relationship to the efficiency, power and speed of the turbine motor.
  • Figure 10 is a graph showing the limiting ranges of pressure and air flow performance characteristics of vacuum cleaners which are required in order to provide an adequate power source for the efficient operation of the air-powered motor of the present invention. Most commercially available vacuum cleaners can perform within the required operating range.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP80103626A 1979-06-27 1980-06-26 Moteur à air et son rotor Withdrawn EP0021435A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US5266979A 1979-06-27 1979-06-27
US52669 1979-06-27

Publications (1)

Publication Number Publication Date
EP0021435A1 true EP0021435A1 (fr) 1981-01-07

Family

ID=21979135

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80103626A Withdrawn EP0021435A1 (fr) 1979-06-27 1980-06-26 Moteur à air et son rotor

Country Status (1)

Country Link
EP (1) EP0021435A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0233933A1 (fr) * 1985-08-09 1987-09-02 Scott & Fetzer Co Systeme de transmission par fluide pour petits appareils.
EP0430415A1 (fr) * 1989-12-01 1991-06-05 William Hendrick Williams Aspirateur de fluides et/ou solides
GB2288856A (en) * 1994-03-25 1995-11-01 Mervyn A Hutchings Air engines
CN1061133C (zh) * 1993-11-11 2001-01-24 株式会社金星社 贯流式通风机
GB2351533B (en) * 1999-07-01 2003-11-05 Ntn Toyo Bearing Co Ltd Air turbine spindle

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1103927A (fr) * 1953-07-17 1955-11-08 Ventilateur ou compresseur à courant transversal
US2962748A (en) * 1956-09-17 1960-12-06 Preco Inc Turbine driven sweeper attachments for vacuum cleaners
US3044100A (en) * 1958-09-12 1962-07-17 Joseph P Zaidan Rotary brush attachment for tank type vacuum cleaners
DE2203284A1 (de) * 1972-01-25 1973-08-02 Sueddeutsche Kuehler Behr Trommellaeufer fuer radialventilatoren, insbesondere fuer kraftfahrzeugbelueftungsanlagen
US4014625A (en) * 1973-08-20 1977-03-29 Teruo Yamamoto Transverse flow fan
DE2746202A1 (de) * 1977-10-14 1979-04-19 Heinrich Deierling Turbinenartige antriebsvorrichtung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1103927A (fr) * 1953-07-17 1955-11-08 Ventilateur ou compresseur à courant transversal
US2962748A (en) * 1956-09-17 1960-12-06 Preco Inc Turbine driven sweeper attachments for vacuum cleaners
US3044100A (en) * 1958-09-12 1962-07-17 Joseph P Zaidan Rotary brush attachment for tank type vacuum cleaners
DE2203284A1 (de) * 1972-01-25 1973-08-02 Sueddeutsche Kuehler Behr Trommellaeufer fuer radialventilatoren, insbesondere fuer kraftfahrzeugbelueftungsanlagen
US4014625A (en) * 1973-08-20 1977-03-29 Teruo Yamamoto Transverse flow fan
DE2746202A1 (de) * 1977-10-14 1979-04-19 Heinrich Deierling Turbinenartige antriebsvorrichtung

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0233933A1 (fr) * 1985-08-09 1987-09-02 Scott & Fetzer Co Systeme de transmission par fluide pour petits appareils.
EP0233933A4 (fr) * 1985-08-09 1989-11-20 Scott & Fetzer Co Systeme de transmission par fluide pour petits appareils.
EP0430415A1 (fr) * 1989-12-01 1991-06-05 William Hendrick Williams Aspirateur de fluides et/ou solides
US5168599A (en) * 1989-12-01 1992-12-08 Williams William H Wet and/or dry vacuum cleaning unit
CN1061133C (zh) * 1993-11-11 2001-01-24 株式会社金星社 贯流式通风机
GB2288856A (en) * 1994-03-25 1995-11-01 Mervyn A Hutchings Air engines
GB2351533B (en) * 1999-07-01 2003-11-05 Ntn Toyo Bearing Co Ltd Air turbine spindle

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Effective date: 19811214

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Inventor name: RODOWSKY JR., STANLEY JOSEPH