EP1193369B1 - Rotary eddy machine - Google Patents

Rotary eddy machine Download PDF

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Publication number
EP1193369B1
EP1193369B1 EP00919186A EP00919186A EP1193369B1 EP 1193369 B1 EP1193369 B1 EP 1193369B1 EP 00919186 A EP00919186 A EP 00919186A EP 00919186 A EP00919186 A EP 00919186A EP 1193369 B1 EP1193369 B1 EP 1193369B1
Authority
EP
European Patent Office
Prior art keywords
rotor
working cavity
working
stator
blades
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
EP00919186A
Other languages
German (de)
French (fr)
Other versions
EP1193369A4 (en
EP1193369A1 (en
Inventor
Vladimir Dmitrievich Anokhin
Anatoly Ivanovich Lepekha
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.)
Individual
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
Priority claimed from RU99109484/06A external-priority patent/RU2156863C1/en
Application filed by Individual filed Critical Individual
Publication of EP1193369A1 publication Critical patent/EP1193369A1/en
Publication of EP1193369A4 publication Critical patent/EP1193369A4/en
Application granted granted Critical
Publication of EP1193369B1 publication Critical patent/EP1193369B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • 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
    • 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
    • F01D1/36—Non-positive-displacement machines or engines, e.g. steam turbines characterised by non-bladed rotor, e.g. with drilled holes using fluid friction
    • 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
    • F04D29/18—Rotors
    • F04D29/188—Rotors specially for 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

Definitions

  • the present invention relates to the engineering industry field and can be used in pumps, compressors and engines.
  • a rotary-vortex machine is known e.g. US 5 328 325, containing a stator and rotor having a working torus-type cavity between them, comprising blades and a separator connected respectively to the stator and rotor and the working cavity is connected to a channel to supply the working medium arranged in the rotor and a channel for removal of the working medium.
  • Its section width is equal to a difference of maximum and minimum radii of the working cavity, determined accordingly as a distance from the axis to the most remote point of the working cavity and a distance from the axis to the nearest point (See published Application No. WO98/46886, cl. F01D 9/02, F04D 5/00, 1998).
  • a shortcoming of the indicated machine is a low efficiency caused by considerable volumetric and hydraulic losses caused by leaks from the working cavity through slit clearances between the rotor and stator, transfer of the working medium from the section with high pressure to the section with low pressure through the working cavity, low intensity of vortex formation at the inlet of the working medium to the working cavity and hydraulic losses of the vortex flow in the working cavity.
  • the object of the present invention is to provide means for increasing the machine efficiency at the expense of reduction of total volumetric and hydraulic losses by optimization of the ratio of the maximum radius to a width of the working cavity section effecting the values of leaks from the working cavity through slit clearances between the rotor and stator, transfer of the working medium from the section with high pressure to the section with low pressure through the working cavity, intensity of vortex formation at the inlet to the working cavity and hydraulic losses of the vortex flow in the working cavity.
  • the assigned objective is accomplished by the fact that in the rotor-vortex machine containing the rotor and stator having a torus-type working cavity between them, containing blades and separator, connected accordingly with the stator and rotor and the working cavity is connected to a channel to supply the working medium, arranged in the rotor and channel for removal of the working medium and its section width is equal to a difference of the maximum and minimum radii of the working cavity, determined accordingly as a distance from the axis to the most remote point of the working cavity and a distance from the axis to the nearest point, in compliance with the invention a ratio of the minimum radius of the working cavity with its section width is no less than 4.5 and no more than 9.5.
  • an angle of setting the blades is within the limits from 0 ° to 26 ° and every blade has a front edge faced to the rotor with a direction angle within the limits from 20 ° to 70 °.
  • a sum of setting angles of blades and direction of the front edge should be no less than 22 ° and no more than 94 °.
  • the rotary-vortex machine consists of stator 1 and rotor 2 having torus-type working cavity 3 between them. Contours of the working cavity (in the plane perpendicular to the machine axis) and contour of the working cavity section (in the meridian plane passing through the longitudinal axis of the machine plane) can be made round or with insignificant deviations from the round form (oval).
  • the working cavity incorporates blades 4 and separator 5 connected accordingly to stator 1 and rotor 2.
  • the working cavity has connection to channel 6 to supply the working medium, arranged in the rotor, and to channel 7 for removal of the working medium.
  • Maximum radius (R) of the working cavity is equal to a distance from the machine axis to the most remote point of the working cavity; minimum radius (r) is equal to a distance from the machine axis to the nearest point of the working cavity; width (h) of the working cavity is equal to difference (R-r) of the maximum and minimum radii.
  • Ratio (R/h) of the maximum radius of the working cavity to its section width is no less than 4.5 and no more than 9.5 (9.5 ⁇ R/h ⁇ 4.5).
  • Every blade 4 (See Figs 6 and 7) has front edge 8 faced to rotor 2 and arranged on crossing of surface 9 of blade 4 and median secant of surface 10 of blade 4.
  • Median secant surface 10 of blade 4 is a surface dividing in two parts a distance between the concave and convex sections of the blade surfaces counted over the normal to these surfaces.
  • Median secant 10 of blade 4 can be arranged as a geometric place of centers of spheres arranged between the indicated parts of the blade surface.
  • Angle ⁇ of the blade front edge direction i. e.
  • Angle ⁇ of setting the blades, i. e. angle between chord 15 and meridian plane 11, passing through center 12 of front edge 8 is no less than 0 ° and no more than 26 °.
  • a sum of angles ⁇ and ⁇ should be no less than 22 ° and no more than 94 °(22° ⁇ + ⁇ 94°).
  • Change of a ratio (R/h) of the maximum radius of the working cavity of the machine to its section width is connected with increase of the maximum radius of the working cavity (under condition of remaining the consumption characteristic of the machine) and results from one side in the increase of leaks from the working cavity through slit clearances between the rotor and stator, at the expense of increase of the area of the passage section of the slit clearance between the rotor and stator, and from the other side - in reduction of leaks of the working medium from the section with high pressure to the section with low pressure over the working cavity at the expense of increase of the working cavity length.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Reciprocating, Oscillating Or Vibrating Motors (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Joints Allowing Movement (AREA)
  • External Artificial Organs (AREA)
  • Threshing Machine Elements (AREA)
  • Vehicle Body Suspensions (AREA)
  • Soil Working Implements (AREA)
  • Nitrogen And Oxygen Or Sulfur-Condensed Heterocyclic Ring Systems (AREA)

Abstract

The rotary-vortex machine contains stator (1) and rotor (2). The rotor and stator form between them torus-type working cavity (3), which has blades (4) and separator (5) connected accordingly to the stator and rotor. The working cavity is connected to channel (6) to supply the working medium, arranged in the rotor, and to channel (7) for removal of the working medium. A section width of the working cavity is equal to a difference of the maximum and minimum radii of the working cavity determined accordingly as a distance from the axis to the most remote point of the working cavity and distance from the axis to the nearest point. A ratio of the maximum radius of the working cavity (R) to its section width (h) is no less than 4.5 and no more than 9.5. <IMAGE>

Description

Field of Engineering
The present invention relates to the engineering industry field and can be used in pumps, compressors and engines.
Prior Engineering Level
A rotary-vortex machine is known e.g. US 5 328 325, containing a stator and rotor having a working torus-type cavity between them, comprising blades and a separator connected respectively to the stator and rotor and the working cavity is connected to a channel to supply the working medium arranged in the rotor and a channel for removal of the working medium. Its section width is equal to a difference of maximum and minimum radii of the working cavity, determined accordingly as a distance from the axis to the most remote point of the working cavity and a distance from the axis to the nearest point (See published Application No. WO98/46886, cl. F01D 9/02, F04D 5/00, 1998).
A shortcoming of the indicated machine is a low efficiency caused by considerable volumetric and hydraulic losses caused by leaks from the working cavity through slit clearances between the rotor and stator, transfer of the working medium from the section with high pressure to the section with low pressure through the working cavity, low intensity of vortex formation at the inlet of the working medium to the working cavity and hydraulic losses of the vortex flow in the working cavity.
Invention Object
The object of the present invention is to provide means for increasing the machine efficiency at the expense of reduction of total volumetric and hydraulic losses by optimization of the ratio of the maximum radius to a width of the working cavity section effecting the values of leaks from the working cavity through slit clearances between the rotor and stator, transfer of the working medium from the section with high pressure to the section with low pressure through the working cavity, intensity of vortex formation at the inlet to the working cavity and hydraulic losses of the vortex flow in the working cavity.
The assigned objective is accomplished by the fact that in the rotor-vortex machine containing the rotor and stator having a torus-type working cavity between them, containing blades and separator, connected accordingly with the stator and rotor and the working cavity is connected to a channel to supply the working medium, arranged in the rotor and channel for removal of the working medium and its section width is equal to a difference of the maximum and minimum radii of the working cavity, determined accordingly as a distance from the axis to the most remote point of the working cavity and a distance from the axis to the nearest point, in compliance with the invention a ratio of the minimum radius of the working cavity with its section width is no less than 4.5 and no more than 9.5.
In addition, it is expedient that an angle of setting the blades is within the limits from 0 ° to 26 ° and every blade has a front edge faced to the rotor with a direction angle within the limits from 20 ° to 70 °. A sum of setting angles of blades and direction of the front edge should be no less than 22 ° and no more than 94 °.
This will provide the increase of efficiency of the machine at the expense of reduction of hydraulic losses of the vortex flow of the working medium in the working cavity and reduction of transfer of the working medium from the section of the working cavity with high pressure through a clearance between the blades and separator and through the working cavity in arrangement of values of the front edge direction angle and blade setting angle simultaneously close to their boundary values.
Brief Description of Drawings Figures
  • Fig. 1 presents a meridian section of the rotor-vortex machine with blades arranged in one plane.
  • Fig. 2 presents the lateral section of the machine presented in Fig. 1 in plane A-A.
  • Fig. 3 presents a section of the machine presented in Fig. 1 in plane B-B (enlarged).
  • Fig. 4 presents a meridian section of an alternative embodiment of a rotor-vortex machine with front edges of blades arranged on the cylinder surface.
  • Fig. 5 presents a lateral section of the machine presented in Fig. 4 in plane B-B.
  • Fig. 6 presents a section of the machine presented in Fig. 5, with cylinder plane Γ-Γ (enlarged).
  • Fig. 7 presents a lateral section of a blade presented in Figs 3 and 6, plane E-E passing through the center of its front edge, perpendicular to its meridian plane and chord connecting the ends of the front edge.
    • Preferred Embodiment of Invention
    The rotary-vortex machine consists of stator 1 and rotor 2 having torus-type working cavity 3 between them. Contours of the working cavity (in the plane perpendicular to the machine axis) and contour of the working cavity section (in the meridian plane passing through the longitudinal axis of the machine plane) can be made round or with insignificant deviations from the round form (oval). The working cavity incorporates blades 4 and separator 5 connected accordingly to stator 1 and rotor 2.
    The working cavity has connection to channel 6 to supply the working medium, arranged in the rotor, and to channel 7 for removal of the working medium.
    Maximum radius (R) of the working cavity is equal to a distance from the machine axis to the most remote point of the working cavity; minimum radius (r) is equal to a distance from the machine axis to the nearest point of the working cavity; width (h) of the working cavity is equal to difference (R-r) of the maximum and minimum radii.
    Ratio (R/h) of the maximum radius of the working cavity to its section width is no less than 4.5 and no more than 9.5 (9.5 ≥ R/h ≥ 4.5).
    Every blade 4 (See Figs 6 and 7) has front edge 8 faced to rotor 2 and arranged on crossing of surface 9 of blade 4 and median secant of surface 10 of blade 4. Median secant surface 10 of blade 4 is a surface dividing in two parts a distance between the concave and convex sections of the blade surfaces counted over the normal to these surfaces. Median secant 10 of blade 4 can be arranged as a geometric place of centers of spheres arranged between the indicated parts of the blade surface. Angle α of the blade front edge direction, i. e. angle between meridian plane 11 passing through center 12 of front edge 8 and tangent line 13 to middle line 14 of the lateral section of blade 4 in the crossing point of middle line 14 with front edge 8 (in center 12) is no less than 20 ° and no more than 70 °. Middle line of the lateral section is the line of crossing the median secant surface 10 of blade 4 and plane passing through center 12, perpendicular to meridian plane 11 and chord 15 connecting the opposite ends of front edge 8. Angle β of setting the blades, i. e. angle between chord 15 and meridian plane 11, passing through center 12 of front edge 8 is no less than 0 ° and no more than 26 °. A sum of angles α and β should be no less than 22 ° and no more than 94 °(22°<α+β<94°).
    In operation of the rotor-vortex machine in the engine mode the working medium flow is fed through channel 6 to working cavity 3, where under the effect of torus-type sections of the surface of the stator and rotor and blades acquires a vortex form, excluding a potentiality of its free flow over the working surface to channel 7. As a result separator 5 is under effect of the working medium pressure differential and rotor 2, to which the separator is connected, performs revolving motion, which is applied to the machine shaft.
    In operation of the machine in the mode of a pump or compressor with rotation of rotor 2 the working medium under effect of separator 5, blades 4 and torus-type sections of the surface of the stator and rotor acquires the vortex form motion. Such a motion of the working medium guards against its free flowing over the working cavity in the direction of rotation of the rotor from channel 6 to channel 7. As a result the vortex-form flow of the working medium is fed by the separator to channel 7, and through channel 6 a new quantity of the working medium is sucked in the working cavity.
    Change of a ratio (R/h) of the maximum radius of the working cavity of the machine to its section width, for example to the side of increase, is connected with increase of the maximum radius of the working cavity (under condition of remaining the consumption characteristic of the machine) and results from one side in the increase of leaks from the working cavity through slit clearances between the rotor and stator, at the expense of increase of the area of the passage section of the slit clearance between the rotor and stator, and from the other side - in reduction of leaks of the working medium from the section with high pressure to the section with low pressure over the working cavity at the expense of increase of the working cavity length. In addition increase of R results in the increase of the centrifugal acceleration applied to the working medium by the rotor and thus in more intensive vortex formation at the inlet of the working medium to the working cavity, which finally results in reduction of the working medium transfer over the working cavity. Experimental data showed that accomplishment of 9.5 ≥ R/h ≥ 4.5 is optimal with regard to the ratio of indicated characteristics, as well as optimal with regard to hydraulic losses of the vortex flow at the expense of friction of the working medium against the blades, rotor and stator.

    Claims (2)

    1. A rotary-vortex machine containing a stator (1) and rotor (2) having a working torus-type cavity (3), comprising blades (4) and a separator (5) connected respectively to the stator (1) and rotor (2) and the working cavity (3) is connected to a channel (6) to supply the working medium arranged in the rotor and a channel (7) for removal of the working medium. Its section width (4) is equal to a difference of maximum (R) and minimum radil (r) of the working cavity (3), determined accordingly as a distance from the axis to the most remote point of the working cavity and a distance from the axis to the nearest point, is characterized by the fact that a ratio of the maximum radius of the working cavity to its section width is no less than 4.5 and no more than 9.5.
    2. The rotor-vortex machine in compliance with claim 1 is characterized by the fact that an angle (8) of setting the blades is within the limits from 0 ° to 26 ° and every blade has a front edge faced to the rotor with a direction angle (α) within the limits from 20 ° to 70 °. A sum of setting angles of blades and direction of the front edge should be no less than 22 ° and no more than 94 °.
    EP00919186A 1999-05-12 2000-04-14 Rotary eddy machine Expired - Lifetime EP1193369B1 (en)

    Applications Claiming Priority (5)

    Application Number Priority Date Filing Date Title
    RU99109484/06A RU2156863C1 (en) 1999-05-12 1999-05-12 Rotary swirling machine
    RU99109484 1999-05-12
    RU99119419 1999-09-02
    RU99119419 1999-09-02
    PCT/RU2000/000132 WO2000070189A1 (en) 1999-05-12 2000-04-14 Rotary eddy machine

    Publications (3)

    Publication Number Publication Date
    EP1193369A1 EP1193369A1 (en) 2002-04-03
    EP1193369A4 EP1193369A4 (en) 2002-10-23
    EP1193369B1 true EP1193369B1 (en) 2005-09-07

    Family

    ID=26654014

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP00919186A Expired - Lifetime EP1193369B1 (en) 1999-05-12 2000-04-14 Rotary eddy machine

    Country Status (6)

    Country Link
    EP (1) EP1193369B1 (en)
    AT (1) ATE304117T1 (en)
    AU (1) AU3989700A (en)
    DE (1) DE60022510T2 (en)
    DK (1) DK1193369T3 (en)
    WO (1) WO2000070189A1 (en)

    Family Cites Families (6)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    US2042499A (en) * 1933-09-15 1936-06-02 Roots Connersville Blower Corp Rotary pump
    US3685287A (en) * 1970-12-08 1972-08-22 Mcculloch Corp Re-entry type integrated gas turbine engine and method of operation
    DE3822267A1 (en) * 1988-03-06 1989-12-07 Webasto Ag Fahrzeugtechnik RING CHANNEL BLOWER
    SU1697596A3 (en) * 1989-12-27 1991-12-07 В.Д.Анохин, А.Ф Винокуров, Ю.В.Гусев, С.Ю.Ермаков и А.И.Лепеха Stator of eddy current machine
    DE4020521A1 (en) * 1990-06-28 1992-01-02 Bosch Gmbh Robert PERIPHERAL PUMP, ESPECIALLY FOR DELIVERING FUEL FROM A STORAGE TANK TO THE INTERNAL COMBUSTION ENGINE OF A MOTOR VEHICLE
    RU2121608C1 (en) * 1997-04-11 1998-11-10 Анохин Владимир Дмитриевич Rotary-swirl machine

    Also Published As

    Publication number Publication date
    EP1193369A4 (en) 2002-10-23
    DK1193369T3 (en) 2005-11-14
    EP1193369A1 (en) 2002-04-03
    AU3989700A (en) 2000-12-05
    ATE304117T1 (en) 2005-09-15
    DE60022510D1 (en) 2005-10-13
    DE60022510T2 (en) 2006-07-13
    WO2000070189A1 (en) 2000-11-23

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