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WO2001002701A1 - Machine de compression centrifuge et dynamique d'un fluide - Google Patents

Machine de compression centrifuge et dynamique d'un fluide Download PDF

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Publication number
WO2001002701A1
WO2001002701A1 PCT/US2000/017044 US0017044W WO0102701A1 WO 2001002701 A1 WO2001002701 A1 WO 2001002701A1 US 0017044 W US0017044 W US 0017044W WO 0102701 A1 WO0102701 A1 WO 0102701A1
Authority
WO
WIPO (PCT)
Prior art keywords
vanes
channel
casing
disks
inlet
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.)
Ceased
Application number
PCT/US2000/017044
Other languages
English (en)
Inventor
Essam T. Awdalla
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.)
GIRGIS SAMI E
Original Assignee
GIRGIS SAMI E
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 GIRGIS SAMI E filed Critical GIRGIS SAMI E
Priority to AU54984/00A priority Critical patent/AU5498400A/en
Publication of WO2001002701A1 publication Critical patent/WO2001002701A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F01D1/06—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 traversed by the working-fluid substantially radially
    • 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
    • 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
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/168—Pumps specially adapted to produce a vacuum
    • 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
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2205—Conventional flow pattern
    • F04D29/2211—More than one set of flow passages
    • 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
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/2255—Special flow patterns flow-channels with a special cross-section contour, e.g. ejecting, throttling or diffusing effect
    • 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
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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

Definitions

  • the present invention relates to rotary fluid pressurizing machines that utilize the
  • Rotary fluid pressurizing machines are well known devices, used in several fields to develop a pressure gradient between two points across a fluid stream. They are designed for use with compressible fluids, to provide a positive pressure gradient, i.e.,
  • compressors or a negative pressure gradient, i.e., vacuum pumps, or with incompressible
  • Rotary compressors are machines that increase the pressure of a compressible
  • Rotary vacuum pumps are machines that reduce the pressure of gas or air in a
  • a rotary pump is a machine used to draw an incompressible fluid, i.e., liquid, into
  • the ram pressure rise is a well investigated phenomenon by those involved in the design of ramjet engines, and inlet ducts of turbo-jet engines, whether of the subsonic, transonic, or supersonic types.
  • Ram pressure rise occurs when a fluid is rammed into a suitably shaped diffuser moving at a high speed, wherein the fluid is diverged with conversion of the kinetic energy of the fluid relative to the moving diffuser into a rise in the pressure energy of the fluid, referred to as the ram pressure rise.
  • incompressible fluids to develop either a positive, or a negative pressure gradient, between two points across the fluid stream, utilizing the phenomenon of ram pressure
  • pressurizing machine that is simple in design, and can handle a wide range of fluid mass
  • pressurizing machine for applications wherein adjustable control of the volumetric delivery of the pressurized fluid is needed during operation.
  • the present invention provides rotary ram fluid pressurizing
  • the rotary ram fluid pressurizing machine comprises a
  • stationary casing having an inlet passage for admission of fluid and an exit passage for
  • a drive shaft supported by an arrangement of bearings, for rotation in a given direction inside the casing and extending to a drive receiving end
  • the rotor located outside the casing; and a rotor assembly housed inside the casing.
  • the rotor is located outside the casing; and a rotor assembly housed inside the casing.
  • first disk surrounding the drive shaft and lying in a first plane
  • each of the disks having a large open center and a widened rim, and with each of the disks having a
  • each of the vanes has a first edge attached to the inner surface of the first disk, a second edge attached to the inner surface of the second disk, a relatively radially outwards leading edge or tip and a relatively radially inward trailing
  • each vane curved preferably smoothly from its leading edge towards its trailing edge.
  • Each vane has a concave displacing surface and a convex
  • the channel has an inlet communicating
  • the divergence of the channel is provided by designing the boundaries confining the channel between them so that: 1) the axial width of the channel, and/or 2) the width between the opposing parts of the surfaces of the two adjacent vanes confining the
  • channel between them increase preferably gradually from the inlet of the channel towards its outlet, and hence, the cross-sectional area of the channel increases preferably gradually
  • the gradual increase in the axial width of the channel is provided by designing the
  • vanes with suitable angles of inclination at their different parts, according to the desired rate of divergence of the channel described above.
  • vanes and is gradually displaced to the space relatively radially inwards of the vanes
  • the fluid is fed to the space relatively radially outwards of the vanes through one
  • the pressurized fluid is discharged through one or more than one opening(s) in either one or both of the disks, within the disk(s) portion confined between the vanes and the drive shaft, and communicating with the exit passage in the casing.
  • the volumetric capacity of the rotary ram fluid pressurizing machine depends on the number of diverging channels confined between the vanes, their dimensions, and the speed of the vanes leading edges. In the present embodiment, to increase the volumetric capacity without marked increase in the height of the vanes, to avoid the formation of
  • vanes of the further level(s) are quite similar to those of the single leveled embodiment,
  • the circumferentially arranged vanes and the drive shaft may be provided, to functionally communicate the formed sub-spaces inside the rotor.
  • the fixed disk(s) may provide
  • the obtainable ram pressure rise from this embodiment will have a certain upper limit.
  • vanes arranged in one or more concentric sets, inward of the periphery, may be used, with the design and operation of the further vanes being quite similar to those of the single stage embodiment discussed herein before, so that in operation, the fluid in the space relatively radially outwards of each of the vane sets is rammed into the inlets of the diverging channels formed between the vanes, and is gradually displaced to the space relatively radially
  • the rotary ram fluid pressurizing machine comprises a
  • stationary casing having an inlet passage for admission of fluid and an exit passage for
  • a drive shaft supported for rotation in a given direction inside the casing by an arrangement of bearings, and extending to a drive receiving end
  • the rotor located outside the casing; and a rotor assembly housed inside the casing.
  • the rotor is located outside the casing; and a rotor assembly housed inside the casing.
  • first disk surrounding the drive shaft and lying in a first plane
  • the disks having a relatively outer surface facing its adjacent part of the casing and a relatively inner surface, with the inner surfaces of the two disks defining an annular space in-between, and a plurality of vanes arranged circumferentially within the annular space defined in-between the inner surfaces of the disks.
  • Each of the vanes has a first edge attached to the inner surface of the first disk, a second edge attached to the inner surface
  • midpoint of the vane decreases preferably gradually from its leading edge towards its
  • Each vane has a
  • each two adjacent vanes defining a channel between them, with the channel confined by a part of the concave surface of one vane and its opposing part of the convex surface
  • the channel has an inlet communicating with the space relatively radially inwards of the
  • vanes and an outlet communicating with the space relatively radially outwards of the
  • the boundaries of the channel are formed of the opposing parts of the surfaces of the two adjacent vanes and of the opposing parts of the disks' surfaces related to the
  • the divergence of the channel is provided by designing the boundaries confining the channel between them so that the axial width of the channel and/or the width between the opposing parts of the surfaces of the two adjacent vanes confining the channel between them increase preferably gradually from the inlet of the channel towards its outlet, and hence, the cross-sectional area of the channel increases preferably gradually from its inlet towards its outlet.
  • sloping preferably gradually from the inlet of the channel towards its outlet.
  • vanes with suitable angles of inclination at their different parts, according to the desired rate of divergence of the channel.
  • vanes and is gradually displaced to the space relatively radially outwards of the vanes
  • the fluid is fed to the space relatively radially inwards of the vanes through one,
  • inlet port in the casing communicating with the space, through one, or more than one, inlet port in the casing, communicating with the space, through one, or
  • the pressurized fluid is discharged from the space relatively radially outwards of the vanes through one or more than one exit passage(s) in the casing.
  • volumetric capacity of the rotary ram fluid pressurizing machine depends on the number of diverging channels confined between the vanes, their dimensions, and the speed of the vanes leading edges, so, to increase the volumetric capacity in the present
  • the intervening disk(s) may be provided with opening(s) in the portion of the intervening disk(s)
  • the obtainable ram pressure rise from this embodiment will have a certain upper limit.
  • vanes arranged in one or more concentric sets, inward of the periphery, may be used, with the design and operation of the further vanes being quite similar to those of the single stage embodiment discussed herein before, so that in operation, the fluid in the space relatively radially inward of each of the vane sets is rammed into the inlets of the diverging channels formed between the vanes, and is gradually displaced to the space relatively radially outwards of the set of vanes while being diverged.
  • the present invention also provides a rotary ram fluid pressurizing machine with
  • variable capacity rotary ram fluid pressurizing machine the variable capacity rotary ram fluid pressurizing machine
  • a stationary casing having an inlet passage for admission of the fluid and an exit passage for discharge of the pressurized fluid; a first shaft supported for rotation in a give direction in the casing by an arrangement of bearings, and extending to a drive receiving end located outside the casing; a second shaft concentric with the first shaft, and supported by an arrangement of bearings for rotation in the casing, with the rotational support of one of the two shafts designed to allow for axial movement of the shaft, while the rotational support of the other shaft is designed so that the shaft is axially fixed; and a
  • the rotor assembly located inside the casing.
  • the rotor assembly includes a first disk
  • each of the disks having a relatively outer
  • Each of the vanes has a first edge attached to the inner surface of one of the disks.
  • each vane curved preferably
  • each vane has a concave displacing surface and a convex surface, with the opposing parts of the surfaces of each two adjacent vanes defining a channel between them, with the channel confined by a part of the concave surface of one vane and its opposing part of the convex surface of an adjacent vane. The rest of the concave surface freely communicates
  • the channel has an inlet communicating with the space relatively radially
  • the divergence of the channel is provided by designing the boundaries confining
  • the gradual increase in the width between the opposing parts of the surfaces of the two adjacent vanes is provided by designing the vanes with suitable angles of inclination at their different parts, according to the desired rate of divergence of the channel.
  • the volumetric delivery is regulated by variations in the axial width
  • the axial movement of the axially movable shaft can be provided by mechanical,
  • electro-mechanical, electrical, hydraulic, or pneumatic means are well known
  • vanes arranged in one, or more concentric sets, inward of the periphery, may be
  • each of the further vanes having an edge forming male end in fluid tight communication with a further female groove in the inner surface of one of the disks.
  • the design and operation of the vanes of the further set(s) are quite similar to those of the single stage variable capacity rotary ram fluid pressurizing machine described herein before, wherein on operation, the fluid in the space relatively radially outwards of each of the vane sets is rammed into the inlets of the diverging channels formed between the vanes, and is gradually displaced to the space relatively radially
  • machine comprises a stationary casing, having an inlet port(s) for admission of the fluid
  • a first shaft supported for rotation in a given direction in the casing, by an arrangement of bearings, and extending to
  • the rotor assembly includes a first
  • each of the disks having a relatively outer surface facing its adjacent part of the casing, and a relatively inner surface, with inner surfaces of the two disks defining an annular space in-between, and a plurality of vanes arranged circumferentially within the annular space defined in-between the inner surfaces
  • Each of the vanes has a first edge attached to the inner surface of one of the disks, a second edge forming male end in fluid tight communication with a female
  • vane has a convex displacing surface and a concave surface, with the opposing parts of
  • the channel has an inlet communicating with the space relatively
  • the boundaries of the channel are formed of the opposing parts of the surfaces of the two adjacent vanes and of the opposing parts of the disks' surfaces related to the channel and confined between the opposing parts of the surfaces of the two adjacent vanes, with the channel diverging from its inlet towards its outlet.
  • the divergence of the channel is provided by designing the boundaries confining the channel between them so that the axial width of the channel and/or the width between the opposing parts of the surfaces of the two adjacent vanes confining the channel
  • the cross-sectional area of the channel increases preferably gradually
  • the gradual increase in the axial width of the channel is provided by designing the
  • the volumetric delivery is regulated by variations in the axial width of the diverging channels confined between the vanes and the inner surfaces of the disks. This is achieved by axially moving the axially movable shaft, with the axial movement of the shaft being transmitted to the disk mounted on it, which results in changing the axial width between the inner surfaces of the two disks, and hence, the axial width of the diverging channels.
  • the axial movement of the axially movable shaft can be provided by mechanical,
  • electro-mechanical, electrical, hydraulic, or pneumatic means are well known
  • vanes arranged in one, or more concentric sets, inward of the periphery, may be
  • each of the further vanes having an edge forming male end in fluid tight
  • the rotary ram fluid pressurizing machine provided in the present invention can be used in the applications wherein two discharge passages are used, with the provided pressurized fluid being discharged through either one of the two discharge passages, or distributed between both of them with an adjustable variable ratio, as needed during operation.
  • the rotary ram fluid pressurizing machine comprises a stationary casing having an inlet passage(s) for admission of the fluid and two exit
  • each exit passage having a separate exit port(s); an axially movable shaft,
  • the rotor located outside the casing; and a rotor assembly housed inside the casing.
  • the rotor is located outside the casing; and a rotor assembly housed inside the casing.
  • first disk surrounding the shaft and lying in a first plane transverse
  • a second disk surrounding the shaft and lying in a second plane transverse to the rotational axis of the shaft and axially spaced from the first
  • each of the disks having a relatively outer surface facing its
  • Each of the vanes has a first edge attached to the inner surface of the first disk, a second edge attached to the inner surface of the second disk, a relatively radially inward leading edge or tip and a relatively radially outward trailing edge or tail, with each vane curved preferably smoothly from its leading edge towards its trailing edge.
  • the average angles of inclination of the successive portions of the vane with respect to a plane comprising the midpoint of the vane and perpendicular to a radial plane including the rotational axis of the rotor and the midpoint of the vane decreases preferably gradually from its leading edge towards its trailing edge, within a range from about +56 to about -
  • Each vane has a convex displacing surface and a concave surface, with the
  • the channel has an inlet communicating with the space relatively radially inwards of the vanes, and an outlet communicating with the space relatively
  • the divergence of the channel is provided by designing the boundaries confining
  • the channel between them so that the axial width of the channel and/or the width between the opposing parts of the surfaces of the two adjacent vanes confining the channel between them increase preferably gradually from the inlet of the channel towards its outlet, and hence, the cross-sectional area of the channel increases preferably gradually from its inlet towards its outlet.
  • the gradual increase in the axial width of the channel is provided by designing the part(s) of the surface(s) of one (or both) of the disks related to the channel and
  • the obtainable ram pressure rise from this embodiment will have a certain upper limit.
  • the axial movement of the axially movable shaft can be provided by mechanical, electro-mechanical, electrical, hydraulic, or pneumatic means. Such means are well known to those of ordinary skill in the art.
  • the present invention also provides a rotary ram fluid pressurizing machines, that is relatively simpler in design, for applications where design simplicity is of more concern than providing optimum efficiency during operation. Accordingly, in one
  • the rotary ram fluid pressurizing machine comprises a stationary casing
  • the rotor assembly includes one
  • vanes has a first edge attached to its related surface of the disk, a second free edge, a
  • each vane curved preferably smoothly from its leading edge towards its
  • Each vane has a concave displacing surface and a convex surface with the opposing parts of the surfaces of each two adjacent vanes defining a channel between them, with the channel confined by a part of the concave surface of one vane and the opposing part of the convex surface of an adjacent vane. The rest of the concave surface freely communicates with the space relatively radially
  • the channel has an inlet
  • the divergence of the channel is provided by designing the boundaries confining
  • said channel between them so that: 1) the axial width of the channel, and/or 2) the width
  • the gradual increase in the axial width of the channel is provided by designing the part of the surface of the disk related to the channel and confined between the opposing parts of the surfaces of the two adjacent vanes so that it is sloping preferably gradually from the inlet of the channel towards its outlet.
  • the gradual increase in the width between the opposing parts of the surfaces of the two adjacent vanes is provided by
  • vanes with suitable angles of inclination at their different parts, according to the desired rate of divergence of the channels described above.
  • vanes and is gradually displaced to the space relatively radially inwards of the vanes
  • volumetric capacity of a rotary ram fluid pressurizing machine depends on the number of diverging channels confined between the vanes, their dimensions, and the
  • each of the vanes having an edge attached to the related surface of the disk, and a free
  • Opening(s) in the disk(s) portion confined between the circumferentially arranged vanes and the drive shaft may be provided, to provide functional communication between the sub-spaces formed inside the rotor.
  • the speed of the vane leading edges cannot be increased above the speed of sound without the formation of shock waves in the case of compressible fluids. Similarly, the speed of the vane leading edges cannot be increased above the critical velocity without
  • each of the vane sets is rammed into the inlets of the diverging channels formed between the vanes, and is gradually displaced to the space relatively radially
  • the rotary ram fluid pressurizing machine comprises a
  • stationary casing having an inlet passage for admission of fluid and an exit passage for
  • the rotor assembly includes one disk surrounding the drive shaft and lying in a plane transverse to the rotational axis of the drive shaft, and secured for rotation with it, and a plurality of vanes arranged circumferentially within the annular space defined in-between one of the surfaces of the disk and the opposing part of the inner surface of the casing.
  • Each of the vanes has a first edge attached to the related inner surface of the disk, a second free edge,
  • each vane curved preferably smoothly from its leading edge towards its
  • Each vane has a convex displacing surface and a concave surface, with the opposing parts of the surfaces of each two adjacent vanes defining a channel
  • the channel has an inlet communicating with the
  • the divergence of the channel is provided by designing the boundaries confining
  • said channel between them so that: 1) the axial width of the channel, and/or 2) the width
  • channel between them increase preferably gradually from the inlet of the channel towards
  • the outlet, and hence, the cross-sectional area of the channel increases preferably
  • the gradual increase in the axial width of the channel is provided by designing the
  • volumetric capacity of a rotary ram fluid pressurizing machine depends on the number of diverging channels confined between the vanes, their dimensions, and the speed of the vanes leading edges.
  • each of the vanes having an edge
  • circumferentially arranged vanes and the drive shaft may be provided, to provide
  • the fluid in the space relatively radially inward of each of the vane sets is rammed into the inlets of the diverging channels formed between the vanes, and is gradually displaced to the space relatively radially outwards of the set of vanes while being diverged.
  • the overall ram pressure rise in the space relatively radially outwards of the outermost set of vanes will equal the multiplication of the ram pressure rises obtained from the successive concentric sets of vanes.
  • the attachment of the vane edges to their related surfaces of the disks may be by casting the disk integrally with the vanes, or by fastening
  • Sealing means may be provided at one or more sites, in the clearance between the
  • the sealing means may be of the
  • the resulting ram pressure rise depends on the speed of the vane leading edges
  • Fluid directing vanes may be
  • reaction force of the fluid acting on the displacing surface of each of the vanes can be resolved into two components; a radial component and a tangential
  • the resulting rise in the temperature of the pressurized fluid will be minimal, with marked improvement in the efficiency of subsequent compression, when needed, and which enables the recovery of more heat energy from the exhaust gases,
  • provided pressurized fluid through the exit passage(s) may be intermittent, i.e., when used
  • exit passage(s) e.g. when used in pumps or with propulsive nozzles, or means for rated accelerated discharge of the pressurized fluid being provided e.g. when used in gas
  • Fig. 1 is a sectional view in a schematic representation of an exemplary embodiment of a rotary ram compressor, in accordance with the present invention.
  • Fig. 2 is a cross sectional view, taken at the plane of line 2 -2 in Fig. 1.
  • Fig. 3 is a partial cross sectional view, taken at the plane of line 3 - 3 in Fig. 2.
  • Fig. 4 is a sectional view in a schematic representation of an exemplary embodiment of another rotary ram compressor, in accordance with the present invention.
  • Fig. 5 is a cross sectional view, taken at the plane of line 5 - 5 in Fig. 4.
  • Fig. 6 is a partial cross sectional view, taken at the plane of line 6 - 6 in Fig. 5.
  • Fig. 7 is a sectional view in a schematic representation of an exemplary
  • pressurized fluid is discharged through a propelling nozzle.
  • Fig. 8 is a cross sectional view, taken at the plane of line 8 - 8 in Fig. 7.
  • Fig. 9 is a sectional view in a schematic representation of an exemplary embodiment of a multi-level, multi-stage rotary ram compressor, in accordance with the
  • Fig. 10 is a cross sectional view, taken at the plane of line 10 - 10 in Fig. 9.
  • Fig. 11 is a partial sectional view in a schematic representation of an exemplary
  • Fig. 12 is a partial cross sectional view, taken at the plane of line 12 - 12 in Fig.
  • Fig. 13 is a sectional view in a schematic representation of an exemplary
  • Fig. 14 is a cross sectional view, taken at the plane of line 14 - 14 in Fig. 13.
  • Fig. 15 is a sectional view in a schematic representation of an exemplary embodiment of a combined rotary ram compressor, in accordance with the present invention.
  • Fig. 16 is a cross sectional view, taken at the plane of line 16 - 16 in Fig. 15.
  • Fig. 17 is a cross sectional view, taken at the plane of line 17 - 17 in Fig. 15.
  • Figs. 18, 19 are sectional views in a schematic representation of an exemplary
  • variable capacity rotary ram compressor in accordance with the present
  • Figs. 20, 21 are sectional views in a schematic representation of an exemplary
  • variable capacity rotary ram pump in accordance with the present
  • FIGs. 22 - 24 are sectional views in a schematic representation of an exemplary
  • Figs. 25 - 29 are schematic representations of alternatives in which the diverging
  • Fig. 30 is a sectional view in a schematic representation of an exemplary
  • Fig. 31 is a sectional view in a schematic representation of an exemplary
  • FIG. 32 is a sectional view in a schematic representation of an exemplary embodiment of another rotary ram pump, in accordance with the present invention.
  • Fig. 33 is a sectional view in a schematic representation of an exemplary
  • Fig. 34 illustrates the angles of inclination of the vanes of the rotor of a rotary ram
  • Fig. 35 illustrates the angles of inclination of the vanes of the rotor of another
  • Fig. 1 is a sectional view in a schematic representation of an embodiment in
  • stationary casing 21 having an inlet passage 22 for admission of compressible fluid 23
  • the rotor assembly includes a first disk 28, a second disk 29, and a plurality of vanes 30 arranged circumferentially within the annular space defined in-between the relatively inner surfaces of the disks, with both of the disks being secured for rotation with the drive shaft.
  • Each of the disks has a relatively inner surface 31, forming one of the boundaries of the space confined inside the
  • Each of the circumferentially arranged vanes has a first edge 33 attached to the inner surface of the
  • Fig.2 which is a cross sectional view, taken at the plane of line 2 - 2 in Fig. 1, each of
  • the vanes has a relatively radially outwards leading edge or tip 35. and a relatively
  • Each vane is preferably smoothly curved from its
  • Each vane has a concave displacing
  • Fig. 3 which is a cross sectional view, taken at the plane of line 3 - 3 in Fig. 2, each of the opposing parts of the inner surfaces of the disks confined
  • the pressurized fluid is discharged through openings 46 in one of the disks 29,
  • leading edges 35 which depends on the rotational speed of the rotor assembly, and its dimensions.
  • the speed of the vane leading edges must be kept within the subsonic range, to avoid the formation of shock waves, which if formed, will interfere with the feeding of the fluid to the inlets 42 of the diverging channels 39.
  • Fig. 4 is a sectional view in a schematic representation of another embodiment in
  • stationary casing 51 having an inlet passage 52 for admission of compressible fluid, 53
  • the rotor assembly includes a first
  • Each of the disks has a relatively inner surface 61, forming one of the boundaries of the space confined inside the rotor, and a relatively outer surface 62 facing its adjacent part of the casing.
  • Each of the circumferentially arranged vanes has a first edge 63 attached to the inner surface of the first disk and a second edge 64 attached to the inner surface of the second disk.
  • Fig. 5 which is a cross sectional view, taken at the plane of line 5 - 5 in Fig.
  • each of the vanes has a relatively radially outwards leading edge or tip 65 and a
  • Each vane is preferably smoothly
  • Each vane has a concave displacing surface 67 and a convex surface 68, with the opposing parts of the
  • channel has an inlet 72 communicating with the space relatively radially outwards of the
  • vanes and an outlet 73 communicating with the space relatively radially inwards of the
  • Fig. 6 which is a cross sectional view, taken at the plane of line 6 - 6 in Fig. 5, the part of the inner surface of the second disk confined between the opposing parts of the
  • Fig. 7 is a sectional view in a schematic representation of an embodiment in
  • pressurized fluid is discharged through a propelling nozzle.
  • rotary ram pump in this embodiment are a stationary casing 81 having an inlet passage 82
  • the rotor assembly includes a
  • first disk 89 a second disk 90, and a plurality of vanes arranged circumferentially in two
  • the disks 89, 90, 93 are secured for rotation with the drive shaft.
  • each of the circumferentially arranged vanes of the first level 91 has a first edge 98 attached to the inner surface of the first disk 94 and a second edge 99 attached to its related surface of the intervening disk 93.
  • Each of the circumferentially arranged vanes of the second level 92 has a first edge 100 attached to the inner surface of the second disk 95, and a second edge 101 attached to its related surface of the intervening
  • Fig. 8 which is a cross sectional view, taken at the plane of line 8
  • each of the vanes has a relatively radially outwards leading edge or tip 102
  • Each vane is preferably
  • rotational axis of the rotor and the midpoint of the vane decreases gradually from its leading edge towards its trailing edge within a range from about +22 to about -42
  • Each vane has a concave displacing surface 104 and a convex surface 105, with
  • the channel is confined by a part of the concave surface of one vane and
  • the channel has an inlet 109 communicating with the space 108
  • the boundaries of the channel are formed of the opposing parts of the surfaces of the two adjacent vanes and of the two opposing parts of the inner surfaces of the disks related to the channel and confined between the opposing parts of the surfaces of the two adjacent vanes 111, 112.
  • the width between the opposing parts of the surfaces of the two adjacent vanes increases gradually from
  • the inlet of the channel 109 towards its outlet 110 Accordingly, the channel diverges from its inlet towards its outlet.
  • Means for contact sealing 113 are provided in the clearance between the outer
  • pressurized fluid is discharged through a propelling nozzle, can be used in the propulsion of different types of sea vehicles, with a propulsive efficiency more than that provided by other conventional means, e.g., propellers and the like.
  • Fig. 9 is a sectional view in a schematic representation of another embodiment in accordance with the present invention, a multi-level, multi-stage rotary ram compressor.
  • the main components of the rotary ram compressor in this embodiment are a stationary casing 121 having an inlet passage 122 for admission of compressible fluid
  • the rotor assembly includes a first
  • Each of the vane levels has three concentric sets of vanes 130, 131, 132, with two
  • Each of the vanes has two edges, each
  • Fig. 10 which is a cross sectional view, taken at the plane of line 10 - 10 in Fig.
  • each of the vanes has a relatively radially outwards leading edge or tip 135, and a
  • each vane preferably smoothly
  • each vane has a concave displacing surface 137 and a convex surface 138. Opposing parts of the surfaces of each two adjacent vanes define a channel 139 between them, with the channel confined by a part of the concave surface of one vane and its opposing part of the convex surface
  • channel 139 having an inlet 142 communicating with the space 141 relatively radially
  • the boundaries of the channel are formed of: 1) the
  • vanes 130 increases gradually from the inlet of the channel towards its outlet.
  • each of the channels confined between the adjacent vanes diverges from its inlet towards its outlet.
  • the fluid in the space relatively radially outwards of each of the concentric sets of vanes is rammed into the diverging channels confined in-between the vanes of each of the concentric sets, and is gradually displaced to the space relatively radially inwards of the vanes, while being diverged, resulting into a rise in the static
  • a ducted fan 146 is used for rated accelerated discharge of the provided
  • Fig. 11 is a partial sectional view in a schematic representation of an exemplary
  • components of the rotary ram pump in this embodiment are a stationary casing 151
  • Fig. 12 which is a partial cross sectional view, taken at the plane of line 12 - 12 in Fig. 11, a drive shaft 157 supported for rotation in a given direction inside the casing by an arrangement of bearings 158, and extending to a drive receiving end located
  • the rotor assembly includes a first disk 159, a second disk 160, and a plurality of vanes 161 arranged circumferentially within the annular space defined in-between the relatively inner
  • Both of the disks are secured for rotation with the drive shaft 157.
  • Each of the disks has a relatively inner surface 162, forming one of the boundaries of the
  • Each of the circumferentially arranged vanes has a first edge attached to
  • second disk 165 a relatively radially inward leading edge or tip 166 and a relatively
  • Each vane is preferably smoothly curved from its leading edge towards its trailing edge, with the average angles of inclination of the
  • Each vane has a convex displacing
  • the channel has an inlet 173 communicating with the space 171 relatively radially inwards of the vanes, and an outlet 174 communicating with the space 172 relatively radially outwards of the vanes.
  • the boundaries of the channel are formed of the opposing parts of the surfaces of the two adjacent vanes and of the opposing parts of the disks' surfaces related
  • adjacent vanes increases gradually from the inlet of the channel towards its outlet, so that
  • the channel diverges from its inlet towards its outlet.
  • the pressurized fluid is discharged through the volute chamber 154
  • leading edges 166 which depends on the rotational speed of the rotor assembly, and its
  • the rotary ram pump provided in the present embodiment can be used to move or lift incompressible fluids, i.e., liquids, with an overall efficiency more than that of the conventionally used types of rotary pumps.
  • Fig. 13 is a sectional view in a schematic representation of an embodiment in accordance with the present invention of a two-stage rotary ram vacuum pump.
  • stationary casing 181 having an inlet passage 182 communicating with the container to be
  • the rotor assembly includes a first disk 188, a second disk 189, and a plurality of vanes
  • Each of the vanes has two edges each attached to the relatively
  • Fig. 14 which is a cross sectional view
  • each of the vanes has a relatively radially
  • inward leading edge or tip 192 and a relatively radially outward trailing edge or tail 193.
  • Fig. 15 is a sectional view in a schematic representation of an exemplary
  • the main components of the combined rotary ram compressor in this embodiment are a stationary casing 201 having an inlet passage 202 for admission of
  • compressible fluid e.g., gas, or vapor, or a mixture of gases and vapors 203, and an exit
  • the rotor assembly includes a first disk 208, a second disk 209,
  • the rotor assembly is functionally divided into two serially disposed
  • compressor stage comprises a plurality of vanes arranged in two axially stacked levels, with the vanes of each of the levels arranged in three concentric sets 211, 212, 213, with a fixed intervening disk 214 between the vane levels.
  • the second compressor stage comprises a plurality of vanes arranged in three concentric sets 215, 216, 217, with the three disks 208, 209, 210 being secured for rotation with the drive shaft 206.
  • the fixed intervening disk is attached to the casing, with an arrangement of bearings provided between the disk and the drive shaft.
  • Each of the vanes of the first compressor stage has
  • Fig. 16 which is a cross sectional
  • 212, 213 has a relatively radially inward leading edge or tip 218, and a relatively radially inward leading edge or tip 218, and a relatively
  • Each vane preferably smoothly curves from
  • Each vane has a convex displacing
  • the channel has an inlet 225 communicating with the space 223 relatively radially inwards of the vanes, and an outlet 226 communicating with the space relatively radially outwards of the vanes 224.
  • the boundaries of the channel are formed of the opposing parts of the surfaces of the two adjacent vanes and of the opposing parts of the disks' surfaces related to the channel and confined between the opposing parts of the surfaces of the two
  • vanes 227, 228 are sloped, so that the axial width of each of the channels confined
  • Each of the vanes of the second compressor stage has two edges, each attached
  • vanes of the second stage 215, 216, 217 has a relatively radially outwards leading edge
  • Each vane preferably has a relatively radially inward trailing edge or tail 230.
  • each vane has a concave displacing surface 231 and a convex surface 232, with the opposing parts of the surfaces of each two adjacent vanes defining a channel 233 between them.
  • the channel is confined by a part of the concave surface of one vane and its opposing part of the convex surface of an adjacent vane. The rest of the concave
  • the channel has an inlet 236 communicating with the space 235
  • adjacent vanes of the relatively outermost set of vanes 238 are sloped so that the axial
  • compressor stage increases gradually from the inlet of the channel confined between
  • each of the channels confined between the adjacent vanes diverges from its inlet towards its outlet.
  • the fluid in the inlet passage 202 is rammed through the diverging channels confined in-between the concentric sets of vanes of the first compressor stage to an intermediate passage 239, from which the partially pressurized fluid 240 is rammed through the diverging channels confined in-between the concentric sets of vanes of the second compressor stage to the exit passage 204.
  • the overall ram pressure rise in the exit passage 204 will equal the multiplication of the ram pressure rises obtained from the two compressor stages.
  • a ducted fan 241 is used for rated accelerated discharge of the provided
  • Figs. 18, 19 are sectional views in a schematic representation of an embodiment
  • variable capacity rotary ram compressor The main components of the variable capacity rotary ram compressor in this case
  • embodiments are a stationary casing 251, having an inlet passage 252 for admission of the
  • compressible fluid e.g., gas, or vapor, or a mixture of gases and vapors 253 provided with
  • the rotor assembly include, a first disk 261 secured for rotation with the first shaft 256, a second disk 262 secured for rotation with the second axially movable shaft 258, and a
  • Each of the disks has a relatively inner surface
  • Each of the vanes has a first
  • edge 263 attached to the inner surface of the first disk 261, a second edge 264 forming a
  • the second disk 262 a relatively radially outwards leading edge or tip, and a relatively radially inward trailing edge or tail (not shown in the drawing).
  • the volumetric delivery is regulated by variations in the axial width of
  • the axial movement of the axially movable shaft can be provided by mechanical, electromechanical, electrical, hydraulic, or pneumatic means. Such means are well known to those of ordinary skill in the art.
  • Figs. 20, 21 are sectional views in a schematic representation of an embodiment, in accordance with the present invention, of a variable capacity rotary ram pump in the full and partial capacity operating positions, respectively.
  • variable capacity rotary ram pump The main components of the variable capacity rotary ram pump in this case
  • embodiments are a stationary casing 271 having an inlet passage 272 for admission of fluid
  • the rotor assembly includes a first disk 280 secured for rotation with
  • Each of the disks has a
  • first edge 282 attached to the inner surface of the first disk 280, a second
  • the volumetric delivery is regulated by variations in the axial width of the diverging channels confined between the vanes and the inner surfaces of the disks.
  • the axial movement of the axially movable shaft can be provided by mechanical,
  • electro-mechanical, electrical, hydraulic, or pneumatic means are well known
  • Figs. 22 - 24 are sectional views in a schematic representation of an embodiment in accordance with the present invention of a rotary ram pump having an axially movable
  • casing 291 having inlet passages 292,293 for admission of fluid 294, and two exit
  • passages 295, 296 in axially stacked relation, and separated by an intermediate ring-shaped
  • each exit passage having a separate exit port 298,299; an axially
  • the rotor assembly includes a first disk 303, a second disk 304, and a plurality of vanes arranged circumferentially in two axially stacked levels 305,306 within the annular space defined in-between the relatively inner surfaces of the disks.
  • An intervening disk 307 is disposed between first and second disks 303,304 which are secured for rotation with the axially movable drive shaft 300.
  • Each of the two disks has a relatively inner surface
  • circumferentially arranged vanes has a first edge, and a second edge, each attached to its
  • the exit passages 296 are formed of two parallel tubular chambers, which join
  • the pressurized fluid may be discharged either completely through the first exit passage 295 as shown in Fig. 22, or completely through the second exit passages 296 as shown in Fig. 24.
  • the former mode, illustrated in Fig. 22 provides a forward thrust to the propelled vehicle, with the fluid being admitted through the relatively anterior group of inlet passages 293 due to the
  • the later mode illustrated in Fig 24, provides a
  • the axial movement of the axially movable shaft 300 can be provided by
  • Figs. 25 - 29 are schematic representations of alternative ways in which the diverging channels confined between the opposing parts of the surfaces of each two adjacent vanes of a rotary ram fluid pressurizing machine in accord with the present invention, may be designed.
  • each of the channels are formed of the opposing parts of the surfaces of the two adjacent vanes confining the channel between them (right front and left rear surfaces of the drawings), and of the opposing parts of
  • Fig. 27 the divergence of the channel is provided by designing the boundaries confining the channel between them so that both the axial width 320 of the channel and the width 321 between the opposing parts of the surfaces of the two adjacent vanes confining the channel between them increase gradually from the inlet 322 of the channel towards its outlet 323, with the gradual increase in the axial width of the channel
  • vanes 324 so that it is gradually sloping from the inlet of the channel towards its outlet
  • vanes 329,330 so that they are gradually sloping from the inlet of the channel towards its
  • the divergence of the channel is provided by designing the boundaries confining the channel between them so that the width 331 between the opposing parts of the surfaces of the two adjacent vanes confining the channel between them increases gradually from the inlet 332 of the channel towards its outlet 333, with the gradual increase in the width between the opposing parts of the surfaces of the two adjacent vanes provided by designing the vanes with suitable angles of inclination at their different
  • Fig. 30 is a sectional view in a schematic representation of another embodiment of
  • inlet passage 352 for admission of compressible fluid 353 e.g., gas, or vapor, or a mixture
  • compressible fluid 353 e.g., gas, or vapor, or a mixture
  • the rotor assembly includes a disk 358. and a plurality of vanes 359
  • Each of the circumferentially arranged vanes has a first
  • edge 362 attached to the inner surface of the disk, a second free edge 363, a relatively
  • Fig. 31 is a sectional view in a schematic representation of an exemplary
  • the rotor assembly includes a disk 359, and a plurality of vanes arranged
  • annular spaces defined in-between one of the surfaces of the disk and its opposing inner
  • the disk is secured for rotation about the
  • Each of the vanes of each level has a first edge 382, 383 attached to their
  • a second free edge 384,385 a relatively radially outwards leading edge or tip, and a relatively radially inward trailing edge or tail (not shown in the drawing), with the design and operation of the circumferentially arranged vanes being quite similar to those of the embodiment of Figs. 7, 8.
  • the clearance space between the free edges of the vanes and the casing is kept at a minimum to decrease the flow of pressurized gases round the free edges of the vanes, and thus minimize the associated decrease in the overall machine efficiency.
  • Fig. 32 is a sectional view in a schematic representation of an exemplary
  • main components of the rotary ram pump in this embodiment are a stationary casing 391
  • the rotor assembly includes a disk
  • the disk is secured for rotation about the drive shaft.
  • circumferentially arranged vanes has a first edge 401 attached to the inner surface of the
  • Fig. 33 is a sectional view in a schematic representation of an exemplary embodiment of another rotary ram compressor, in accordance with the present invention.
  • the main components of the rotary ram compressor in this embodiment are a stationary
  • casing 411 having an inlet passage 412 for admission of compressible fluid 413, and an
  • the rotor assembly includes a disk 418, and a plurality of vanes
  • Each of the vanes has a first edge 421, 422
  • Fig. 34 illustrates one of the practical ranges within which the angles of inclination of the vanes of the rotor of a rotary ram fluid pressurizing machine may be designed, according to the present invention and illustrates the meaning of the term angle of inclination as used herein.
  • the vane is preferably smoothly curved from its leading edge I, towards its trailing edge t,.
  • the angle of inclination of the successive portions of the vane are measured with respect to a plane x-i-x, comprising the midpoint of the vane m, and perpendicular to a radial plane c,-m, including the rotational axis c, of the rotor and the
  • leading edge of the vane 1 is + 15 degrees, and is gradually decreasing towards the
  • range of angles of inclination in this embodiment is from + 15 to - 43 degrees.
  • Fig. 35 illustrates another practical range within which the angles of inclination of
  • vanes of the rotor of another rotary ram fluid pressurizing machine may be designed, according to the present invention.
  • the vane is preferably smoothly curved from its leading edge 1 2 towards its
  • leading edge of the vane L 2 is + 44 degrees, and is gradually decreasing towards the
  • range of angles of inclination in this embodiment is from + 44 to - 16 degrees.
  • each inlet and outlet of each of the diverging channels formed by two adjacent vanes together with the related surfaces of two adjoining disks or of a disk and the casing are radially opposed to each other.
  • each inlet is disposed at a smaller radial distance from the drive shaft than its corresponding
  • each outlet is disposed at a smaller radial distance from the drive shaft than the corresponding inlet as appropriate when the rotary ram fluid pressurizing machine is
  • fluid pressuring machine may comprise disks having vanes disposed to produce both radially inward displacement of fluid and radially outward displacement of fluid to

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne des machines de compression centrifuge et dynamique d'un fluide faisant appel au phénomène de l'augmentation de la pression dynamique qui apparaît lorsqu'un fluide est déplacé dans un diffuseur adapté se déplaçant à une vitesse élevée pour développer un gradient de pression entre deux points traversés par un courant de fluide. Dans une machine, des aubes (30) fixées à des disques rotatifs (28, 29) forment des passages (39) qui agissent comme diffuseurs lorsque les disques tournent pour déplacer et mettre sous pression un fluide rapidement vers l'intérieur et radialement vers l'extérieur. L'invention concerne aussi différents modes d'exécution de compression, de pompage ou d'évacuation de fluides compressibles ou incompressibles.
PCT/US2000/017044 1999-07-06 2000-06-20 Machine de compression centrifuge et dynamique d'un fluide Ceased WO2001002701A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU54984/00A AU5498400A (en) 1999-07-06 2000-06-20 Rotary ram fluid pressurizing machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US34821999A 1999-07-06 1999-07-06
US09/348,219 1999-07-06

Publications (1)

Publication Number Publication Date
WO2001002701A1 true WO2001002701A1 (fr) 2001-01-11

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PCT/US2000/017044 Ceased WO2001002701A1 (fr) 1999-07-06 2000-06-20 Machine de compression centrifuge et dynamique d'un fluide

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Country Link
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WO (1) WO2001002701A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6877951B1 (en) 2003-09-23 2005-04-12 Essam T. Awdalla Rotary ram-in compressor
US6938404B2 (en) 2003-09-23 2005-09-06 Rrc-Sgte Technologies, Llc Supercharged open cycle gas turbine engine
US7195451B1 (en) 2003-09-23 2007-03-27 Awdalla Essam T Radial out-flowing rotary ram-in compressor
US7390162B2 (en) 2005-03-01 2008-06-24 Awdalla Essam T Rotary ram compressor
WO2009135027A3 (fr) * 2008-04-30 2010-01-21 Kim Yong W Dispositif médical pneumatique manuel peu bruyant
US11441621B2 (en) 2019-01-31 2022-09-13 Horton, Inc. Pump and wiper assembly, associated viscous clutch and associated method

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US5427503A (en) * 1991-03-15 1995-06-27 Toto Ltd. Multi-stacked circular plate fan provided with blades

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US45755A (en) * 1865-01-03 Improvement in water-wheels
US2138814A (en) * 1937-03-15 1938-12-06 Kol Master Corp Blower fan impeller
US2324011A (en) * 1940-09-19 1943-07-13 Hydraulic Brake Co Blade wheel
GB625535A (en) * 1943-09-20 1949-06-29 Thomas Chester Impeller for centrifugal apparatus
US3536416A (en) * 1968-05-14 1970-10-27 Dov Z Glucksman Squirrel-cage rotor for fluid moving devices
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US4195965A (en) * 1977-03-18 1980-04-01 Walter Masnik Ram pump flowmeter
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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6877951B1 (en) 2003-09-23 2005-04-12 Essam T. Awdalla Rotary ram-in compressor
US6938404B2 (en) 2003-09-23 2005-09-06 Rrc-Sgte Technologies, Llc Supercharged open cycle gas turbine engine
US7195451B1 (en) 2003-09-23 2007-03-27 Awdalla Essam T Radial out-flowing rotary ram-in compressor
US7390162B2 (en) 2005-03-01 2008-06-24 Awdalla Essam T Rotary ram compressor
WO2009135027A3 (fr) * 2008-04-30 2010-01-21 Kim Yong W Dispositif médical pneumatique manuel peu bruyant
US11441621B2 (en) 2019-01-31 2022-09-13 Horton, Inc. Pump and wiper assembly, associated viscous clutch and associated method

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