US2241460A

US2241460A - Compressor

Info

Publication number: US2241460A
Application number: US313890A
Authority: US
Inventors: Ernest R Huntley
Original assignee: Individual
Current assignee: Individual
Priority date: 1940-01-15
Filing date: 1940-01-15
Publication date: 1941-05-13
Anticipated expiration: 1958-05-13

Description

May 13, 1941. E. R. HUNTLEY COMPRES SOR Filed Jan. 15, 1940 5 Sheets-Sheet 1 May 13, 1941. E, R, HUNTLEY 1 2,241,460

COMPRESSOR May 13, 1941.

E. R. HUNTLEY COMPRESSOR 5 Sheets-Sheet 3 Filed Jan. 15, 1940 ll? //5 I16 5% AW/a/y y 1941- E. R. HUNTLEY 2,241,460

COMPRESSOR Filed Jan; 15, 1940 5 Sheets-Sheei s Patented May 13, 1941 COIiflRESSGR Ernest 1R. Huntley, .Los Angeles, Calif., assignor to Leo Mrflarvey, La Canada, Calif.

Application January'15, 1940, Serial No. 313,890

24" Claims.

This invention relates to apparatus for the compression or evacuation of gases and relates more particularly to a compressor or vacuum pump of the centrifugal type. A general object of this invention is to provide-a practical, effective compressor that is highly efficient, requiring a minimum of power forits operation.

Compressors and vacuumpumps have been introduced in which a liquidsuch as oil or water is subjected to centrifugal action and in which gas is entrained in .the liquid-so that the liquid acts as the compressing agent. Such priordevices employ various meansfor causing the gas to be entrained in the liquid so that itis carried outwardly to the periphery of the impeller wheelto be subjected to apressure equal to the centrifugal pressure on the liquid .at the point of .discharge from the impeller. In such devices .practically all of the power consumed is represented by the energy required to accelerate the fluidfrom the peripheral velocity-at the pointof intake .of the impeller wheel to the velocity at the point of discharge from the impeller wheel. Theliquid discharging from theimpeller wheel .of such a device is theoretically capable of doing substantially as much work as the-work done inaccelerating the liquid to the velocity of discharge. This work or energy .in the liquid discharging from the impeller wheel is not efficiently utilized in the prior devices but is wasted or expended for no useful purpose. The prior devices do not embody effective means for .proportioning the liquid and gas handled by theimpeller wheel and a large part of the energy used in accelerating the liquid handled by'the impeller wheel is wasted. For these reasons the prior devices of the charac ter referred to are extremely ineiiicient and, therefore, expensive to operate.

Another and important object of this invention is to provide a compressor or vacuum pump of the centrifugal type mentioned above embodying a novel and highly efficient means for utilizing the energy in the heavy fluid or liquid discharging from the impeller wheel to promote efiicient operation-and reduce the cost of operation. The energy or a substantial portion of the energy in the rapidly rotating mass of heavy liquid leaving the rotary element of the present invention is utilized to assist in rotating the impeller thereby greatly reducing the power required to drive the compressor.

Another object of this invention is to provide a device of the character mentioned embodying a rotating element or impellerreceiving the liquid and the gas at its interiorand discharging the fluid at its periphery, "and-a rotatable casing enclosing theimpeller arranged to be drivenby the liquid leaving the periphery of the impeller and having a driving connection with the impeller to assist in rotating thesame. The casing embodied in the device of this invention is driven or rotated by the fluid putinto motion by theimpeller and is geared or-otherwise connected with the impeller to assist-in'rotating the same,thus reducing the power necessary to drive thedevice. The casing rotates in the same direction-as the impeller thereby practically eliminating the high fluid friction losses present in prior devices of this type embodying stationary casings for the impellers.

Another object of this invention is to provide a compressor of the character mentioned-in which the liquid employed as the compressingagent is used over and overagain or repeatedly recirculated.

Another object of this invention is to provide a compressor of the character mentioned embodying novel means for maintaining the fluid in the compression member in continuous motion thus eliminating the energy loss that occurs in most devices of this nature where the fluid must at some point pass through a port or nozzle in a stationary part and again be put into rotarymotion by the impeller.

Another object of this invention is to provide a compressor of the character mentioned embodying novel and effective means for removing the heat of compression from the compressing liquidwithout interfering with or stopping the above-mentioned continuous circulation of the fluid in the compressor.

Another objectof this'invention is to provide a compressor of the character mentioned in which the drive between theimpeller and the rotating casing provides a differential in the speed of rotation of the impeller and casing thereby setting up a differential in the pressures on the fluid in said passages, etc. to induce a continuous flow of the heavy fluid or liquid from its point of discharge from the impeller back to its point of delivery to the impeller.

Another object offthis invention is to provide a compressor of the character mentioned embodying a novel port member that rotates with the rotatable casing and which serves to alternately admit quantities of the gas and liquid'to the intakes of the impeller vanes or passages while rotating in the same direction as the impeller but at'a slower speedso'that the slugs or charges of liquid leaving the rotating portmemher are picked up by the rotating impeller with a minimum of shock and little or no loss of energy.

Another object of this invention is to provide a compressor of the character mentioned in which the fluid discharges from the impeller at a substantial distance from the intake openings of the impeller assuring a large capacity operation in a compressor of small size.

The various objects and features of my invention will be fully understood from the following detailed description of typical preferred forms and applications of the invention, throughout which description reference is made to the following drawings, in which:

Fig. 1 is a central vertical detailed sectional view of one form of compressor of the invention showing a part of the driving motor and other 7 as indicated by-line 44 on Fig. 2. Fig. 5 is a fragmentary horizontal detailed sectional View of another form of the invention, being a View taken as indicated by line 55 on Fig. 6. Fig. 6 is a central, vertical, detailed sectional view of the said other form of the invention, and Fig. 7 is a central, vertical, detailed sectional view of still another form of the invention.

The compressor or vacuum pump of the invention illustrated in Figs. 1 to l inclusive, of the drawings, may be said to comprise, generally, a housing ill, a rotary element or impeller II in the housing), a casing l2 rotatably supported in thehousing it and enclosing the impeller II, a port member is rotatable with the casing i2 and delivering liquid and gas to the impeller II, a drive 14 between the casing l2 and the impeller l l, a cooling system I 5 for cooling the compressing liquid employed in the casing 12, and port andconduit systems for handling the liquid and gas, the'details of which will be later described.

The housing If! contains the impeller H, the

casing l2 and the other active parts of the compressor. In the'construction illustrated the casing I0 comprises a base l6 having a horizontal wall ll spaced between its ends and a main housing member [8 supported on the base. Assuming the compressor to be positioned as illustrated in the drawings, the main housing member 58 is of inverted cup-shape and has a flange It on its lower edge secured to the upper end of the base l6 by screws 20. The drive means or power means for operating the compressor may be mounted on the member it. ,A rather large opening 21 is formed in the upper wall ofthe housing member [8 and an electric motor 22 or other power means may be secured to the upper end of the member 18 .by screws 23 to close the opening 2|. It will be observed that the base IS, the member I8 and the motor 22 define a sealed chamberizd that may contain the gas to be compressed. I have shown a pipe 25 communicating with the upper portion of the chamber 25 and leading to the atmosphere or ,to'a supplyof the gas to be compressed. If the device is to be employed as a vacuum pump the pipe 25 may lead to the space to be evacuated.

The horizontal wall l! of the base member l6 has a central depression-26 surrounded by an upstanding annular wall 21. A boss 28 projects downwardly fromthe wall- I] and has a central socket 28 communicating with the lower end of the depression 28.. A central opening 30 enters the boss 28 from its lower end and a plug 5i closes the lower end of the opening 39. An outlet pipe or discharge pipe 32 communicates with the opening 38. A check valve 33 is preferably connected in the pipe 32 to prevent the return flow of the compressed gas when the compressor is idle. The housing H1 forms the principal stationary element of the device and the base l6 may be suitably fixed.

The rotary element or impeller l l is supported in the housing It for rotation about a central vertical axis. The construction of the impeller H may be varied considerably without depart ing from the broader aspects of the invention. In the construction illustrated the impeller H has a central hub 3d and a disc-like main part 35 of enlarged diameter on the upper end portion of the hub 34. The impeller hub 34 is connected with the shaft 36 of the motor '32 to be driven by the motor. In the arrangement illustrated the hub 34 has an opening 31 in its upper end receiving the motor shaft 36. A flanged nut 38 is threaded or otherwise secured to the hub 34 and a collar 39 is pinned or otherwise fixed to the motor shaft st to oppose the nut 38. Axial pins 40 project from the collar 39 and are loosely received in openings ll in the nut 38 to provide for the transmission of rotation between the motor shaft 36 and the impeller l l. A longitudinal opening 42 enters the hub 34 from its lower end and a tubular shaft 43 is forcefitted or otherwise fixed in the opening 42. The shaft 43 projects downwardly fromthe hub 34 and passes through the depression 28 and the socket 29 to enter the opening 38. A suitable antifriotion bearing 44 is seated in the socket 29 to rotatably support the shaft 43 and the impeller ll. The tubular shaft 53 forms a conduit for the compressed gas as will be later described, and means is provided in the boss 28 for sealing about the shaft 43. This means may include packing 45 seated in the opening 39 and a coiled spring 46 under compression between the plug 3| and the packing 45 to hold the packing compressed. 7

The enlarged upper portion 35 of the impeller H is proportioned to have its periphery spaced a considerable distance inwardly from the wall of the housing It and preferably has a flat under side provided with a circular downwardly facing annular socket 4?. The impeller vanes or the compression passages for handling the fluid when it is subjected to the centrifugal action may be provided in a circular or annular part 48 secured to the under side of the part 35. The part 48 is arranged to have its inner surface at the peripheral wall of the socket ll and to have its periphery adjacent the periphery of the part 35. Pins or rivets 69 may serve to secure the part 48 to the part 35. The part $8 is provided with a multiplicity of circumferentially spaced compression passages 5%. The passages 59 are equally circumferentially spaced and are of the same size or capacity. The lower sides of the passages 53 are closed by an integral wall of the part 4-8 and the impeller part 35 closes the upper sides of the passages. The passages 53 are preferably pitched outwardly and rearwardly relative to the direction of rotation of the impeller H.

The impeller part "58 is further provided with spaced peripheral pockets 5| for receiving the compressed gas. The pockets 5| are spaced between the discharge ends of the spaced passages ape-1 460 55 .of reclining L-'shaped cross section secured to the upperside of the member 35. The inner ends of the radial portsf52 slope or curve upwardly and inwardly tow-ard'the-ports 53 to assist in directing the fluid to the ports 53.

The centrifugal action assures-'a complete separation of the gas and liquidinthe annular chamber 54. "Radial ports 55aare-provided in the impeller part35' and lead inwardly from the chamber'54lto the opening 42. The inner-fend of the tubular shaft 43 communicates with the inner portion of the opening 42 and the gas under pressure is'free to pass longitudinally through the shaft 33 to the opening 30 and thence through the discharge "pipe 32. 'Longitudinally spaced annularflanges 5! are provided on the periphery of therrimpeller ll to assist in directing the gas to the pockets 5'! as the fluid leaves'the compression passages'liil. On flange 51 may be formed on the impeller part 35 and the other may be formed on the partifi. The opposing sides of the flanges 51 are outwardly divergent.

The casing I2 is rotatably'supported in the housing I to enclose the impeler II. The casing I2is a hollow structure-comprising a gen" erally cylindrical 'cup-likesection 53 and plate 59.closingthe upper end of the section. The'in -peller lliiszarranged withinthe section stand theplate 59 extends across the upper end of the impeller with clearance. Screws may serve to attach the-plate '59 to the section '58. The section 5B'has an'openi-ng 6I passing the shaft d3with clearance and a suitable anti riction bearing 62 is set in the opening 6! to assist in rotatably supporting the casing. The plate 59 has a central opening 63 'receivingthe upper portion of the hub 34 with clearance-and an antiiriction bearing 64 isseated on the 'huband is and the upper and lower ends of the impeller are suitably spaced from the end walls of the casing. The casing I2 of course has suitable clearance in the stationary housing Ill. A boss 66 is formed on the lower end of the casing section 58 below the bearing 62. The casing 12 is ported, as will-be later described.

The port member I3 is provided to deliver or discharge the liquid and gas into the passages 59 of the impeller II. tates with the casing I2 and may be attached. to or may form a part of the casing. In the preferred construction the member i3 surrounds the hubfi iof the impelleri I with considerable clearance, leaving an annular spacetlaround the hub. As illustrated, the member I3 is a generally cylindrical part whose pei cooperation with the internal sur-facelof the-impeller part' lll. A disc-like enlargement 58 is provided on the lower end of the member I3 and The port member l3 ro- Til rests on the lower wall ofthe-casing' section 58.

Screws 69 may secure the port member -I3'to the section 58. The'enlargement 58'ha's substantial clearance with the under side of the impeller part 4'8 'leaving anannular space 15 "which communicates j with the outer portion of the casing chamber I 68. "The enlargement 58 maybe of substantially the same -diameter as the fianges 51- of the impeller I I.

The periphery-of the portmember I3'has-a plurality of axially extending circumferentially spaced liquid ports I2 and a plurality of 'circumferentially spaced axially extending gas, ports 73. Thegas-ports'73 may be smallerin'capacity than the ports 12 and are spaced between the ports. The

ports

12 and 13 extend between the upperand lower ends of the port member I3Land are open at the periphery of the member to discharge --into the passages "50" of the -impeller I I. Radialports l4 communicate with the lower ends ottheports 12 and :extend outwardly through the enlargementiiifl to the periphery of the enlargement. The ports "14 serveto circulate the 'fiuid or liquid from the peripheral portion of port member I3 to closethe upper ends-of the liquid ports 12. The plate I5Ihas openings placing the upper ends of the 'gasports l3 incommunication with the annular socketiflsin-the upper wall ofthe impeller I I. One or moreports 16 in the upper impeller part communicate withthe socket 41 so thatthe upper-ends of .the gasports I3 are maintained in communication with the upper'end of thecasing'chamber' 65.

One or more ports'll are provided in thecover plate 59 of the casing I2 to maintain the upper portion of the casing chamberBB in communication with the upper part of the housing chamber 24. or gas admitted to the housing chamber 24 by the pipe 25 is drawn through the ports 11 into the upper portion of the casing chamber 65 and is drawn from the chamber65 through the ports lfiinto the ports I3 in the rotating port 7 member I3.

With the compressor provided with the gas'port system described above the gas from the pipe 25 reaches the ports 13 and slugs or portions of the gas are delivered to the passagesinthe rotating impeller to be entrained with the liquid ad mitted bythe ports I2. The gas thus entrained with the liquid is subjected to compression by the centrifugal forces acting on the liquid in the passages 50 and upon leavingthe periphery of the impeller the compressedgas'is received in the pockets 5| and flows through the

ports

52 and 53 to discharge into the chamber 54. 7 From the chamber 54 the compressed gas passes through the ports 56, the tubular shaft 43 and the opening litv to the discharge pipe 32. It will be seen that there is a continuous circulation of gas from 'the. pipe 25 to the discharge pipe 32, thegas discharging under an increased pressure. It is im- .portant tonote that the liquid employed as the compressing medium is continuouslyrecirculated through the impeller I I while thefgas is being drawn in and discharged under increased pres- Sure g V The drive I4 between the casing I2 and the impeller I I transmits movement and power from the casing to the impeller so that the energy expended by the fluid discharging from the impeller II is utilized to assist in rotating the impeller I I. In accordance with the invention the drive I4 is a differential drive restraining the casing I 2 to rotate at a slower speed than the impeller II so that the fluid discharging from the impeller is effective in producing rotation of the casing I2 and so that the ports I2 and I3 alternately discharge into the impeller passages 59. The differential drive I4 may, of course, be varied considerably in character.

In the construction illustrated the drive I4 comprises a pinion I8 keyed or otherwise fixed to the casing boss 66 and a larger gear I9 keyed or otherwise fixed to the shaft 43 of the impeller I I. A vertical stub shaft 89 is fixed to the lower wall I! of the housing I to project upwardly in parallel relation to the shaft 43. A pair of connected ears 8| and 82 is rotatable on the shaft 89. The gear 8| meshes with the pinion I8 while the gear 82 meshes with the gear I9. It will be seen that the gearing just described constitutes a differential drive for transmitting rotation from the casing I 2 to the impeller II.

The means I serves to remove or reduce the heat of compression by continuously subjecting a stream of the compressing medium or liquid to a cooling action. The lower portion of the housing I 0 below the casing I2'and surrounding the wall 2! constitutes a basin or reservoir 83 for the liquid and a cooling coil .84 is arranged in this reservoir.

-A pipe 85 delivers a suitable cooling medium to one .end of the coil 84 and a similar pipe 86 conducts thecooling medium from the other end of the 'coil.

The invention includes a novel duct system for circulating the compressing liquid to and from the-.co'olingreservoir 83. Vertical or axial ports 81 are provided in the port member I3 and notches 88 in themember I3 connect the upper ends of the ports 81 with the liquid discharge ports I2. Theup-per inner portions of the ports wardly sloping surface 99 terminating in an abrupt annular shoulder 9|.

The liquid discharges from the ports 89 at the surface 99 and .centrifugalforce carries the liquid outwardly on the surface to the shoulder 9I where it discharges 'into the reservoir 83.

The case contains sufiicientliquid to maintain a level above the upper imipeller flange 51 and a small stream of liquid continuously discharges through the ports .89 to fall to the cooling reservoir 83.

' fRadial ports 92 lead from. the bottom. of the reservoir 83 to the socket 29. The gear I9 is provided at its lower end with an apron 93 and a portedmember 94 is'arranged in the socket 29 to conduct the liquid from the ports 92 to the interior of the apron 93. The lower end of the pinion I8 is provided with an annular skirt 95.

Ports 96 extend longitudinally through the gear 19 to conduct the liquid from the interior of the apron 93 to the interior of the skirt 95. Axial ports 9! extend through the pinion I8 and conduct theliquid from the interior of the skirt 95 to ports 98 in the lower wall of the case section 58. The ports 98 deliver the cooled liquid to the annular space 61 in the port member I3. It will be observed that the ports in the member 94 and the ports 96 and 91 are'spaced varying or increased distances from the axis of rotation of the impeller II and the case I2 and centrifugal force causes the liquid to advance through the series of ports into the space 61. Narrow passages 99 extend tangentially through the port member I3 from the space 67 to the periphery of the member. The passages 99 discharge portions of the cooled liquid into the passages 59 of the rotating impeller II. A tubular normally closed fitting I may be provided on the base ID to facilitate the delivery of liquid to the reservoir 83. In practice the compressor will operate for a prolonged period before required additional liquid. J

In operation, the motor 22 directly drives the impeller II and the impeller rotating within the casing I2 subjects the'fiuid in its passages 59 to centrifugal action. The fluid discharging from the periphery of the impeller II at a high velocity serves to rotate the casing I2. The liquid discharging from the impeller at a high velocity is capable of giving up the same amount of en-.

ergy as that required to accelerate it to this velocity. In the device of the invention the energy represented by the rapidly rotating mass of liquid must be absorbed or utilized in rotating the casing, there being no other way of absorbing this energy. It follows then that where the casing is made to rotate at a slower speed than the impeller, by the differential gearing I4, all of this energy is transmitted back to the driving shaft 36 with no loss of energy other than that represented in the heat dissipated, the friction in the bearings and gearing and the friction loss in the fluid flowing diametrically into and out of the impeller. Thus the casing I2 is made to rotate in the same direction as the impeller I I through the action of the compressing fluid discharging from the impeller.

The differential drive I4 transmits the rotary motion from the casing i2 to the impeller II, so that the energy given up by the liquid in turning the casing I2 assists in rotating the impeller II, and causes the casing to rotate at a slower speed than the impeller. Because of this difierential in the speed of rotation, the passages 50 of the impeller I2 move into and out of receiving communication with the spaced

ports

22 and 23 in the member I3. Thus the passages 59 alternately receive definite charges of liquid and definite charges of the gas and these charges move out through the passages 50 to discharge from the impeller at a greatly increased velocity. The compressing medium or liquid leaving the impeller II under an increased pressure flows back or rearwardly through the passages 74 to the ports I2 and the liquid is thus continuously recirculated through the impeller. This recirculation of the compressing medium is effected with practically no loss of energy, the energy represented by the rotating mass of the discharged compressing medium being transmitted to the driving shaft 36 as described above.

The gas discharging from the outer ends of the passages 50 under an increased pressure is received by the pockets 5I and flows through the

ports

52 and 53 to the chamber 54. The final separation of the gas and liquid takes place in the chamber 54. The compressed gas flows through the ports 56, the shaft 43, and the openat H2.

at their lower ends. The outer pins I I5 may be ing 30 to discharge from the, pipe32. handled or compressedby the device is received from the chamber 24 of the housing, It? andmay be supplied to the housing by the pipe 25. The

gas passes through the ports IT and T6 to the. chamber I4 and enters the upper ends of the ports I3 to be picked up by the rapidly rotating,

impeller II. Where the compressor is provided with the, cooling system described. above a portion of the heated compressing medium or liquid continuously flows through the ports 8'! andfifi.

to discharge into the reservoir 83 where it gives up a portion of its heat.

the ports 96, 91 and 98 to thespace 6'Iand-re-.

enters the active part of the compressor through.

the passages 99. This cooledliquid continuously supplied to the, compressor keeps the temperature of the compressor down;

Figs. 5 and 6 of thedrawings illustrate a form of the inventioneinbodying a simple inexpensive impeller H and a form of structure that iszdesigned to handle a constant flow of liquid to. The structure produce the compressing action. illustrated in Figs. 5 and 6 may be said to comprise, generally, a housin Iii, the impeller, Ii rotatable in the housing Ili a casing IZ rotatable in the housing Iii and enclosing the impeller H a drive It between the casing I2 and the impeller II and fluid handling systems tobe.

later described.

The housing Id may be substantially the samev as the housing II! comprising a base Is andian upper member I8. iii provide achamber Z t in which the casing I2 rotates. A central depression: 2% is provided in the base ES and an upstanding annular wall 21 is provided in the bottom of the depression.

The motor 2% for driving the compressor may close the upper end of the housing member; IS.

The impeller II comprises a hub. 3t andan. enlargement or disc-like part 35* projecting from: ihe hub M cates with the opening 3%. A suitable connection H5 is provided between the motor shaft 36 and the impeller hub 34 whereby the motor 2? directly drivesthe impeller.

The impeller II further includes a series of discs III formed of sheet metal or the like and surroundingthe hub 35 with substantial clearance. and may be of substantially the same diameter as the part 35*. The discs III are dished or pitched and the adjacent discs are pitched in opposite directions. The inner edge portions of the adjacent discs HI abut and are connected The uppermost disc III is spaced from the lower. side of the part 35 The discs III are shaped and related to have annular passages I I3 between their opposing surfaces. H3 extend from the interior of the assembly to the periphery of the impeller and decrease in thickness or capacity as they extend outwardly. Inner and outer rows of pins H4 and H5-serve to connect the several discs HI and serve to attach tliedisc assembly to the impeller part 35*.

The innerpins H4 are tubular and are closed The; gas- The cooled liquid flows. through the ports 92, theport member 94', and.

The base It? and memberv The, shaft 63 is flxediin the opening.

An outlet pipe 32 provided. with. a check valve 33 -communi-' The discs III are preferably of-like size The passagesdirect the liquid to the tubular pins lid.

flange, I26 is adjacent and spaced outwardly.

interior-of the assembly-of discs III.

sages. H3 between the adjacent discs III are flared attheir outer parts to have mouths; I It.

The upper ends of the tubulardisc carrying pins.

H4 are open at the top ofthe impeller part 35*. Thecasing I2 is substantially the same as the above described casing I2 comprising a. main cup-like section 58 closed at its upper end by a plate 5%. The casing I2 encloses the impeller II with clearance and is independent- 1y rotatably supported in1 the housing I A bearing H8 mounts the lower part of the section 8 on the shaft 43 whilea bearing H9 supports theyplate 59*} on the impeller hub 34*.

The drive M is-a differential drive between the casing I2 and the impeller H I l may be the same as: the drive I4 described above. As illustrated; the drive I l includes a gear I8 keyed or fixed to the casing I2 and a largergear lfl fixed to the-impeller shaft AS A pair of connected gears-iiI and 82 is mounted on the stub 80 to rotate as a unit The gear S2 -meshes with the gear, 1% and the gear 8W meshes with. the gear. 18%. The diiferential drive hi is preferably disposed below thecasing [2 within the wall 27 The compressor includes port means or duct means for supplying the compressing liquid and the gas to the impeller Hi and for handling the compressed gas. In the construction-illustrated a pipe I20 delivers the compressing liquid to a port I2I in the wall of the housing member !8 A valve I22l may be provided to govern the flow through the port I2I. the port I2I to an annular recess I2-i in the top of the plate 59 Series of radially spaced ports I25 are provided in the plate 59? to conduct the under side of the plate Bil and is received in an annular groove I21 in the top of the impeller part The-flange I26. is arranged to The from the upper ends of the pins. HA and centrifugal force carries the liquid from. the ports I25 to the upper. ends of the pins I I i. The pins H4 have lateral ports I28 for discharging. into the passages H3. The ports I28 are vertically, spaced and are faced outwardly to discharge the compressing liquidoutwardly in the passages.

The compressing liquid thus delivered to the passages H3 dischargesfrom the mouths IE1 of the passages H3 into the casing. I2. An annular deflector I29 is securedto the lower wall of the case member 58 by rivets or pins I38.

The deflector I23 is turned upwardly at its. in-

ner and outer edges. to have its edge portions in adjacent relation to the lowermost disc I I I. .The

4 supplied to the compressor by the pipe I26 and means is provided for continuously leading the used liquid from the compressor. This means includes an annular'upstanding wall I32 on the" section 58* spacedbetween the hub 34 and the L n itu- The drive A pipe I23 leads from dinal ports I33 extend through the wall I32 and the lower wall of the section 50. The upper ends of the openings I33 are open to the interior of the impeller H at the normal liquid level of the compressor so that the excess liquid runs down the ports A plate I34 is secured to the upper end of the 'wall 21 to direct the liquid from the ports I33 outwardly to the outer portion'of the depression 26 A liquid discharge pipe I35 carries the liquid away from the depression 26 The air or gas to be compressed is admitted to the housing It! by a pipe I36 communicating with the upper portion of the housing chamber 24 The gas is free to flow through the inner ports I25 to the interior of the casing I2 Vertical ports I3I extend through the impeller part 35 and terminate at'a trap-flange I38 adjacent the upper end of the wall I325 The gas is thus admitted to the interior of the impeller -I I and is entrained with the liquid discharging from the ports I28 moving outwardly through the passages II3. The gas is put under pressure by the liquid subjected to centrifugal action in the passages II3 and the compressed gas leaving the mouths II! is caught in an annular groove I40 formed in the impeller part 35 Radial ports I4I extend from the groove I40 to the upper end of the opening 42* to conduct the compressed gas to the upper end of the tubular shaft 43*. The gas flows through the shaft 43 to the opening 30 to discharge through the pipe 32 The operation of the compressor illustrated in Figs. 5 and 6 is similar to the operation of the previously described form of the invention. Assuming that the impeller Il is driven by the motor 22 and that water or other liquid is admitted through the pipe I23 at a suitable rate, the device operates to compress the gas admitted by the pipe I36. As described above, the liquid flows through the ports I25 to enter the upper ends of the tubular pins I4 and discharges from the ports I28. Centrifugal force carries the liquid outwardly through the passages H3. The gas from the chamber 24 flows through the ports I25 and I3! to the interior of the impeller Il to be entrained in the liquid. The liquid moving outwardly through the passages II3 compresses the gas and the compressed gas discharges from the periphery of the impeller II to be received in the groove I40. As described above, the compressed gas flows through the.

ports I4I, the pipe 43 and the opening 30 to the discharge pipe 32 The centrifugal action provides a differential in pressures in the casing I 2 and the liquid under high pressure at the peripheral part of the compression chamber returns through the space I3I to the interior of the impeller II where it re-enters the passages I I3. Thus there is a continuous recycling of the liquid. 7

The fluid discharging from the 'periphery of the impeller Il into the body of liquid rotating with the impeller I I a acts on the casing I 2 to rotate the same. As in the foregoing form of the invention the energy required to increase the peller. This action is the same as in the foregoing form of the invention.

Figure '7 illustrates a form of the invention embodying a hydraulic means ld for producing a differential in the speed of rotation of the impeller and the casing, and a governing means or unloading means X.

In the compressor shown in Figure 7 the hydraulic speed differential means I4 replaces'the gear drive I4, described above. The housing I0 the impeller II the casing I2 the port member I3 and the port and conduit means for handling the liquid and gas are the same as the corresponding elements of the structure shown in Figures 1 to 4 inclusive, except for the differences described below.

The hydraulic means I4 for causing a diflerential in the speed of rotation of the casing 2 and the impeller II includes ports 81 and 89* similar in character to the ports 81 and 89, but much greater in fluid capacity to provide for the return of liquid to the reservoir 83 at a substantial rate. The means I 4 also provides for the delivery of a large volume of liquid from the reservoir 83 to the valve member I3". A cuplike member I50 is secured in the reservoir 83 in overlying relation to a sump I5I formed in the bottom wall of the reservoir. Ports I52 maintain communication between the reservoir 83 and the sump I5I. Similar ports I53 in the bottom of the member I50 put the interior of the 7 member in communication with the sump I5I.

velocity of the liquid as it moves through the The casing I2 has a central depending boss I54, which enters the member I50 with substantial clearance. The boss I54 carries a bearing I55, which assists in rotatably supporting the casing I2 The lower end of the boss I54 has a series of ports I 55 of substantial aggregate fluid capacity for conducting the liquid from the member I50 to the interior of the boss. The boss I54 is hollow or tubular and its upper end communicates with the space 67* in the port member I3 The port member I 3 has a plurality of spaced lateral ports 99*, considerably larger than the above described ports 99, for conducting the cooled liquid from the space 67 to the outer surface of the port member to be picked up by the rotating impeller II The port system, or fluid handling system just described, is designed to handle a large volume of the compressing medium or liquid. This conducting of a large volume of the liquid, as it circulates to and from the reservoir 83 imposes a substantial load or drag on the casing I2 causing the casing to rotate at a slower rate than the impeller II It is to be observed that the differential in the speed of rotation of the impeller II and the casing I2 depends upon the rate of circulation of the liquid from the interior of the casing I2 to the reservoir 83 and back to the reservoir.

The means X serves to regulate or govern the rate of flow of the liquid from the reservoir 83 to the interior of the casing I2 and thus serves to control the differential in the speed of rotation of the casing and the impeller II and the compressing action of the device. The means- X includes a port system in the impeller I I b for handling the compressed gas after the compressor has reached a given or maximum output. This port system is an addition to the

ports

52, 53, 54, 56 and 43 described above, and includesan annular space or trap I58 in the impeller above the upper flange 51. The trap I58 serves to receive the compressed gas thatoverflows from the.

pockets 5| and spills over the upper flange 51. Ports I59 extend inwardly through the impeller II from the trap I58 to longitudinal ports I60 formed in the hub portion of the impeller. A socket ISI is provided in the lower end of the impeller II and the ports I60 communicate with the upper end of the socket.

The means X further includes a plunger I62 movable longitudinally in the, socket IGI. A

spring I63 is arranged against the under-side of.

the plunger I62 to urge the plunger upwardly to a retracted position. A stop, flange IE4 is provided on the shaft 43 to limit the upward movement of the plunger I62. and to prevent the plunger from closing the. lower ends of the ports I66. The lower end of the plunger I62 carries a valve part 355 exposed at the. lower end .of the socket IGI. The valve part I65 is operable to restrict or close the liquidcreturn ports I56when the plunger I62 is moved downwardly.

The operation of the compressor illustrated in Figure 7 is substantially the-samerasin the previously described form of the invention. Under some conditions ,of-use or operation the compressing rate of the device may exceed a given or fixed value, in which case compressed gas overflows the pockets 51 and the upper flange 51 and spills into the space or trap I58. This compressed gas is received by the ports I59 and I60 and acts downwardly against the upper end of the plunger I62. When the pressure of this gas exceeds a given value it overcomes the spring 168 and the plunger I62 moves downwardly. The downward.

movement of the plunger may bring the valve part I65 to a position where it closes or substantially closes the ports I56. Upon-a marked restriction or ayclosing of the ports I56,.the load imposed on the casing I2 by reasonof the circulation of liquid between the casing and the reservoir 83, is relieved or removed and the casing soon rotates at substantially the same speed as the impeller II With the casing I-2 rotating at substantially the samespeed as the impeller I I the compressing action is reduced to a minimum or stops. Thus closing of the ports I55 by the action of the overflow. gas pressure unloads the compressor. When the demand for the compressed gas is resumed or when conditions return to normal the gas pressure against the upper end of the plunger Hi2 lessens because of the leakage of gas from above the plunger and the spring 53 returns the plunger to its normal position where the ports I56are cpenl This allows the circulation of liquid from the casing I2 to the reservoir 83 to be resumed and the load or drag is re-applied to the casing +2 to provide the normal differential in the speed of rotation of the impeller and casing. The compressor illustrated in Figure 7 embodies a simple hydraulic means for producing a differential at the speed of rotation of the impeller and casing and a novel means for unloading or governing the compressor.

The present invention provides a compressor or vacuum pump that is quiet in operation and that operates eificiently with a minimum of power. The compressor utilizes the energy in the fluid discharged from the impeller to drive the surrounding casing which in turn is geared to the impeller so that the otherwise wasted energy is utilized to assist in rotating the impeller.

Having described only typical preferred, forms and applications of my invention, I do not wish to be limited or restricted to the speclfic deta11s hgreinset forth, but wish to. reserve tomys li.

to those skilled in theart or .fall within the-scope of the following claims. 7

Having described my invention, I claim: 7 l. A compressor or vacuum pump of the character described comprising a rotatable impeller having outwardly extending passages in which fluid is subjected to the efiect of centrifugal action, said passages discharging the-fluid from the impeller, means for conducting-liquid and gas to the. inner ends of said passages, means for rotating the impeller, a rotatable case enclosing the impeller and rotated by the fluid discharging from the impeller, a. drive between the case and impeller. whereby the case assists in rotating the impeller, means for conducting the gas from the case, and means for returning theliquidfrom the case to the first namedmeans.

2. Ascompressor or vacuum pump of the character described comprising a rotatable impeller having passagesin which fluid is subjected to the efiect of centrifugal action, said passages discharging the, fluid from the impeller, means for rotating the impeller, a rotatable caseenclosing the impeller and rotatedby thefluid discharging from the impeller, port means rotatable with the casefor supplying fluid to the passagesof the impeller, means for conducting gas to the port means, means for conducting liquid from the case to the port means, and means for conducting away the compressedgas leaving the passages.

3. A compressor or vacuum pump of the character described comprising a rotatable impeller having passages in which fluid. is subjected to .the eflect of centrifugal action, inlet port means for supplying liquid and gas to said passages,

said passages discharging the fluid from the impeller, means for rotatingthe impeller, a rotatable case around the impeller rotated by the fluid discharged from. the impeller, means for conducting away the compressed: gas discharged from. said passages, and a differential. drive between the case and impeller whereby the energy of, the said discharging fluid assists in rotating the impeller.

4. In a machine of the character described, a case supported for rotation. a, centrifugal type impeller rotatable in the case, means for ad'mitting, charges of gas and a, heavier fluid to the impeller to be subjected to the effect of centrifugal action so that the gas is under increased pressure upon leaving the impeller, means for ting charges of gas and a heavier fluid to the impeller to be subjected to the effect of centrifugal action so that .the gas is under increased pressure upon leaving the impeller, means for conducting the compressed gas from the impeller,

the case receiving the fluid leaving the impeller and being rotated by said fluid, means for returning the fluid from thecase to the first named means for re-use, and a drive between the case and impeller whereby the case assists in rotating the impeller.

6. In a machine of the character described, a case supported for rotation, acentrifugaltype impeller rotatable in the case, means rotatable with he. asel pr sch r i o e f gas-and a any variations or modifications that may appear heavier fluid to the impeller so that the gas is compressed by the effect of centrifugal action on the said fluid, means for conducting the compressed gas from the impeller to the exterior of the case, the case being rotated by the said fluid discharged from the impeller, and means producing a differential in the speed of rotation of the case and impellerwhereby the impeller rotates relative to the first named means to receive said charges therefrom.

'7. In a machine of the character described, a case supported for rotation, a centrifugal type impeller rotatable in the case, means rotatable with the case for discharging bodies of gas and a heavier fluid to the impeller so that the gas is compressed by the eflect of centrifugal action on the said fluid, means for conducting the compressed gas from the impeller to the exterior of the case, the case serving to receive the said fluid discharged from the impeller and being rotated by the same, means directing the said fluid from the case to the'first named means for re-delivery to the impeller, and means retarding rotation of the case so that the impeller rotates relative to said first named means to receive said charges.

8. In a machine of the character described, a case supported for rotation, a centrifugal type impeller rotatable in the case, means rotatable with the case for discharging bodies of gas and a heavier fluid to the impeller so that the gas is compressed by the effect of centrifugal action on the said fluid, means for conducting the compressed gas from the impeller to the exterior of the case, the case serving to receive the said fluid discharged from the impeller and being rotated by the same, means directing the said fluid from the case to the first named means for re-delivery to the impeller, and means retarding rotation of the case so that the impeller rotates relative to said first named means to receive said charges, the last named means comprising a differential power transmitting drive between the case and the impeller whereby the said fluid in rotating the case assists in rotating the impeller.

9. In a machine of the character described, a rotatable centrifugal impeller, means supplying liquid and gas to the impeller to be discharged therefrom, a rotatable case around the impeller rotated by the fluid discharged from the impeller means for conducting the compressed gas from the case, and means for conducting liquid from the case.

10. In a machine of the character described, a rotatable centrifugal impeller, means supplying liquid and gas to the impeller to be discharged therefrom, means for rotating the impeller, a rotatable case around the impeller rotated by the fluid discharged from the impeller, a drive between the case and impeller transmitting force from the case to the impeller, means for conducting the compressed gas from the case, and means for returning the liquid from the case to the first named means.

11. In a machine of the character described, a case supported for rotation, a centrifugal type impeller rotatable in the case, means rotatable with the case for discharging bodies of gas and a heavier fluid to the impeller so that the gas .is

compressed by the eflect of centrifugal action on the said fluid, means for conducting the compressed gas from the impeller to the exterior-of the case, the case serving to receive the said fluid discharged from the impeller and being rotated by the same, means directing the said fluid from the case to the first named nieans for re-delive'iy to the impeller, and cooling means withdrawing a stream of said fluid from the said first named means, reducing the temperature of the fluid thus withdrawn and then returning the cooled fluid to the said first named means.

12. In a machine of the character described, a rotatable centrifugal impeller, means for supplying gas and a heavier fluid to the impeller to be discharged therefrom, a rotatable case enclosing the impeller to receive the fluid leaving the impeller and rotated by the fluid put into motion by the impeller, a part rotatable with the case having a passage conducting said heavier fluid from the periphery of the impeller to the said means for redelivery to the impeller and outlet means for conducting away the gas discharged from said passages.

13. A compressor or vacuum pump comprising a rotatable impeller having outwardly directed passages discharging at its periphery and having ports leading inwardly from its periphery, means for rotating the impeller, a case supported for rotation and enclosing the impeller to receive the fluid discharged from said passages and to be rotated by the fluid put into motion by the impeller, a member rotatable with the case and arranged within the impeller, the member having fluid ports adapted to communicate with the said passages, and gas ports adapted to communicate with the passage, means delivering gas to the gas ports, means in the case circulating fluid from the peripheral part of the case to said fluid ports of the member, a diflerential drive between the case and the impeller causing the case to rotate at a slower speed than the impeller whereby said passages pick up alternate charges of fluid and gas from said fluid ports and gas ports, the gas being compressed in said passages and discharged at I the periphery of the impeller where it is received by said inwardly directed ports, and means conducting the compressed gas from the impeller to the exterior of the case.

14. A compressor or vacuum pump comprising a rotatable impeller having outwardly directed passages discharging at its periphery and having ports leading inwardly from its periphery, means for rotating the impeller, a case supported for rotation and. enclosing the impeller to receive the fluid discharged from said passages and to be rotated by the fluid put into motion by the impeller', a member rotatable with the case and ar ranged within the impeller, the member having fluid ports adapted to communicate with the said passages, and gas ports adapted to communicate with the passage, means delivering gas to the gas ports, meansin the case circulating fluid from the peripheral part of the case to said fluid ports of the member, a differential drive between the case and the impeller causing the case to rotate at a slower speed than the impeller whereby said passages pick up alternate charges of fluid and gas from said fluid ports and gas ports, the 'gas being compressed in said passages and discharged at the periphery of the impeller where it is received by said inwardly directed ports, means conducting the compressed gas from said inwardly directed ports, a stationary housing enclosing the case, fluid cooling means in the; housing, and means conducting a stream of thefluid from within the'case to the cooling means and back into the case. .1

15. A compressor or vacuum pump, of the character described comprising a rotatable impeller having passagesiniwhic'h fluid is subjected to the effect of centrifugal action, means supplying gas and a heavier fluid to said passages,said passages discharging the fluid from the impeller, the impeller comprising a plurality of disks connected in spaced relation to define said passages, means for rotating the impeller, a rotatable case enclosing the impeller and rotated by the fluid dis charging from the impeller, outlet means for conducting away the gas discharged from said passages, means for conducting the heavier fluid from the case to the first named means for redelivery to said passages, and a drive between the case and impeller whereby the case assists in rotating the impeller.

16. A compressor or vacuum pump of the character described comprising a rotatable impeller having passages in which the fluid is subjected to the eflect of centrifugal action, said passages discharging the fluid from the impeller, means for rotating the impeller, a rotatable case enclosing the impeller and rotated by the fluid put into motion by the impeller, the impeller having port means for admitting gas and a heavier fluid to its passages, valve controlled means supplying said heavier fluid to the port means, means for conducting the gas to the port means, means in the case circulating the heavier fluid from the periphery of the case to the inner ends of said passages, means discharging the excess heavier fluid from the case, and a drive between the case and impeller whereby the case assists in rotating the impeller.

17. In a machine of the character described, a case supported for rotation, a centrifugal type impeller rotatable in the case, means rotatable with the case for discharging bodies of gas and a heavier fluid to the impeller so that the gas is compressed by the effect of centrifugal action on the said fluid including a member secured to the case and provided with circumferentially spaced ports in its periphery for discharging said heavier fluid into the passages and peripheral ports spaced between the first mentioned ports for discharging the gas into the passages, means for conducting the compressed gas from the impeller to the exterior of the case, the case being rotated by the said fluid discharged from the impeller, and means producing a differential in the speed of rotation of the case and impeller whereby the impeller rotates relative to the flrst named means to receive said charges therefrom.

18. A compressor or vacuum pump comprising a rotatable impeller having outwardly directed passages discharging at its periphery and having ports leading inwardly from its periphery, the ports being enlarged at their outer ends to form pockets for the reception of the compressed gas, means for rotating the impeller, a case supported for rotation and enclosing the impeller to receive the fluid discharged from said passages and to be rotated by the fluid put into motion by the impeller, a member rotatable with the case and arranged within the impeller, the member having fluid ports adapted to communicate with the said passages, and gas ports adapted to communicate with the passage, means delivering gas to the gas ports, means in the case circulating fluid from the peripheral part of the case to said fluid ports of the member, a differential drive between the case and the impeller causing the case to rotate at a slower speed than the impeller whereby said passages pick up alternate charges of fluid and gas by said inwardly directed ports, and means conducting the compressed gas from the impeller to the exterior of the case.

19. A compressor or vacuum pump of the character described comprising a rotatable impeller having passages in which fluid is subjected to the eflect of centrifugal action, said passages discharging the fluid from the impeller, means for rotating the impeller, a rotatable case enclosing the impeller and rotated by the fluid discharging from the impeller, gas inlet means, liquid inlet means receiving liquid from the case, a ported member rotatable with the case receiving the gas and liquid from the inlet means and operating to deliver the same to said passages upon a diflerential in the speed of rotation of the impeller and case, and means retarding the case to causesaid speed diiierential.

20. .A compressor 'or vacuum pump of the character described comprising a rotatable impeller having passages in which fluid is subjected to the effect of centrifugal action and by which the fluid is discharged from the impeller, gas inlet means, means for rotating the impeller, a rotatable case enclosing the impeller and rotated by the fluid discharging from the impeller, a ported member rotatable with the case operable to deliver said gas and a heavier fluid to said passages upon a differential in the speed of rotation of the impeller and case, and means retarding the case to cause said speed difierential, said means including a source of such heavier fluid external of the case, port means in the case conducting the heavier fluid from said source to the ported member to impose a drag on the case and an outlet for said heavier fluid.

21. A compressor or vacuum pump of the character described comprising a rotatable impeller having passages in which fluid is subjected to the effect of centrifugal action and by which the fluid is discharged from the impeller, gas inlet means, means for rotating the impeller, a rotatable case enclosing the impeller and rotated by the fluid discharging from the impeller, a ported member rotatable with the case receiving the gas from said inlet means and operable to deliver the gas and aheavier fluid to said passages upon a differential in the speed of rotation of the impeller and case, and means retarding the case to cause said speed differential including a container for said heavier fluid external of the case, and port means in the case circulating said heavier fluid from the case to the container and from the container to the ported member to impose a load on the case.

22. A compressor or vacuum pump of the character described comprising a rotatable impeller having passages in which fluid is subjected to the eflect of centrifugal action and by which the fluid is discharged from the impeller, gas inlet means, means for rotating the impeller, a rotatable case enclosing the impeller and rotated by the fluid discharging from the impeller, a ported member rotatable with the case receiving the gas from the inlet means and operable to deliver the gas and a heavier fluid to said passages upon a differential in the speed of rotation of the impeller and case, and means retarding the case to cause said speed differential, including a container for said heavier fluid external of the case, port means in the case circulating said heavier fluid from the case to the container and from the container to the ported member to impose a load on the case, and means controlling the rate of said circulation of said heavier fluid to control the rate of action of the compressor.

23. A- compressor orvacuum pump of the character' described comprising a rotatable impeller having passages in which fluid is-subjected to the-effect of "centrifugal action-and by which the fluid is-discharged from the impeller, gas inlet means; means for rotating the impeller, a rotat able case'enclosi ng the impeller and rotated by the fluiddischargingfrom the impeller, aported member rotatable with the 'case receiving the gas fromsaid-inlet means-and operable to-deliver the gasand a heavier fiuid t'o said passages upon a differentialin the speed of rotation of the impellerand case: and meansretarding the case to cause-said speed differential including a-container for said heavier-fluid external of the case, port means-in= the case circulating saidheavier fluid from the case to the container and from the container to the ported memberto impose a load onthecase, and.- means for governing the compressor or pump comprising ava-lvefor controlling said port means; and means for subjectingthe valve to fluidpressure' developed in said passages to operate whensaidpressure reachesa given valua 24. A compressor or*va'cuum pumpiof the=char-"- acte'r described comprising a' rotatableimpeller havingpassages inwhich fluid is subjected to the effect of: centrifugal= action byw-hich the fluid is discharged from the impeller, gas inlet means; means-for rotating the impeller, a rotatablecase enclosing the impeller and'rotated by thefliiid' discharging from the impeller, a ported member'rotatable with'th'e case receiving'the gas from said inlet means and operable to deliver thegas-and a heavier fluid to said-passages upon adifierentialimthe speed of rotation of the impeller and case; and means retarding the case to cause saidspeed'differential including a container for said heavier fluid external of the case, port means in the case circulating said heavier fluid from the case to the container and from thecontainer tothe ported member to impose a load on-the -case; and'means for governing the compressor: or-pump-comprising a valve for con-