US2776086A

US2776086A - Fluid compressor or pump

Info

Publication number: US2776086A
Application number: US277243A
Authority: US
Inventors: Irving H Selden
Original assignee: Individual
Current assignee: Individual
Priority date: 1952-03-18
Filing date: 1952-03-18
Publication date: 1957-01-01
Anticipated expiration: 1974-01-01

Description

Jan. 1, 1957 l. H. SELDEN FLUID COMPRESSOR OR PUMP 2 Sheets-Sheet 1 Filed March 18, 1952 *l/fl/l/flllf I I I f I I f I I I I I! IN VEN TOR.

Jan. 1, 1957 I. H. SELDEN FLUID COMPRESSOR 0R PUMP 2 Sheets-Sheet 2 Filed March 18, 1952 filllilllill'l'i'l I I M Ow United States Patent FLUID COIVIPRESSOR OR PUMP Irving H. Selden, Tacoma, Wash.

Application March 18, 1952, Serial No. 277,243

8 Claims. (Cl. 230-45) This invention relates to fluid pumps or more specifically to rotary compressors and has particular reference to compressors adapted to be operated at high speeds and to compress relatively large volumes of air to substantial pressure within the compressor. Such compressors are inherently reversible so as to be operable as motors and it is within the scope of this invention to include such use. However, for sake of simplicity of description the apparatus forming the subject matter of this invention will hereinafter be described and claimed but without limitation as to motor use, as compressor apparatus.

Positive rotary compressors with good volumetric efliciency have long been the object of investigation. However, the problems of line seals, proper clearances and tolerances and noise of operation due to their designs solely specifying metals have been hard to solve. Now with the constant developments of improved plastics it may be possible that most of the old obstacles to this type of compressor can be overcome. Polyethylene plastics capable of withstanding temperature ranges of 250 degrees recently developed may be applicable for certain parts but in using the word plastic in this specification no particular plastic is referred to but the term is used loosely with the aim being that special thought be given to each adaptation in separate parts of the compressor in as much as certain parts would necessarilyrequire a plastic of more resilience than others. In this connection rubber or rubber compounds may be covered by the use of the word plastics.

Methods of fastening all the plastic parts in their respective places are not specifically covered but it is assumed they will be cemented to the metal parts in an approved manner.

In the development of 'a new piece of mechanism such as herein specified it is hard to foresee definitely to what surfaces the application of plastics would attain the most efiicient results, consequently it has been a constant aim in this design to be all inclusive of any adaptation of plastics for seals, valves and resilient surfaces. It is also the belief of the inventor that the most elficient compressor built from this design would not include all the plastic adaptations shown.

One of the main objects of this invention is to avoid line seals. In the application of resilient plastic surfaces on adjacent rolling cylindrical bodies with suflicient mechanical pressure between them to form two dimensional seals such a result may be achieved. This may be clarified as follows:

If two steel cylinders with parallel axes are placed against each other side by side their common line of contact is merely a line. The use of line seals in this art is unsatisfactory because blowby and wear from dirty fluids soon pit the surfaces thereby rendering them impractical.

However if two cylinders with resilient plastic surfaces and parallel axes are forced together with sufiicient pressure their common contact surface becomes an area of two dimensions. In this art such a condition when used to withstand increased fluid pressure may be referred to as a two dimensional seal and is practical because sufiicient mechanical pressure between the bodies can be applied to prevent blowby and small particles of dirt no matter how hard may roll through this contact area without any permanent harm to the rolling parts.

Due to the scale used in this design and ratio or sizes of parts it was predetermined there would have to be 4 abutments and 4 vanes to give the highest efficiency to its piston displacement. However a change in the number of pistons and/or abutments should not be construed to be outside the scope of this invention.

Other objects of this invention are to provide a rotating or rolling vane or piston and fan blades on the intake side of the main rotor thereby giving a supercharging effect to the intaken air or gases.

These and other objects are attained by the devices, mechanisms and arrangements illustrated in the accompanying drawings, in which:

Fig. 1 is a section taken on the line 1-1 of Fig. 2.

Fig. 2 is a cross-section taken on the line 22 of Fig. 1.

Fig. 3 is an enlarged section of 2 rotary abutments in their proper relation to each other in a segment of the main rotor housing but turned to positions out of proper sequence to each other, and a sector of the main rotor is left out in order to show the two vanes in their relatively untrue positions, to demonstrate certain phases of the compression cycle.

Fig. 4 is .a cross-section of part of the main rotor housing where it encloses a rotary abutment.

Fig. 5 is a cross-section of part of a cylindrical vane.

Similar numerals of reference refer to similar parts throughout the several views.

Referring now, to the drawings, it will be seen that the fixed frame comprises an enveloping casting 6, of general circular section, having a series of four extensions 7 equally distributed around the circle and adapted to enclose the four abutments, hereinafter described, and closed by two end plates 8 and 9, suitably shaped to cover the central casting and bored and adapted to receive end plates'10 of abutment housings or extensions 7. The said plates 8 and 9 are secured to the enveloping casting 6 to form the containing frame.

The end plate 8, on the intake side of the machine, is provided with a series of openings 12,, between louvers or blades 13, around the axis of the machine and each blade 13 is inclined to the axis so as to give the air, passing through the blades, an initial circular or spiral mo tion in the direction of rotation of the rotor.

The shaft 14 is mounted in suitable bearings 15 in the plates 8 and 9 and carries the hub 16 of the rotor. As seen in Fig. 2, this rotor is provided with an end plate 17 in which inlet ports 18 are formed between radially inclined fan blades 19 extending inward and adapted to draw air, or other fluid, through the inlet ports 18 and the openings 12 in the rotor housing by screw action. The outer surface of the hub 16 is curved, as shown, to direct the inflowing fluid outward towards the periphery of the rotor.

The interior of the rotor is equpped with a ring of blower blades 20. These blower blades subtend a radial angle and extend a part way to the hereinafter described rotor drum, leaving an opening or passage 21 between the drum and their sides. The blower blades 20 extend horizontally across the rotor.

Four blower blade extensions 22 are appropriately placed to close passage 21 and effectively deflect the fluid into the passages 23 provided behind each piston or vane for the centrifugally actuated fluid from the interior of the rotor to be delivered into the channel 24 wherein it is positively compressed between the next succeeding piston andthe next intervening abutment.

The space between the inner surface of the enveloping casting 6and'the outer surface of 'the'drum section 25', or main rotor, forms a closed channel 24 in which the pistons 26, travel.

Each-abutment comprises a cylindrical body, 27; fit-' ting with suflieient clearance to prevent friction, in the extensions'7 of theenveloping frame 6, and is positioned so that its external surface is substantially tangent to the drum 25'of the rotor, with'either the rotor drum'or the abutment or both sufliciently. surfaced with a slightly resilient plastic. These .two bodies tobe fit with sufficient pressure between them to forma surface of two dimensions'thus avoiding a line seal. The dimensionsofgthe component parts are suchthat the abutments, will turn 4 times 'as fast as the mainv rotor. The pitch diameters of i the gears (not shown) that turn the abutments beingthe same as thediameter of the main. rotor and thediameter of'the.abutments. Consequently the only, friction here would be that ofrolling friction.

The main gear and pinion gears to drive theabutments are not shown but would be placed on the left end (see Fig: 2) of the main shaft 14 and abutment shafts28 and have a ratio of 4. to 1.

Thenouter surface of the abutment 27"has a passing slot 31. The slot being of less length than the abutment body but of sufficient clearance to allow the rotating vanes 26 .to pass.

The'rotatingvanes 26 (Fig. consist of a hollow cylindricalbody mounted on suitable bearings 36 and shaft 34. Shaft 34 is held in annular rings 35and keptfromturning by square boss 37" on end'of shaft 34' in square holes in rings 35. Annular rings 35 are the same diameter as and bolted to the ends of the main rotor drum 25 and are the same width as the abutment extension 29 of'abutments 27. Plastic sleeve 40 covers the cylindrical surface of the vanes 26 giving them a slightly resilient surface which when properly fitted with sulficient pressureagainst the outer curved plastic surface 38.0f annular channelf24 will give a seal-oftwo dimensions, thus avoiding another line seal. The only friction here Would'be that of rolling friction and the bearings. The plastic discs 41 fastened. to the ends of the vanes 26 are of 'aresilient nature and are so constructed as to exert a slight outward pressure at point 42. Disc,41[ is not cemented to sleeve 40but allowed to open a little at their joiningsurface to allow discs 41 to continue to exert a slight outward pressure evenv after a slight. amount .of

wear.

This outwardipressure would have the same effect in sealing the air channel as a leather suckeron an air pump andthe pressure against the sides .ofthe channel would increase with the airpressure. This feature .would be important on a compressor designed'to run very slowly but in compressors of average speeds'wou'ld lose its importance due to'the terrific'speed the vanes wouldtravel, approximately 3 times as fast as a pistonin a .reciproe eating engine of comparable size turning 'at'the'same R; P: M. However it'seems important to have plastic discs on the endsof the vanes if only to reduce noise. The vanes-rotation on'itsaxis is due mainly to'the friction against the curved'surface 38'.

In cases of'wearor improper fit between" the rolling; vane and outer channel surface 38 the square bosson the end of the vane shaft may be ground ofi'theside'desired as the case may be and properly fitted'shims placed on the opposite-side of the boss to regulate the'fit.

Fig; 4 shows plastic ring- 43 fastened. on the ends 'of'. the abutments 27. It will 'be noted that ring -43"is-feath ered toward its greatest circumference which is'formed' to exert a slight outward pressure against enclosing plate This pressure supplemented-bythe'pressure'of fluids against its back side should supply a practical seal' in preyenting 'saidfluidsfrom passing the'ends'ofthe abut mentsto blowout by the bearings. Plastic-"rings 44'--are fastened to the annular rings 35' and turn with thiem=and the main rotor. They arealso featheredat'thei-r'outer' 4. circumferences and seal the gap between the annular rings 35'andthe main end plates 8 and 9.

Fig. 3,

numbers

45, 46, 47, 49 and 50 illustrate plastic seals at the vanes and abutments. Due to the fact the rotors and abutments both turn away from the surfaces to be sealed it facilitates the application of these plastic seals. The lines being sealed run the full length of the abutments or the rotary vanesand seal the lines where the circumferences of. the-abutments-intersect the arcs formed by the line 38 and the lines where the vanes intersect the outer circumference-25 of therotor.

Two. types are shown, 45, 46, and .47 maybe-called a parallel type for they are parallel to the curved surfaces of the smallest arcs, and-.49-and 50.;a..perpendicular type, the latter two being approximately perpendicular to the surfaces of the smallest arcs being sealed.

In the cases of 45, 46 and 49 and 50, either type would suffice. but in the case. of 47 the parallel. typenis imperative. Seal 47 is an auxiliary sealto prevent blowby at thecircumference of abutmentsi29' when the abutmentopenings 31. are in such a position as to render the. seals 46 for 49 ineffective. In the sonamed perpendicular seals 49'andi50 their back sides are cut away at the ex.- treme contact point to allow for flexibility and clearancev for wear. The pressure of thefluidfagainst these seals supplementsv their natural'resilience to. make them effective,;wh-ich is alsothe casein the parallel 'type but in the parallel type clearanceon the outside of these seals must besa feature at their .rear. tapered ends to allow the fluids under pres-surea surf-ace .to..work on. Saidi'clearances are showngreatly enlarged. forillustration purposes only;

Fig. 3illustrates themaximumwor-king length ofa.

compressionst-roke. The. positions .of the vanes asshown. is .a result of removing a sector of'the main rotor-.and placing'the twovanes closer. togetherthanis their true position..o'f 90. degrees apart. This naturally turnsthe,

abutments 27," out of proper relation. to .eachother. The. amount of ,degrees-0f.turn-required.by abutment B to .pass.

vane D from itsentering positionasshowntoa departing, position. as illustrated. by relative positions .of abutment A1 andvane vC is 38ldegrees. Assuming;that abutmentvA' is in. its normal position then abutment B is. turned38. degrees behind, its normal position. andvane. D is 9 /2. degrees behind-its proper relative position for. asbefore stated. the. abutments. rotate four. times as, fast asthe.v

the vanes are approximately in a position as.illustrated..

byabutment ,B. and. vane. D. The. compression-.ratioat this point is about 6.7 to .1.. Outletor exhaustports32are. apparently cut off v by. vane- D'. as :seen. in position of .vane.

D; however thisis .not.the case. astheedges ofpassages 32v arereceded onv the arc.side.ofwsaid. portsatthezarc. formed by the lines of theabutments. Thus .the,port .32..

opening. is notin one geometric. planerbutlalsoopensa into. the arc of the circle that the. abutmentsturnintr.

There are 2'outlet ports 32 in each channel.section.o1'..4

0 through eachend plate '8. and. 9, makinga total of 8 ports 32 in the compressor. Thereare no .exhaustvalvesz shown .due to the limited space butforwthe machine.to..be.- practical there wouldhave ,to.be.an.-automatictvalvezin.

each passagebetween ports 32and a main disch-argemanifold and the closer to the main channel .24 .themoreeflicient the compressor.

Fig. 4 shows..part.of.an:abutment'27 with itst-passing).

In Fig. 3, the function of automatic intake valves 52 can be best explained if we assume that abutment B and vane D are in their proper location and consequently abutment A would be rotated back 38 degrees and vane C would be back 9 /2 degrees to be in the same relative positions as abutment B and vane D. As the main rotor 25 rotates to the right, abutment B rotating to the left soon breaks the seal between the outer circumferences of said bodies as the abutment opening 29 turns into channel 24, at practically the same instant the vanes 31 (see vane D) continuing into the passing slots of the abutments break the seal between their outer circumference and outer channel surface 38 and as the fluids compressed into abutment openings 31 are released into main channel 24 the direction of the fluids flowing through channels 23 is reversed and the back pressure of said fluids blows automatic valves 52 closed as shown at vane C.

Lateral segments 53 offer very little resistance to the flow of the fluids through the spacious passages 23. The intake passages 23 have a cross-section approximately /4 as great as the main channel itself as can be seen for they extend virtually the full width of the rotor. The said segments 53 merely divide channel 23 into several smaller channels their purpose being to furnish a seat to suitably support valve 52 when it is closed. Valve 52 itself consists either of suitable rubber reinforced with fabric or a piece of suitable plastic properly fastened at one end to the interior of channel 23 in main rotor 25 lying free at the other end and normally closing channel 23 as seen at vane C, but opens as shown at vane D when the air pressure is greater from the center of the rotor than from the main channel. This furnishes a valve of great volume and little resistance and at the same time the centrifugal force from the speed of the rotor would have little effect on it due to its position approximating that of a radial line.

The purpose of these valves is to retain as much fluid in the main channel as possible; thus when the next succeeding compression stroke begins the said fluids may have a higher than atmospheric pressure.

The machine should have proper lubrication for its plastic surfaces depending on the types of plastics used. In some adaptations suflicient lubrication could be derived from the Water used in air cooling processes sometimes used to increase the efliciency of compressors whereby the air could carry enough humidity to properly lubricate the plastic surfaces.

If a drier compressed air were required the plastic surfaces would no doubt have to be lubricated by oil in which case the plastics used would have to be of a type impregnable to the type of oil used.

Description of action As the rotor is turned, the piston 26 which is receding from one of the abutments 27 causes a partial vacuum in the channel 24 and in the

passages

21 and 23, thus drawing air from the intake ports 12 and 18. As the air passes the blades 13 in the end of the rotor housing it is given a swirling motion thereby, thus entering the rotor with an initial spiral motion. This rotary motion is increased by the fan blades 19 which also have a strong sucking effect on the air.

As the fluid starts to rotate and is drawn in, the centrifugal force is supplemented by the low pressure volume behind the piston 26 which is connected by the

large passage

21 and 23 with the interior of the rotor. As the piston 26 passes the next abutment 27, the abutment has rotated to close the channel 24. Thus the succeeding piston 26 compresses the fluid in the said closed channel against the abutment ahead of it. Then, as the piston 26 approaches the abutment the fluid is forced by the positive compressive action of the piston, through the outlet port 32.

Having therefore described my invention, what I claim and desire to secure by Letters Patent, is:

1. In a rotary compresson unit having an enclosing circular frame; a hollow cylindrically shaped rotor mounted concentrically therein to form an annular channel and adapted to travel therein; vanes on the rotor effectively closing said channel; a plurality of rotating abutments mounted in said frame and extending into said annular channel and into egagement with said rotor, dividing said channel into intake and compression chambers, said chambers to be used alternately as intake and compression chambers; slots in said abutments adapted to mesh with each said vane as it passes said abutments; exhaust ports through the enclosing frame from the intake and compression chamber on the compression side of the abutments; an intake passage on one end wall of said frame consisting of an annular opening therethrough concentric with said rotor; intake ports in the adjacent end wall of said rotor, consisting of an annular opening therethrough concentric with said rotor and adapted to admit fresh charges into the interior of said rotor from said intake passage; said intake passage on said end wall of said frame formed by a series of radial louver blades mounted in said end wall, designed and pitched to transmit a minimum of friction to the fluid as it enters said intake passage; radial fan blades mounted in said intake ports in said adjacent end wall of said rotor and having a pitch in the opposite direction to that of the said louver blades in said end wall of said frame and cooperating with said louver blades to draw fresh charges into said rotor and to force them into passages between longitudinal-blades within said rotor which assist in further compressing said fluids to force them through openings in the periphery of said rotor adjacent to the vanes on the low pressure side of said vanes into the annular channel where the fluids are further compressed between the vanes and the abutments.

2. In a rotary compression unit having an enclosing circular frame; a hollow cylindrically shaped rotor mounted concentrically therein to form an annular channel and adapted to travel therein; vanes on the rotor effectively closing said channel; a plurality of rotating abutments mounted in said frame and extending into said annular channel and into engagement with said rotor, dividing said channel into intake and compression chambers, said chambers to be used alternately as intake and compression chambers; slots in said abutments adapted to mesh with each said vane as it passes said abutments; exhaust ports through the enclosing frame from the intake and compression chamber on the compression side of the abutments; an intake passage on one end wall of said frame consisting of an annular opening therethrough concentric with said rotor; intake ports in the adjacent end wall of said rotor, consisting of an annular opening therethrough concentric with said rotor and adapted to admit fresh charges into the interior of said rotor from said intake passage; radial fan blades mounted in said intake ports in said adjacent end wall of said rotor cooperating with said intake ports to draw fresh charges into said rotor and to compress them therein; arcuate channels from the interior of the said rotor extending to rectangularly shaped longitudinal ports in the periphery of said rotor adjacent to the vanes on the low pressure side of said vanes adapted to deliver said charges into said intake and compression chambers; a flow of fluid alternating in direction through said rectangular ports in said rotor due to varying pressures in said intake and compression chambers; lateral seating segments in said arcuate channels, spaced sufliciently apart and extending from the side of the channel opposite said vane to a line from the intersecting point of the opposite side of said arcuate channel and the circumference line of the rotor drum and tangent with the inner convex surface on the side adjacent to the vane where the channel leads out of the inner side of the rotor, to substantially form a valve surface; a plastic flap at each of said ports designed to rest on said lateral seating segments and to substantially cover said segments, said flaps fastened at their, central or interior end, atsai point suflicientlybeyondiits tangential :contact line. withisaid convexsurface'. when .in a closedposition;

tosexertayeryslight pressure whennormal against said lateral seating. segments andofsufiicient dimension'to effectively close said port when the pressureris greater :on

theintake and compression.sideiofsaidport and to readily open when the pressureis greater onrthe interior or cenrality of rotating abutments mountediin said frameand! extending. into said annular channel and .into. engagement withv said rotor, dividing said-channel into intake and compression. chambers, said). chambers to beused alternately as intake and compression chambers; slots in said abutments adaptedto mesh'with each said vane as it passes said abutments; said-1 vanesconsisting of cylindrically shaped rollingbodies arranged to substantially.

close said annular channel, traveling in a rolling position with their outer surface rolling against the inner arc of the enclosing frame where it forms the outer circle of the said annular channel.

4.- In a rotary compression unit'having an enclosingcircular frameconsisting 0f.a central body and two end plates; a hollow cylindrically shaped rotor mounted concentrically therein, to form an annular channel and roll-' ing cylindrical vanes on the rotor arranged to travel insaid annular channel the .ends of said vanes laying adjacent to said frame. end. plates, a plurality of rotating abutments turning. in frame'extensions on shafts supported by bearings in separate end plates at said frame extensions said ro-tatingabutments extending into said annular channel and into engagementnwith; said rotor, dividing said' channel into intake and compression chambers, saidcham bersto be used alternately as intake and compression chambers, concave passing slotsiin said abutments adapted: to mesh with each said vane asit passes saidabutments; 40

plastic ring members of substantial thickness and substantially fastened, one to each end of each said vane, one to each end of each saidabutrnents, and one to each end of said hollow rotor; coaxial with and of the same diameter as each'respective body andeach exertinga longi-w tudinal pressure at its greatest circumference .against their;

respective said end plates; whereby a seal is formed-be tween said bodies andsaid endv plates.

5. The rotary compression unit-of the class. described as set forth in claim. 4,- inwhich each ofthefollowing: surfaces is.equipped with a .substantiallayer of resilient,

plastic; the cylindrical vanes-on. their-.entirezconvex surface; the entire concave surface of'the enclosingwframe'.

central :body where it formswthe. outer arcs of the annular channel; the entireconvex surface of therotora- 66 Where itforrns theinner surface of .the' annular channel;

the entire convex andconcave'surfaces of-the abutrnents; the relative bodies so positionedand adjustedas to employ the resilient qualities-in said-plastic surfaces to the;

extent that the contiguous parts areno longertrue'arcs but depressed .to suclradegneeas to form--a:contact area as against a line which -would-be-..the contact point between two touching. geometrically perfect cylinders of parallel axes if side by side; wherebya two dimensiona al seal is for red between each said abutment convex sur- 6. in a rotary compression unit havingtan. enclosing,

circular frame consisting of a-central body and two end plates; a hollow cylindrically shaped rotormounted concentrically therein, to form an annular channel andv rolling vanes on the rotor arranged. to travel in said.an-

75-.- said rolling vanes and said rotor-being parallel :to allow nular-ucliannel, saidv rolling vanes recessed in concave pockets in-therirn-of saidrotor, a plurality of rotating abutments turning in frame. extensions'on shafts supported bybearingS-in separate end plates at said frame extensions,=. said; rotatingi abutments extending into said annular ch'an nel and dividing saidiannular channel into intake-andcompression chambers, said chambers to be .usedalternately; asintake and compression chambers; slots'in said abutments-adap ted vto mesh witheach said vane as'it passes said 'abutrnents, theforward sides of-said vanes and said: abutments being the. approaching side and the side ap proached-respectivelyas the rotor turns to the right, compressed fluids-in said compression chambers; a plastic. flap-at each' vanelying; parallel to the convex surface. ofeach saidivane within said-concave pocket of said rotor on the forward side of said vanes and extending; to a line of intersection between the circumference of said vanes and the greatest arc ofthe rotor, and extendinggthe full lengthof the vane; a plastic flap; seated within theeframeextensions, parallel to the'convex surfaceof-the said abutrnents and extending to the line Of'lI'll'CIt section between the. circumference of said abutment and. theate ofthe annular channel formed by'said enclosingframe,' on the. forward side of saidab'utments and-extending the entire-length of said abutrnents; an auxiliary plastioflap seatedwell within the frame extensions a distanceslightly greater than the arc subtended-by the abutment.passing-,slot, measured on the forward side of said.abutmentffonrthe intersecting lineformed where ;the circumferenceof saidv abutment intersectsthe arc of.th'e annular: channel formedby said central body, lying; parallelto. thev convex surfaceof said .abutments andextndingthe entire length of said abutrnents; a plastic flap seatedwithin the rotorrim atthe-forward side and, againsteach said rollingvane and approximately per: pendi'cular to the convex surfaceof said vane and extending' tlie' entire lengthbf saidvane; a plastic fiapseated. within stem; of the. annular channel in said framecen tral 'body'on'the forward side and against each said abutmen-t and approximately perpendicular to. the. convex surface of'.said"abutm'ent and extending the entire length of saidabii'tnrent'; all of said'plastic.fiaps of sufficient width and substantially fastened and shaped to respond to the pressure of the compressed-fluids to effectively; form: seals" first betweenthe forwardside of said vanes andthe rimof said'rotor at the line where the convex arcs of these bodies intersect and second between said frame central body at the abutments where the arcs of said frame central body and'said'abutments intersect on meter: ward sideofsaidabutrhents and third'atthesaid auxiliary 'seals of the abutments wellwithin the frame extension between said frame extension 'andsaid. abutments; whereby seals areformed-to prevent blowby between .the said rotor and the convex surface of said rollingvanes'; and. whereby seals are formed to prevent blowby between the. convexlsurface of said'rotar'y abutments and the. said. enclosing frame central body and-betweensaid abut-f ments" and said frame extensions;

71" Ina rotary compressionunit having an enclosing. circular frame; a hollow cylindrically shaped rotor mount 'ed concentrically therein to form an annular channel} vanes on the rotor arranged to travel in said annular-channel;-'a*plurality" of rotating abutments mounted'insaid fr'arneand extendinginto said annular channel a'nd'into engagement with said rotor, dividing said channel 'into 'intake'*and"'compression chambers, said chambers to be used-alternately asintake and compression chambers; and=slots insaid'abutm'ents adapted to mesh witheach saidvaneas it'passes said abutrnents; said'vanes' consisting"of"cylindrically"shaped rolli'ng bodies arranged.

- to substantially close said'annular channel, eachof said rolling vanes-suitably mounted on a vane shaft, said shaft extending into and supported by two'annularvan'e mounting: rings' coaxial. with said rotor 'and" fastened substantially to opposite endsof said rotor; the axes of the vanes to roll in the annular channel against the concave surface of said annular channel.

8. In a rotary compression unit having an enclosing circular frame; a hollow cylindrically shaped rotor mounted concentrically therein to form an annular channel; vanes on the rotor arranged to travel in said annular channel; a plurality of rotating abutments mounted in said frame and extending into said annular channel and into engagement with said rotor, dividing said channel into intake and compression chambers, sa'id chambers to be used alternately as intake and compression chambers; and slots in said abutmen'ts adapted to mesh with each said vane as it passes said abutments; said vanes consisting of cylindrically shaped rolling bodies arranged to substantially close said annular channel, each of said rolling vanes suitably mounted on a vane shaft, said shaft extending into and supported by two annular vane mounting rings coaxial with said rotor and fastened substantially to opposite ends of said rotor, the axes of said rolling vanes and said rotor being parallel to allow the vanes to.roll in the annular channel against the concave surface of said annular channel; said vane shafts terminating 10 in a square boss on each end to fit square holes in said vane mounting rings, said square holes so positioned to have one side perpendicular to and bisected by a radial line of said mounting ring, suitably arranged to grind one side or another 011 of said square bosses on said vane shafts and shims applied on the opposite side to provide means for adjustment for original fit or subsequent wear.

References Cited in the file of this patent UNITED STATES PATENTS 87,023 Boorman Feb. 16, 1869 137,056 Chapman Mar. 25, 1873 801,373 Gearhart Oct. 10, 1905 888,814 Jones May 26, 1908 1,404,717 Humphrey Jan. 24, 1922 2,383,194 Hoopes Aug. 21, 1945 2,407,753 Wallgren Sept. 17, 1946 2,418,793 Selden Apr. 8, 1947 2,603,412 Chilton July 15, 1952 FOREIGN PATENTS 178,861 Switzerland Nov. 1, 1935