US3283084A - Fluid supported apparatus - Google Patents

Description

1966 A. L. WITCHEY 3, ,0

FLUID SUPPORTED APPARATUS Filed May 17, 1962 5 Sheets-Sheet 1 INV EN TOR. 415.577 Z. W/rmzr Arraxwzr A. L. WITCHEY FLUID SUPPORTED APPARATUS Nov. 1, 1966 5 Sheets-Sheet 2 Filed May 17, 1962 INV EN TOR. Azazn- Z. l V/rawir BY Arr-mews) United States Patent FLUID SUPPORTED APPARATUS Albert L. Witchey, Erlton, N .J., assignor to Radio Corporation of America, a corporation of Delaware Filed May 17, 1962, Ser. No. 195,464 9 Claims. (Cl. 179100.2)

This invention relates to fluid supported apparatus, and particularly to fluid driven and fluid supported apparatus, such as devices including turbines and fluid bearings.

The invention is especially suitable for use in recording apparatus, such as a magnetic drum recording device, and involves mechanism for enabling a recording surface to be rotated at very high speeds. When the terms recording apparatus or recording surface are used herein, it should be understeod that reproducing, as well as recording, may be accomplished by such apparatus or on such surface.

Turbines have been proposed wherein a shaft is driven by means of stream of air. It has also been proposed to support a turbine driven shaft by air bearings. The pneumatic power requirements (the volume of pressurized air used per minute) of known air bearing supported turbines may be excessive, especially when high speeds of the order of 10,000 r.p.m. are desired. Moreover, designs for air bearing supported turbine systems have, as a rule, been complex in that they involve a multiplicity of ducts and orifices which are in precise alignment with each other.

It is an object of the present invention to provide improved fluid supported and driven apparatus wherein the foregoing disadvantages of known air bearing supported turbines are substantially eliminated.

It is a still further object of the present invention to provide improved fluid supported and driven apparatus which is highly eflicient in operation, particularly insofar as the pneumatic power required is concerned.

It is a still further object of the present invention to provide an improved pneumatic turbine which is supported on penumatic bearings and which has a pneumatic power consumption of the same order of magnitude as the electric power, consumption of an electric motor which would be required in lieu of the turbine to provide equivalent results.

It is a still further object of the present invention to provide improved recording apparatus and particularly an improved magnetic drum device.

It is a still further object of the present invention to provide magnetic recording apparatus capable of direct magnetic recording of high frequency signals of the order of 50 megacycles per second.

Briefly, fluid supported and driven apparatus embodying the invention is arranged so that the same set of pressurized fluid supply jets which supplies turbine power also establishes a fluid bearing for supporting the turbine.

Apparatus embodying the invention may, for example, comprise a stator and a rotor having opposed, complementary, arcuate surfaces. The stator and rotor may respectively have pressurized fluid supply jets and buckets in their opposed, complementary, arcuate surfaces. Pressurized air emanating from the stator jets both drives the rotor and establishes an air bearing between the opposed, arcuate rotor and stator surfaces for supporting the rotor.

The invention itself, both as to its organization and method of operation, as well as additional objects and advantages thereof, will become more readily apparent from a reading of the following description in connection with the accompanying drawings, in which:

FIG. 1 is a perspective view, partially broken away, showing a magnetic drum device embodying the invention;

FIG. 2 is a vertical sectional view taken along the line 22 in FIG. 1, and viewed in the direction of the apice pended arrows showing in detail the magnetic drum device;

FIG. 3 is a sectional view taken along the line 33 in FIG. 2 and viewed in the direction of the appended arrows;

FIG. 4 is a sectional view taken along the line 44 in FIG. 2 and viewed in the direction of the appended arrows; and

FIG. 5 is a fragmentary, perspective view showing a portion of the rotor of the magnetic drum device shown in the foregoing figures.

Referring more particularly to FIG. 1, there is shown a magnetic drum recording device which is an illustrative embodiment of fluid supported and fluid driven apparatus according to the invention. The fluid 'which is used in the device illustrated in FIG. 1 is air. Other fluids, such as gases other than air, or liquids, preferably of low 'viscosity, may be used alternatively. However, use of air is preferred because it is readily available and may be pressurized with compressors of the type which are generally available.

The magnetic drum device includes a rotor 10 in the form of a ring having a cylindrical outer peripheral surface coated with magnetizable material 12, which may be a magnetic oxide. This ring provides a magnetic drum record. The rotor 10 is located around a stator like assembly 14, referred to for convenience as a stator. This stator is mounted in a journal on a panel 16. The stator may be free to rotate on its axis, or it may be rotated on its axis by an electric motor 18 which is secured to the panel. A pulley 20 on the shaft of the motor 18 is belt coupled to another pulley which is connected to the stator. Alternatively, the stator 14 may be held stationary.

A magnetic head 22 is supported by an L-shaped bracket 24. Feet 26 of the bracket 24 are attached to the stator 14 so that the head 22 may either be stationary or rotate with the stator, as desired. The head 22 may desirably be a multi-channel head having a plurality of side-by-side head units which scan adjacent record tracks on the magnetizable coating 12 on the rotor 10. A slip ring assembly (not shown) may be mounted on the stator 14 coaxially therewith. The output leads from the head 22 may be connected to the slip rings of the-assembly. A brush assembly (not shown) mounted on the panel 16, for example, by means of a bracket may cooperate with the slip ring assembly for deriving output signals from the head 22 when the head rotates with the stator 14.

The internal periphery of the rotor 10 is arcuate in shape. More particularly the inner periphery of the rotor 10 is inwardly convex, as viewed in a cross-section taken in an axial plane (see FIG. 2) the rotor being generally toroidal in shape. This inwardly convex, arcuate surface is opposed to a complementary, outwardly concave, arcuate surface (when viewed in like-section) in the stator. The rotor 10 and stator 14 are disposed in nested relationship. In other words, the rotor is seated in the stator. A small clearance of the order of 0.001 inch may be provided between the opposed rotor and stator surfaces.

An array of air propulsion jets (shown at 108 in FIGS. 2 and 3) extends inwardly into the stator from its internally concave, arcuate surface. The inwardly convex surface of the rotor has an array of bucket scoop notches 34 therein (see FIG. 5). Thus, when compressed air is exhausted into the space between the opposed arcuate surfaces of the rotor 10 and stator 14, the rotor is propelled in one direction by the streams of air impinging on the bucket scoops. The stator tends to rotate in the opposite direction from the rotor because of jet reaction forces. The air from the jets also flows between the opposed surfaces of the stator and rotor and fills the clearance therebetween. The rotor therefore floats on a film of air (a hydrostatic air bearing), as it is propelled by the air from the propulsion jets in the stator. Extremely highspeeds of rotation are possible with this magnetic drumdevice. These speeds may exceed 10,000 rpm. when the device is operated in air. Even higherspeeds are possible when the device is operated in a vacuum chamber.

The etficiency of the device is extremely high, since the frictional forces are substantially eliminated due to the air bearing provided by the film of 'air established between the rotor and stator. The drag due to viscous shear losses is also reduced, especially when the stator and rotor rotate, since the relative velocity of the air and the moving stator and rotor surfaces is small. Pneumatic power required in terms of the volume of air and pressure of air required (the dimensions of pneumatic power may be cubic feet, pounds per square inch-seconds) is also reduced because the bucket scoops are arranged opposite to the propulsion jets to utilize the maximum thrust of the air as it emanates from the jets. Since the jets and scoops are directly opposite each other, the velocity of the air is not appreciably diminished before the air impinges upon the scoops. The pneumatic power requirements of the device are also low because the complementary, opposed, arcuate surface of the rotor and stator confine and direct the air as it leaves the propulsion jets. The air therefore cannot disperse appreciably as, for example, would ''be the case if flat or cylindrical stator and rotor surfaces were opposed to each other.

It has been found that a magnetic drum device of the type described herein, when operated at speeds of the order 'of 10,000 rpm. consumes no more pneumatic power than the equivalent amount of electric power which would be consumed by an electric motor for driving such a drum.

The details of construction of a magnetic drum device such as shown in FIG. 1 are illustrated in FIGS. 2 to -5. The rotor 10 is a ring made, for example, of aluminum. The outer periphery 28 of the rotor is cylindrical. The inner periphery 30 of the rotor 10 is as arcuate in shape and semicircular in cross section as viewed in FIG. 2. The side walls 32 of the rotor which extend between the outer periphery 28 and the inner periphery 30 thereof are in parallel planes. The cylindrical bucket scoop notches 34 are milled into the inner periphery 30 of the rotor. The notches 34 lie approximately in a plane perpendicular to the axis of the rotor which plane bisects the rotor (see FIG.

The stator 14 is a two part assembly. The parts of the stator are essentially an outer cylinder 36 and an inner cylinder 38 joined along mating surfaces 37 and 39. The outeredges of the mating surfaces 37 and 39 of the stator parts 36 and 38, respectively have circular, quadrantal cut away portions 41 and 43 milled therein. These portions '41- and 43 form the inwardly concave surface of semicircular cross section in an axial plane (see FIG. 2) in the outer periphery of the stator 14' when the stator parts 36 and 38 are joined in mating relationship with each other. 'This peripheral inwardly concave, arcuate surface 41, 43, provides the seat for the inwardly couvex, inner periphery 30 of the rotor 10. The transverse diameter of this peripheral surface 41, 43 is slightly larger "than the transverse diameter of the convex, inner peripheral surface of the rotor 10. Accordingly, a slight clearance 45(e.g., 0.001 inch) is provided between the stator and the rotor 14. The propulsion jets and duct work for directing air to the propulsion jets are formed at the mating surfaces 37 and 39 of the stator parts 36 and 38, and are described hereinafter. The parts 36 and 38 are held together by a multiplicity of screws 40 which extend through tapped, aligned holes in both parts 36 and 38.

The outer stator part 36 has a central hole 42 which surrounds a central hub 44 of the inner stator part 38. This hub has a central hole 46 into which the end of a flanged shaft 48 extends. A flange 50 on the shaft 48 has a multiplicity of tapped holes therein which are in alignment with tapped holes in the hub 44. Screws 52 in these aligned, tapped holes join the shaft 48 to the stator assembly 14.

The shaft 48 extends through the panel16 and is journaled in ball bearings 54 and 56. The outer races of these ball bearings are mounted in a flanged collar 58.

This collar 58 extends through the panel 16. A flange 60 on the end of the collar has a plurality of tapped holes therein which are aligned with tapped holes in the panel 16. Screws 62 in these tapped, aligned holes fasten the flange 60 to the panel 16.

A pulley 64 is attached to the shaft 48 by means of a set screw 66. A belt 68 (shown in phantom) may be trained around the pulley 64, when it is desired to drive the stator by meansof a motor, as shown in FIG. 1.

A cylindrical shell 70, attached at one end to the panel 16 by means of screws 72,? surrounds the collar 58 and the pulley 68. r The free end of the shell 70 is closed by an apertured disc 74 which is attache-d to the free'end of the shell 70 by means of screws 76. A set screw 88 which is screwed into a tapped hole in the shell70 can be adjusted to engage a cooperating notch 92 in the pulley 64 for holding the shaft 48 and the stator stationary.

A flanged, cylindrical bearing member 78, which may be made of bronze Oilite bearing material, closes the aperture in the disc 74. The bearing member 78 is also apertured and has a conical, tapped hole 80 into which a compressed air fitting 82 is seated. This fittin-g82 is adapted to receive the end of a hose from an air compressor.

The shaft 48 is formed with a blind, axial bore 84. i The openend of this bore is counterbored and receives the cylindrical periphery 86 of the Oilite bearing member 78. The periphery 86 therefore provides another bearing for supporting the shaft 48.

The formation and construction of the duct work which provides the propulsion jets are best shown in FIGS. 3 and 4. Two passages 94 and 96 are drilled through the hub 44 of the inner cylindrical part 38 of the stator and through the shaft 48 into the blind, axial bore 84, each at a suitable angle to the axis of the shaft48 in substantially a common plane and disposed in mirror image relation with respect to the axis. Circular notches 98 and 100 are cut in the outer stator part 36 and in the inner stator part 38, respectively. These notches jointly form a circular groove 102 which communicates with the open, outer ends of the holes 94 and 96. A plurality of radial grooves 104 are cut in the surface 39 of'the stator part 38 which mates with the surface 37 of the other stator part 36. These radial grooves 104 communicate the circular groove 102 with another, gnarrow,

circular groove 106 cut into the surface 39 of the stator part 38. A large number of grooves, 108 are cut in the surface 39 of the stator part '38 at similar angles to radial lines from the axis. These grooves form the propulsion jets. It should, be noted that the grooves 108 are so disposed that each. of them communicates with the pe- 'ripheral groove which forms the seat in the stator 14 of the rotor 10 at the center of that seat. Accordingly, the propulsion jets are directly opposite to, and in alignment with, the, semicircular notches 34 which provide the bucket scoops on the inner periphery 30 of the rotor 10. The propulsion jet grooves 108 are all cut at the same angle (for example, 31.3) with respect to lines tangent to the outer periphery of the stator part 38 at the entrances of these grooves into the stator part 38. The angle is selected to achieve the maximum tangential component of air thrust upon the scoop notches 34 without greatly enlarging the orifices formed by the propulsion jet grooves 108 in the peripheral, concave stator groove.

In operation, pressurized air flows through the fitting 82 into the blind bore 84 in the shaft 48. The pressure of this air, when a rotor having an outer diameter of approximately 8 inches, for example, is to be driven at about 10,000 rpm. may be 60 p.s.i.

The air flows through the passages 94 and 96 into the circular grove 102. The velocity of the air increases as it flows into the radial grooves 104 which are of smaller transverse diameter than the circular groove 102 and therefore the radial grooves 104 act as nozzles. The velocity of the air further increases as the air flows through the propulsion jet grooves 108. The air emanates from these grooves 108 at extremely high velocity. For example, in the case of the air pressure and rotor size referred to above, the velocity of the air escaping from each of the propulsion jets may be 1000 feet per second. This extremely high velocity air impinges upon the semicircular notches 34. These notches catch the air and convert the force of the air into rotary motion of the rotor 10. After impinging upon the scoop notches 34, the air is directed into the clearance 45 between the rotor and the stator because of the arcuate shape of this clearance and because the propulsion jets emanate in the center of the clearance 45.

The escaping, pressurized air establishes a hydrostatic air bearing in the clearance 45. This bearing provides both axial and radial support for the rotor 10. In other words, the escaping air provides a film of air in the clearance 45 between the rotor and stator 14 as this air drives the rotor 10. Extremely high speeds of rotation of the rotor are possible since (1) there is substantially no friction between the stator and the rotor because of the air bearing therebetween, and (2) the viscous drag between the rotor and the stator is small because the relative velocity between the moving air and the rotating rotor is very low. The pneumatic power required by the device is small and the over-all efficiency of the device is high and comparable to the efiiciency of magnetic drums which are driven by electric motors.

Three modes of operation of the device are possible as follows:

(1) The set screw 88 is connected to the pulley 64 and holds the stator 14 stationary so that the rotor 10 alone rotates.

(2) The set screw 88 is withdrawn and the stator 14 is allowed to rotate under the influence of reaction forces developed by the escaping air from the propulsion jets.

(3) The belt 68 is coupled to a motor 18 (as shown in FIG. 1) and the stator 14 is directly driven while the rotor is air driven in the same direction as the stator 14.

In the second mode of operation noted above, the relative speed of the stator with respect to the rotor is greater than when the stator is held stationary with the set screw 88. The relative stator to rotor speed may, for example, be 14,000 r.p.m. when the stator is allowed to rotate.

The efficiency of operation also increases, since losses due to viscous shear effects are reduced. It is believed that, when the apparatus is operating in a gaseous environment of finite pressure (air under atmospheric pressure), viscous shear losses depend directly upon the absolute speed of the rotor 10 through the atmosphere. The absolute speed of the rotor, when the stator 14 is allowed to rotate under the influence of reaction forces developed by air escaping from the propulsion jet grooves 108 (FIG., 3), is less than when the stator 14 is held stationary. Thus, the viscous shear losses are reduced while the relative rotor to stator speed is increased in the second mode of operation.

When the motor 18 (FIG. 1) drives the stator 14 in the same direction as the rotor 10, as in mode (3) noted above, the absolute rotor speed is greater than when the rotor is held stationary because the kinetic energy of stator rotation is added to the energy of the air escaping from the propulsion jet grooves 108 (FIG. 3). Efficiency of operation is somewhat less than in mode 1), since viscous shear losses rise with absolute rotor speed. If the pressure of the atmosphere surrounding the apparatus is reduced, as, for example, when the apparatus is operated in a vacuum, the efficiency would remain high and rotor speed would be further increased. In the absence 6 of appreciable viscous shear and other viscous drag effects, the speed of rotation of the rotor is limited, as a practical matter, only by the capacity of the compressed air supply and the strength of the materials from which the rotor is constructed.

When the device is used for magnetic recording, extremely high frequencies may 'be recorded on the magnetizable coating 12, since the relative head to record speed is very high. As is well known in the magnetic recording art, the recorded signal wavelengths depend upon the head-to-record speed as well as the frequency of the signals applied to head. Since the record rotates at very high speed, the recorded wavelengths may be much larger than the wavelengths of the signals applied to the head. Since the minimum length of the wavelengths which can be recorded on a magnetic record is limited by the characteristics of that magnetic record, the above described magnetic recording device makes possible the recording of very high frequency signals (for example, 50 megacycles per second with known ma-gnetizable materials).

From the foregoing description, it will be apparent that there has been provided improved fluid supported and fluid driven apparatus which is especially suitable for use in magnetic recording devices and whereby high frequency signals may be recorded. Uses of the invention other than in magnetic recording, as well as variations in construction and operation of apparatus described herein, all coming within the scope of the invention will undoubtedly present themselves to those skilled in the art. Accordingly, the foregoing description should be taken merely as illustrative and not in any limiting sense.

What is claimed is:

1. Fluid supported apparatus comprising (a) a rotor and a stator exhibiting complementary, opposed, arcuate surfaces having termination points and disposed in nested relationship with each other,

(b) said stator having a plurality of propulsion jets therein emanating from its said arcuate surface,

(c) said rotor having a plurality of bucket scoops therein extending into its said arcuate surface and disposed opposite to said jets, and

(d) means for applying pressurized fluid through said jets to impinge against said bucket scoops for propelling said rotor with said fluid,

said pressurized fluid being exhausted from between said rotor and said stator arcuate surfaces at said termination points subsequent to the impingement against said bucket scoops so as to establish a fluid bearing between said rotor and said stator.

2. A fluid supported turbine comprising (a) a first member,

(b) a second member about which said first member is rotatable, said first and second members respectively having opposed surfaces of revolution, having termination points being disposed substantially opposite each other r (c) said first member surface having a plurality of propulsion jets therein,

((1) said second member surface having a plurality of bucket scoops disposed in alignment with said jets, and

(e) means for applying pressurized fluid through said jets to impinge against said bucket scoops for propelling said first member with said fluid,

said pressurized fluid exhausted from between the surfaces of revolution of said first and second members at said termination points subsequent to the impingement against said bucket scoops so as to establish a fluid bearing between said first and second members,

3. Fluid supported apparatus comprising (a) a rotor and a stator having complementary, op-

posed, arcuate surfaces,

(b) said stator having a plurality of propulsion jets therein emanating from its said arcuate surface,

(c) said rotor having a plurality of bucket scoops therein extending into its said arcuate surface and disposed opposite to said jets,

(d) means for rotatably mounting said stator, and

(e) means for applying pressurized fluid through said jets and onto said bucket scoops for developing action and reaction forces for rotating said rotor and stator in opposite directions while simultaneously establishing a hydrostatic fluid bearing between said surfaces.

4. A fluid supported turbine comprising (a) a rotor and a stator,

(b) means for rotata-bly mounting said stator,

(c) said rotor and said stator having complementary,

opposed, arcuate surfaces disposed in nested relationship to provide a bearing clearance therebetween,

(d) said stator having a plurality of propulsion jets therein emanating from its said arcuate surface,

(e) said rotor having a plurality of bucket scoops therein' extending into its said arcuate surface and disposed opposite to said jets,

(f) means for supplying pressurized fluid through said jets for floating said rotor on a film of fluid formed in said bearing clearance and simultaneously impinging said fluid on said bucket scoops to rotate said rotor, and

(g) drive means for rotating said stator in the same direction of rotation as said rotor.

5. Recording apparatus comprising (a) a rotor and a stat-or having complementary, opposed, arcuate surfaces which define a toroidal passage between said opposed surfaces,

(b) said stator having a plurality of propulsion jets therein extending from the center of its said arcuate surface,

(c) said rotor having a plurality of bucket scoops therein extending from the center of its said arcuate surface and disposed opposite to said jets,

(d) a recording surface on one of said stator and rotor,

(e) a transducer mounted on the other of said stator and rotor and disposed in scanning relationship with said recording surface, and

(f) means for supplying pressurized fluid through said jets and onto said scoops for simultaneously establishing a combined axial and radial fluid bearing between said opposed surfaces and propelling said rotor with said fluid.

6. Recording apparatus comprising (a) a cylindrical ring rotor,

(b) a cylindrical stator,

(c) said rotor and stator having complementary, opposed, arcuate surfaces disposed in nested relationship and defining a clearance therebetween of arcuate cross-sectional shape,

(d) said stator having a plurality of propulsion jets therein extending from the center of its said arcuate surface,

(e) said rotor having a plurality of bucket scoops therein extending therein from its said. arcuate surface and disposed opposite to said jets,

(f) a recording surface on the surface of said rotor opposite to its said arcuate surface,

(g) a transducer mounted on said stator and disposed in scanning relationship with said recording surface, and

(h) means for supplying pressurized fluid through said jets for simultaneously establishing a fluid bearing in said clearance and propelling said rotor by impingement-of said fluid against said scoops.

7. Apparatus for utilizing pressurized air comprising (a) a cylindrical ring having an inner periphery semicircular in cross-section,

(b) a cylinder having a notch around the outer periphery thereof, said notch being semicircular 'in crosssection and having a radius larger than said semicircular ring inner periphery,

(c) said ring being disposed around said cylinder with said ring inner periphery nested in said notch, said inner and outer peripheries ending at termination points disposed substantially opposite each other (d) said cylinder having a plurality of spaced orifices therein extending from the surface of said notch, said orifices respectively being oriented at a predetermined acute angle With respect, to lines tangent to said cylinder at the entrance thereof into said cylinder, 7 (e) said ring having a plurality of notches therein spaced from each other along said inner periphery thereof, and (f) means for applying pressurized air through said orifices to impinge against said ring notches for driving said ring,

said pressurized air being exhausted from between said ring and said cylinder. at said peripheral termination points subsequent to the impingement against said ring notches so as to establish an air bearing between said ring and said cylinder. 8. Magnetic recording apparatus for cooperation with a magnetic head and. for utilizing pressurized air comprising (a) a cylindrical ring having an inner periphery semicircular in cross-section,

(b) a cylinder having a notch around the outer periphery thereof, said notch being semicircular in crosssection and having a radius larger than said semicircular ring inner periphery,

(c) the outer, peripheral surface of said ring being cylindrical,

(d) a magnetizable coating on said ring outer peripheral surface defining a magnetic record,

(e) said ring being disposed around said cylinder with said ring inner periphery nested in said notch, means for mounting said ring and said cylinder adjacent said magnetic headso that said magnetizable coating cooperates with said magnetic head,

(f) said cylinder having a plurality of spaced orifices extending therein from the surface of said notch, said orifices respectively being oriented at a pre determined acute angle with respect to lines tangent to said cylinder at the entrance thereof into said cylinder,

(g) said ring having a plurality of scoop notches therein spaced from each other along said inner peripher thereof, and

(h) means for applying said pressurized air through said orifices and onto said scoop notches for simultaneously driving said ring and establishing an air bearing for supporting said ring.

9. Apparatus for utilizing pressurized air comprising (a) a cylindrical ring having an inner periphery semicircular in cross-section,

(b) a cylinder having a notch around the outer periphery thereof, said notch being semicircular in crosssection and having a radius. larger than said semicircular ring inner periphery,

(c) said ring being disposed around said cylinder with said ring inner periphery nested in said notch,

(d) said cylinder having a plurality of spaced orifices therein extending from the surface of said notch, said orifices respectively being oriented at predetermined acute angles with respect to lines tangent to said cylinder at the entrace thereof into said cylinder,

(e) a shaft connected to said cylinder,

(f) bearing means rotatably supporting said shaft,

( g) said shaft having an axial bore therein,

(h) said cylinder having passages therethrough c0m-,

municating said orifices with said shaft bore,

References Cited by the Examiner UNITED STATES PATENTS 2,602,632 7/1952 Serduke et a1.

Mathiesen.

Baumeister.

Riddler et a1. 179100 Quade 340174.1 Uritis 179-1002 Quade et a1 340174.1 Levene 340174.1

10 BERNARD KONICK, Primary Examiner.

IRVING SRAGOW, Examiner. H. D. VOLK, G. LIEBERSTEIN, Assistant Examiners.

Claims (1)

1. 9. APPARATUS FOR UTILIZING PRESSURE AIR COMPRISING (A) A CYLINDRICAL RING HAVING AN INNER PERIPHERY SEMICIRCULAR IN CROSS-SECTION, (B) A CYLINDER HAVING A NOTCH AROUND THE OUTER PERIPHERY THEREOF, SAID NOTCH BEING SEMICIRCULAR IN CROSSSECTION AND HAVING A RADIUS LARGER THAN SAID SEMICIRCULAR RING INNER PERIPHERY, (C) SAID RING BEING DISPOSED AROUND SAID CYLINDER WITH SAID RING INNER PERIPHERY NESTED IN SAID NOTCH, (D) SAID CYLINDER HAVING A PLURALITY OF SPACED ORIFICES THEREIN EXTENDING FROM THE SURFACE OF SAID NOTCH, SAID ORIFICES RESPECTIVELY BEING ORIENTED AT PREDETERMINED ACUTE ANGLES WITH RESPECT TO LINES TANGENT TO SAID CYLINDER AT THE ENTRANCE THEREOF INTO SAID CYLINDER, (E) A SHAFT CONNECTED TO SAID CYLINDER, (F) BEARING MEANS ROTATABLY SUPPORTING SAID SHAFT, (G) SAID SHAFT HAVING AN AXIAL BORE THEREIN, (H) SAID CYLINDER HAVING PASSAGES THERETHROUGH COMMUNICATING SAID ORIFICES WITH SAID SHAFT BORE, (I) SAID RING HAVING A PLURALITY OF SCOOP NOTCHES THEREIN SPACED FROM EACH OTHER ALONG SAID INNER PERIPHERY THEREOF, AND (J) MEANS FOR FLOWING SAID PRESSURIZED AIR THROUGH L SAID SHAFT BORE, SAID PASSAGES AND SAID ORIFICES AND ONTO SAID SCOOP NOTCHES FOR SIMULTANEOUSLY DRIVING SAID RING AND ESTABLISHING AN AIR BEARING FOR SUPPORTIN SAID RING.

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