US2865599A - Rotating machine such as a centrifugal opposed pressure turbine - Google Patents

Description

Dec. 23, 1958 BOYER 2,865,599:

ROTATING MACHINE SUCH AS A CENTRIFUGAL OPPOSED PRESSURE TURBINE s Sheets-Sheet 1 Filed March 14. 1955 INVENTOR. lgwaolv R da n Dec. 23, 1958 Y BQYER 2,865,599

ROTATING MACHINE SUCH AS A CENTRIFUGAL OPPOSED PRESSURE TURBINE Filed March 14. 1955 3 Sheets-Sheet 2 Dec. 23, 1958 L. R. QBOYER 2,865,599

ROTATING MACHINE SUCH AS A CENTRIFUGAL OPPOSED PRESSURE TURBINE INVENTOR..

United States Patent ROTATING MACHINE SUCH AS A CENTRIFUGAL OPPOSED PRESSURE TURBINE Lawson R. Boyer, Cleveland, Ohio Application March 14, 1955, Serial No. 493,959 4 Claims. (Cl. 253-161) This invention relates to improvements in rotating machines and more particularly to a centrifugal opposed pressure turbine.

One of the objects of the present invention is to provide a machine with two relatively movable members and with fluid streams urged to flow from both members into a common pocket carried by one member to cause relative movement between said members.

A further object of the present invention is to provide a fluid pressure operated turbine having a casing member with fluid flow streams directed against the periphery of a rotor member rotatably mounted therein and with said rotor member having outwardly directed through passageways therein leading to the periphery thereof.

A further object of the present invention is to provide a rotating machine having speed regulating means responsive to the centrifugal force exerted by rotation of the rotor member thereof.

A further object of the present invention is to provide annular, spinner-type, fiuid pick-ups at the inner end of generally radially extending passageways in a rotor mem ber so that fluid pressure may be exertedin said passageways by centrifugal force.

A further object of the present invention is to provide a centrifugal opposed presIure turbine and a starter for priming said turbine or bringing it up to operating speed.

A further object of the present invention is to provide a turbine characterized by its structural simplicity, its multiplicity of operating advantages, its economy of manufacture, and its operating efliciency.

Other features of this invention reside in the arrangement and design of the parts for carrying out their appropriate functions.

Other objects and advantages of this invention will be apparent from the accompanying drawings and descriptions and the essential features will be set forth in the appended claims.

In the drawings,

Fig. 1 is a front elevational view, partially in section, of the centrifugal opposed pressure turbine, the starter assembly, speed governor and fluid piping layout therefor;

Fig. 2 is a front elevational view of the turbine per se with portions thereof sectional to diflferent depth layers to disclose internal details;

Fig. 3 is a side elevational view, with the up er half in section of the turbine in Fig. 2 and the starter therefor; while Fig. 4 is a longitudinal sectional view of the governor valve in Fig. 1.

While the different aspects of the present invention might be adapted to various uses, I have chosen to show them combined to form a centrifugal opposed pressure turbine driven by any suitable fluid pressure and having a speed governor thereon.

A frame or casing member is provided for the turbine. It includes a housing lit in Fig. 2 comprised of upper and lower sections a, 10b respectively bolted or otherwise secured together and with these sections having rea 2,865,599 F t ted Dec. 23, 1958 spectively radially, outwardly extending enlargements 10c, 10d extending from the periphery thereof on opposite sides. Each enlargement is shown here as extending through an arc of about in Fig. 2 with one end being located about 30 from the vertical and. the other end about 10 from the horizontal. The underside of housing 10 has integrally formed therewith, Welded, or otherwise attached thereto diverging base legs 12, 12 secured at their lower ends to a base 14 adapted to rest upon or be secured to a floor or other suitable mounting foundation. End legs 15, 15 are bolted to the top of the lower housing section 1% and adapted to be secured at their lower ends to the foundation. A panel 16 in Fig. 3 is spaced away from and located generally parallel to one wall of housing 10 and detachably secured thereto at the top thereof by a connecting member 17 to aid in maintaining this spacing. An annular ring or track 19 in Fig. 2 forms the bore of housing 10 by being secured to section 10a, 10b by bolts 20. This annular track or liner 19 has integrally connected to gether a cylindrical, outer wall with inwardly extending, parallel flanges on opposite ends thereof, as shown in Fig. 3. This track 19 extends through substantially the full 360 within the housing 10.

A rotor member or engine 22 is rotatably mounted within the casing member to permit relative rotation with respect thereto. Rotor member or engine 22 is secured by a spline or any other suitable connection to output shaft 24 with this shaft rotatably mounted by hearing 25, 25 for rotation about the longitudinal central axis of shaft 24. During rotation, only a small clearance exists between the bore surface of annular track 19 in Fig. 3 and the peripheral surface of rotor member 22.

A suitable starter is provided if needed to bring the rotor member 22 up to operating speed, although some constructions Within the scope of this invention or operating conditions may permit rotor 22 to be brought up to operating speed Without a starter for priming. In Fig. 3, an electric motor type starter 27, securely fastened on housing enlargement lilo in the manner shown in Fig. 2, rotates its shaft 23, starter pinion 30 carried thereby, intermediate or transmitter gear 31 rotatably mcunted on panel 16, and pinion 32 secured to shaft 24 for rotating rotor 22 in the direction of arrow B in Fig. 2. Gear 31 is rotatably mounted on an axially movable shaft A by bearings at opposite ends in panel 16 and bracket 35 secured to said panel. An electrically actuated clutch 38 is adapted to move the gear 3laxially to engage or disengage gear 31 with pinions 3i and 32. Any suitable conventional type clutch means may be used in place of this construction, if desired.

If output shaft 24 of the turbine drives an electrical generator, electrical flow may be reversed in the generator to use it as a starting motor to prime or to bring the turbine rotor up to operating speed instead of using the illustrated construction. a

The electrical starting motor 27 may have adrive pulley 28:: secured to one end of its output shaft 28 in Fig. 3, if desired, for other uses, such as for operating an air compressor if the pressure fluid for operating this turbine takes the form'of air.

It should be apparent that this construction permits easy lubrication of gears 30, 31 and 32, as well as bear ings 25.

The main fluid piping layout is shown in Fig. l for operating the turbine with the pressure induced flow direction shown by the arrows. Conduit or lead 40 is connected to a source of fluid suitable type, such as air, steam, water, hot gases, etc. Conduit 40 has a branch conduit 41 in Fig. 1 leading to a pressure control valve 42 into port'10e in the lower housing section 10b shown here approximately 50 from pressure with this fluid beingof any v,turbine.

vcaused by rotation of rotor 22, to apply pressure to the the vertical central plane of the turbine. The remainder of the fluid through conduit .40 travels through pressure control valve 44, speed governor valve 45, and Y-conduit 47 to divide into two branches with the fluid in each traveling through a pressure control valve 49, conduit 59 and port 10 withports 10 here shown as located .45 from the vertical center line of the turbine casing in Fig. 1. An exhaust port 10g in upper housing section tea has secured thereto an exhaust valve 52 with an exhaust conduit 54 exhausting to Waste, either atmosphere, a fluid reservoir or through a condenser. Each of these valves 42, 44, 45, 49 and 52 may be individually adjusted to regulate individually the pressure drop and flow therethrough where and when necessary to give proper turbine operation.

Rotor 22 is constructed to permit fluid flow therethrough. Annular rings 22a, 22a in Figs. 2 and 3 are in.- tegrally formed with the remainder of rotor 22, are generally concentric with the axis of rotation of shaft 24, are here shown as located on both sides of rotor 22, and form spinner fluid traps adapted to capture fluid from housing 10 supplied thereto by conduits 40, 41 and port we in Fig. l as well as conduits 40, 47 and 5t), and port f through the clearances between the periphery of rotor 22 and the bore of annular track 19. Passageway means are provided in rotor 22 leading out to bucket-like recess means or pocket means on the periphery thereof. Although one or more of these may be, provided, the construction herein shown discloses twenty-four through fluid ducts or passageways 22b, evenly arcuately spaced around the rotor circumference at 14 intervals with each through passageway having its inner end located between rings 22a and extending generally radially outwardly with a bucket-like recess 22:: at the outer end of each passageway on the periphery of the rotor 22. These recesses 220 are arcuately spaced apart, here shown as a 1 are on the periphery of rotor 22 between adjacent bucket walls, with each bucket-like recess 22c capable of being formed by a substantial enlargement of its associated passageway 22!). Fig. 2 slightly distorts the true picture of rotor 22 by shifting the diametrically opposite bucket-like recesses 22c slightly out of alignment with respect to the diametrically opposite housing ports 10] so as to more clearly show the action of the fluid streams in operation of the This construction permits the centrifugal force,

fluid to urge it in the direction of the arrows in Figs. 1

and 2 to flow from between annular rings 22c, outwardly :through passageways 22b and into bucket-like recesses 22c so that this rotor construction provides port means,

here shown as a plurality of arcuately spaced ports for vdirecting fluid'streams under pressure through the rotor to the buckets to emerge from a plurality of ports formed .thereby spaced about the periphery of the rotor member.

These fluid streams will be forced outwardly by the cen- .trifugal force to create pressure, but of course the direction of flow of the fluid streams (whether the fluid moves outwardly, remains stationary or flows inwardly) will be dependent upon the pressure conditions existing on the.

periphery of rotor 22.

Port means are also provided in housing 10 for directing fluid angularly and non-radially inwardly in the direction of the arrows into the bore thereof against the periphery of rotor 22 to cause rotation of rotor 22 within housing 10. This port means may take the form of one or more :ports or stationary jet nozzles 10 10 here shown as two ,in number, fed from the fluid source through conduit 40,

as previously described, to form streams opposite each otherfor angular and non-radial fluid admission into,

housing 10. The nozzles could be of any shape to'get the desired fluid velocity and pressure for satisfactory operation. Only a portion of the bore (formed by the close fit of annular track 19 over the periphery of rotor 22) of housing 10, small in arcuate extent, 'is covered by Inozzles lt lj, 10 and this is substantially less than the arcuate extent 'of the casing bore therebe tween. The two fluid streams, emerging from ports 10 spaced about the periphery of rotor 22, are angularly and non-radially recelved in the bucket-like recesses 220 as the streams move in the inward direction opposed to the centrifugally caused outward pressure in passageways 22b and buckets 22c caused by the centrifugal force of rotation so as to cause continued rotation of rotor 22 in housing 10 in the direction of the arrow B in Fig. 2 after starter 27 has brought rotor 22 up to operating speed. The angularly opposing fluid columns or streams in nozzles 10f and in passageways 22b produce a resultant force having a substantial tangential force component effectively applied to the forward face 22d of each bucket 22c as a result of deflection of the angular and non-radial stream of pressurized fluid, thereby tending to cause rotation of rotor 22. When rotor 22 is operating at the proper speed, pressure action of the angularly opposing fluid forces are shown at the lower left in Fig. 2 with one of the buckets 22c entering the fluid stream of the casing jet from port 10 Another way of describing the operation might be to state that the centrifugally forced fluid in the passageways 22b, which are of small cross-sectional area, enters each of the corresponding buckets 22c, which diverge outwardly, thus having substantially greater cross-sectionalarea, thus causing the fluid to expand in each of the buckets 22c to fill the angularly diverging and radially non-symmetrical buckets 220, which has the effect of producing a tangential force component which is added to the tangential force component of the opposed fluid column or stream from the corresponding nozzles or ports 10], to create a resultant force wnich acts on the forward face 22d of the corresponding buckets 220, thus driving rotor 22.

It should be noted that the housing, or hollow casing it), is provided with an annular track 19, and that said annular track 19 together with the closely spaced adjacent portions of the rotor 22, and the side or end walls of the casing 10 together with the corresponding spaced ends of the rotor 22, define communication means effectively communicating each of the recesses 22c and the fluid return-inlet aperture means comprising the concentric spaced annular rings 22a; said communication means being adapted to pass deflected and excess pressurized fluid from the region adjacent the angular opposition of the exterior of each of said recesses 22c and each of said port means, or nozzles, 10 to said fluid return-inlet aperture means 22a. It should be noted that all of said deflected and excess fluid is not necessarily re-aspirated into 1 said fluid return-inlet aperture means 22a; some of said deflected and excess fluid being normally exhausted by way of'exhaust valve 52 and duct 54.

An example of what conditions may exist at nozzles 16f under one given flow condition is shown in Fig. 2. As mentioned before, the buckets 220 on diametrically opposite sides of rotor 22 have been displaced circumferentially out of their true diametrical position to show the jet action at two different positions of the rotor in Fig. 2. The pressures exerted by the opposing fluid streams within the bucket at each nozzle may be equal and angularly opposite to each other under some preferred running condition of the turbine. At the upper right-hand nozzle 10) in Fig. 2, it will be seen that the relation between the angle of the incoming jet from nozzle 10 to the greater volume part of bucket 22c, located in front of and immediately clockwise from nozzle 10f and rotating in the direction of arrow B into the incoming stream from nozzle 16 allows the centrifugal pressure eruption through the associated passageway 22b to intrude, as shown at C, into the incoming jet stream fro-m nozzle 10 At the lower left-hand nozzle 10 in Fig. 2, the drawing discloses a bucket'22c moved further into the incoming jet stream from nozzle 10]. Then, the angle of bucket 220 changes and the outline of bucket 220 increases relative to the angle of nozzle 151 and the uniform outlet shape of nozzle 10 to allow the fluid streams to react so as to deflect the entire opposition force of the fluid in passageway 22b to one side of the incoming jet to a position shown by arrow A so as to tend to make rotor 22 accelerate in rotation. This aforedescribed and illustrated action between the fluid streams is given by way of example to illustrate a possible condition existing at some time during rotation of rotor 22 and is not to be considered limiting on this invention in any sense since the coaction between the fluid streams will naturally change as the speed of rotation and fluid flow rates and pressures vary. Therefore, this description may not accurately apply in all details under all conditions.

A speed governor control is provided for this turbine and also is usable on any other suitable rotating machinery. Speed governor valve 45 in Figs. 1 and 4 serves as a means for changing or regulating the fluid flow volume from the source (from conduit 40) through casing jet nozzle 10 for controlling the speed of rotor 22. Means is provided responsive to the centrifugal force of the fluid stream in the rotor member passageways 2222, created by rotation of rotor 22, for automatically regulating governor valve 45 to control the speed of rotor 22. Centrifugal force causes fluid pressure in buckets 22c since the outer open ends of these buckets are covered by track 19 with only a small clearance existing between rotor 22 and annular track 19. This pressure is tapped off housing 10 at port 10 through lead or conduit 56, having pressure gauge 58, to governor valve 45, here shown in Fig. 4 as a conventional, non-back-pressure, constant pressure, reducer valve. The centrifugal force of rotation adds to any inlet fluid pressure existing between spinner rings 22a within casing 10 so that the peripheral pressure at port 10 is greater than the fluid pressure within casing 10 and is a measure of the speed of rotation of rotor 22. Port 10 is located to measure this pressure in rotor buckets 220 a substantial distance after they have travelled past the lower left jet 10 and immediately before they reach the upper right jet 10 in Fig. 2 so that the inlet pressure of the fluid stream through nozzles 10] will have minimum effect upon the centrifugal pressure measured. This centrifugal pressure will provide an accuratemeasurement of the speed independently of the effect of the inlet fluid streams through nozzles 10 thereon, i. e., whether the inlet fluid streams through nozzles 10 are sufficient to completely or partially overcome the fluid pressure in passageway 2212 or whether the pressure in passageway 22b is greater than that of the fluid entering through nozzles 10].

The pressure in conduit 56 acts in the direction of the arrows in Figs. 1 and 4 against valve diaphragm 66 in Fig. 4, secured at its periphery in valve body 67, to expand chamber 68 so as to move valve stem 69 with valve heads 70 toward the left in Fig. 4 toward their seated position in valve body 67. Valve heads 70 each have equal and opposed cross sectional areas facing the upstream flow and the downstream flow (direction of fluid flow shown by arrows in Fig. 4) so that valve head operation is independent of the difference in pressure across the valve seat, the upstream pressure, and the back pressure. A compression spring 72 normally tends to move, by valve stem assembly 69, the valve heads 70 toward their open position by pushing diaphragm 66 toward the right to collapse chamber 68 with spring 72 being backed up by a bolt 73 rotatably mounted and fixed against axial movement in valve body 67 and having threadably secured thereon an adjusting sleeve nut 74. This bolt 73 is adjustable by adjusting wrench 75, shown in dotted lines, for adjusting the pressure response of governor valve 45.

When rotor 22 begins to overspeed, the pressure at port 10 is increased so that diaphragm 66 moves valve heads 70 toward the left and toward their closed position to decrease the amount of fluid entering conduits 50 from the source of fluid pressure through conduit 40. When the rotor 22 tends to overspeed and the governor valve 45 moves toward closed position, the jet pressure through nozzles 10] is reduced with the centrifugal pressure through passageways 22b having a greater decomposing or resisting effect thereon so that rotor 22 quickly slows up to its proper speed. If the speed of rotor 22 slows to its normal operating speed, valve heads 70 in Fig. 4 are moved toward the right by the bias of compression spring 72 to admit normal fluid flow which reforms the compositions of forces after they were deco-mposed.

This turbine is preferably a constant load and constant speed turbine but the disclosed construction can be used to control the speed by varying the quantity of fluid supplied thereto if the load is varied. I

A tachometer 60 is provided in Fig. 3 to indicate the R. P. M. of output shaft 24 and to aid in the adjusting of bolt 73 in governor valve 45 so as to keep the valve in a iven open position against the pressure in line 56 to maintain the constant R. P. M.

The turbine may be operated in any suitable manner and the following description is given by way of example. The starter motor 27 rotates rotor 22 in the direction of the arrow B in Fig. 2. This rotation causes the centrifugal force to build up fluid pressure in buckets 22c by sucking fluid from within housing 10, through passageways 22b into buckets 220. While rotor 22 is rotated entirely by starter 27, inlet pressure valve 42 in conduit 41 in Fig.1 as well as exhaust valve 52 are preadjusted for maintaining proper pressure within housing 10 by reference to pressure gauges 61, 62 in Fig. 1. The pressure from the source in lead 40 may be constantly maintained at a predetermined pressure by a conventional regulator (not shown) with this pressure being coordinated with the stages of starter 27, 'i. e., being of suflicient pressure 50 that the pressures exerted within buckets 22c caused by the streams emerging from nozzles 10] are approximately equal to or at least equal to the centrifugal pressures'in buckets 220 when rotor 22 is rotated by starter 27. Valve 44 may then be fully opened from'its initial closed position to admit fluid to nozzles 10 As rotor 22 is brought up to proper speed by starter motor 27 and nozzles 10 and the normalquantity of fluid is travelling through casing jet nozzles 10 the valves 42, 52 may have to be readjusted since fluid entering through nozzles 10 also spills out into the housing. After the rotor 22 is rotating at proper speed, governor valve 45 is adjusted in relation to the pressure registered by gauge 58 and the rotational speed desired by rotor 22 to take over the flow control function of valve 44. a

If desired, governor valve 45 may be adjusted to increase fluid flow right from the beginning instead of requiring the use of valve 44. Starter motor 27, being of the multiple stage type, will permit bringing the turbine up to its normal operating condition by rotating rotor 22 at a constant speed of a starterstage while permitting increase of the fluid flow quantity through and pressure in jet nozzles 1th and permitting gradual change of the governor valve adjustment in conjunction with the overspeed ambition of the turbine until the tachometer 60 registers the preferred R. P. M. with the turbine operating under the desired load at its proper operating speed. Then, the starter may be disengaged by clutch 38 and the turbine will continue its uniform operating characteristics.

Various changes in details and arrangement of parts can be made by one skilled in the art without departing from either the spirit of this invention or the scope of the appended claims.

What I claim is:

1. A turbine rotatable by pressurized fluid, comprising: a hollow casing; a rotor axially rotatably mountedwithin said casing, said rotor being defined by two ends and a circular periphery therebetween; fluid return-inlet aperture means in atleast one of said ends inwardly dis placed from the circular periphery thereof and extending thereinto; a plurality of arcuately spaced passageways in said rotor extending from said fluid return-inlet aperture means to a plurality of circumferentially spaced locations around the periphery of said rotor; and a pinrality of circumferentially spaced recesses in the periphery of said rotor at said plurality of circumfercntially spaced locations, each recess communicating with a corresponding one of said passageways, whereby rotation of said rotor will, by centrifugal action, aspirate a fluid adjacent said fluid return-inlet aperture means thereinto and will centrifugally pressurize and force said fluid outwardly through saidpassageways into said recesses; said casing being provided with port means, adapted to be supplied with a pressurized fluid, non-radially directed toward said recesses, in rapid sequence during rotation of said rotor, and adapted toangularly press, within each of said recesses in sequence, against said pressurized fluid which is centrifugally outwardly forced by rotation of said rotor; said hollow casing including means spacedly defining, with the circular periphery and at least a portion of one end of said rotor member, communication means effectively communicating said recesses and said fluid returninlet aperture means and adapted to pass deflected and excess pressurized fluid from each of said recesses and said port means to said fluid return-inlet aperture means. 2. A turbine rotatable by pressurized fluid, comprising:

a hollow casing; a rotor axially rotatably mounted within said casing, said rotor being defined by two ends and a circular periphery therebetween; fluid return-inlet aperture means in at least one of said ends defined by concentric spaced annular ring means inwardly displaced from the circular periphery thereof and extending into the interior of said rotor; a plurality of arcuately spaced generally radially directed passageways in said rotor extendin from said fluid return-inlet aperture means to a plurality of circumferentially spaced locations around the periphery of said rotor; and a p urality of circumferentially spaced recesses in the periphery of said rotor at said plurality of circumferentially spaced locations, each recess communicating with and comprising a substantial enlargement of the outer end of a corresponding one of said passageways, whereby rotation of said rotor wi l. by centrifugal action, aspirate a fluid adjacent said fluid return-inlet aperture means thereinto and will centrifugally pressurize and force said fluid outwardly through said passageways into said recesses; said casing being provided with a plurality of port means, each adapted to be supplied with a pressurized fluid, and being angularly directed, with a tangential component, toward said recesses, in rapid sequence during rotation of said rotor, and adapted to angularly press, within each of said recesses in sequence, against said pressurized fluid which is centrifugally outwardly forced by rotation of said rotor; said hollow casing including means spacedly defining, with the circular periphery and at least a portion of one end of said rotor member, communication means effectively communicating said recesses and said fluid return-inlet aperture means and adapted to pass deflected and excess pressurized fluid from each of said recesses and said port means to said fluid return-inlet aperture means.

3. A turbine rotatable by pressurized fluid, comprising: a h llow casing; a rotor axially rotatably mounted within said casing, said rotor being defined by two ends,

and a circular periphery therebetween; fluid return-inlet aperture means in at least one of said ends inwardly displaced from the circular periphery thereof and extending thereinto; a plurality of arcuately spacedpassageways in said rotor extending from said fluid return-inlet aperture means to a plurality of circumferentially spaced locaticns aro-und the periphery of said rotor; a plurality circumterentially spaced recesses in the periphery of said rotor at said plurality of circumferentialiy' spaced locations, each recess communicating with a correspondbig one of said passageways, whereby rotation of said rotor will, by centrifugal action, aspirate a fluid adjacent said fluid return-inlet aperture neans thereinto and will c'entrifug'ally pressurize and force said fluid outwardly through said passageways into said recesses; said casing being provided with port means, adapted to be supplied with a pressurized fluid, non-radially directed toward said recesses, in rapid sequence during rotation of said rotor, and adapteddo angularly press, within each of said recesses in sequence, against said pressurized fluid which is c'entrifugally outwardly forced by rotation of said rotor; said hollow casing including means spacedly defining, with the circular periphery and at least a portion of one end of said rotor member, communication means eflectively communicating said recesses and said fluid return-inlet aperture means and adapted to pass deflected and excess pressurized fluid from each of said recesses and said port means to said fluid return-inlet aperture means; means responsive to centrifugal force at the periphery of said rotor created by rotation ofsaid rotor for controlling the speed of said rotor.

4. A turbine rotatable by pressurized fluid, comprising: a hollow casing; a rotor axially rotatably mounted within said casing, said rotor being defined by two ends and a circular periphery therebetween; fluid return-inlet aperture means in at least one of said ends defined by concentric spaced annular ring means inwardly displaced from the circular periphery thereof and extending into the interior of said rotor; a plurality of arcuately spaced generally radially directed passageways in said rotor extending from said fluid return-inlet aperture means to a plurality of circumferentially spaced locations around the periphery of said rotor; a plurality of circumferentially spaced recesses in the periphery of said rotor at said plurality of circumferentially spaced locations, each recess communicating with and'comprising a substantial enlargement of the outer end of a corresponding one of said passageways, whereby rotation of said rotor will, by centrifugal action, aspirate a fluid adjacent said fluid return-inlet aperture means thereinto and will centrifugally pressurize and force said fluid outwardly through said passageways into said recesses; said casing being provided with a plurality of port means, each adapted to be supplied with a pressurized fluid, and being angularly directed, with a tangential component, toward said recesses, in rapid sequence during rotation of said rotor,

and adapted to angularly press, within each of said recesses in sequence, against said pressurized fluid which is centrifugally outwardly forced by rotation of said rotor; said hollow casing including means spacedly defining, with the circular periphery and at least a portion of one end of said rotor member, communication means effectively communicating said recesses and said fluid returninlet aperture means and adapted to pass deflected and excess pressurized fluid from each of said recesses and said port means to said fluid return-inlet aperture means; means responsive to centrifugal force at the periphery of said rotor created by rotation of said rotor for controlling the speed of said rotor by regulating the flow of pressurized fluid through said port means of said casing.

References Cited in the file of this patent UNITED STATES PATENTS 863,210 Patitz Aug. 13, 1907 1,010,905 Harrison Dec. 5, 1911 1,063,089 Walker May 27,-1913 1,088,761 Anderson Mar. 31, 1914 2,181,741 Rosch Nov. 28, 1939 2,626,655 Trautman et al. Ian. 27, 1953 2,633,327 McDowell Mar. 31, 1953 2,635,848 McDowell Apr. 21, 1953 2,640,678 Andressen June 2, 1953 2,657,902 Williams Nov. 3, 1953 2,669,092 Hammaren Feb. 15, 1954 FOREIGN PATENTS 59,262 France Jan. 6, 1954 (Addition to 954,916) A 347,966 ltaly Apr. 29, 1937

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