US1864640A

US1864640A - Rotary compressor and pump

Info

Publication number: US1864640A
Application number: US428940A
Authority: US
Inventors: William P Dalrymple
Original assignee: CAMERON A WHITSETT
Current assignee: CAMERON A WHITSETT
Priority date: 1930-02-17
Filing date: 1930-02-17
Publication date: 1932-06-28
Anticipated expiration: 1949-06-28

Description

.W. P. DALRYMPLE Filed Feb. 17, 1930 ROTARY COMPRESSOR AND PUMP June 28, 1932.

June 28, 1932. w. P. DALRYMPLE ROTARY COMPRESSOR AND PUMP Filed Feb. 17, I930 2 Sheets- Sheet 2 ZZZZZZZIanl .P DaZrz-ymple Patented June 28, 1932,

UNITED sTATEs PATENT OFFICE- WILLIAM I. DALRYMPLE, OF CHICAGO, ILLINOIS, ASSIGNOR OF ONE-HALF '10 GAMEROfi A. WHI'ISETT, OF CHICAGO, ILINOIS ROTARY comrnnsson Ann PUMP The present invention "relates to rotary compressors or pumps forfhandling either gases or liquids, and servingas a compressor or a pump, depending upon the requirements of the particular use. v

()ne of the principal objects of the invention is to provide an improved construction of rotary pump or the like Characterized by an outer casing, a rotor therein having peripheral working chambers, and a rotating liquid ring in said casing serving as the piston for each of the rotor working chambers. This liquid ring revolves at approximately 7 the same speed as the rotor, and in addition to serving as a piston for the rotor chambers also functions as a sealing medium for sealing the space between each side of the rotor and the adjacent side wall of the casing, thereby enabling therotor to be spaced from the casing, so that there is no'metal to-metal contact between rotating and stationary parts at any point in the construction.-

Those lateral portions of the liquid ringrevolving between the outer sides of the rotor and the casing, and performing the above scaling function, transmit their centrifugal force as an inwardly acting pressure upon the intermediate portion of the liquid ring 7 which revolves in the plane of the rotor chambc'rs, and one of the features of the invention is the provision of displacement surfaces .or members in the casing, wherebythe level of these two outer portions can be increased considerably beyond the level of theintermediate portion at the compression stage ot the cycle for establishing a relatively large pressure differential between these outer por-' tions of the liquid ring and the intermediate portion thereof. Such enables relatively high pumping or compression pressures to be developed in the device. T

Another important object of the invention is to provideimproved valve meansfor the working chambers of the rotor. Such valve meansmay be of a mechanical type or of a liquid type, both embodiments being shown in the present application. In the mechania cal embodiment, one of the features of thein vention resides in properly relating centrifugal forces and valve -move inent; whereby efii Insein'e instances, it may be desira 1e to cool m cient and reliable valve operation is obtained. In the liquid embodiment, the intake to the rotor chambers or the exhaust therefrom, or both, is governed by: the cyclical immersion of intake and outlet ports inrotating rings of liquid revolving with the rotor.

The liquid type of valve means has the advantage of avoiding the objection ofim perfectvalve seating, results in a more quiet operation, and is capableof handling fluids which would be diflicult to handle'with the metallic" valves." In this regard, the present device is particularly adaptable to use as a refrigerant compressor for refrigerating ap paratus, by virtue of the fact that there are no pistons or other pumping parts requiring lubrication, nor are there any other oints which cannot be effectively sealed against leakage of the refrigerant.

Other objects and advantages of the invention will be apparent fromthe following detail description of certain preferred enibodiments thereof. In the accompanying drawings illustratingsuch embodiments:

Figure 1 is a vertical transverse sectional view through a relatively simple form of my invention, utilizing mechanical exhaust valves for the rotor chambers, this 'fi ure corresponding to a section taken on the P am: ofthe line ll of Figure 2; l e p Figure 2 is a vertical axial sectional view of the same, taken approximately on the plane of the line 2-2 of Figure 1';

Figures 3, 4 and 5 are vertical axial sec tional ,VlGWSOf other embodiments.

Referring to Figures 1 and 2, thecasing of the device comprises an intermediate ring or cylindrical portion 321, which is secured to a suitable base 22, as byzthe cap screws 23. The sides ,of this intermediate ring portion are closed by the side or

end walls

25 and 26, which are secured to the cylin-' inner faces-of the

end plates

25, 26 and the edges of theintermediate 'easin portion.

or other suitable pipe connection extends.

for conveying the refrigerant, air or other fluid being handled, into the interior of the casing. For brevity of description, I shall hereinafter refer to this fluid, which is being pumped or compressed in the unit, as the working fluid. Projecting from one of the

end plates

25 or 26 is a boss 38, with which a nipple or other pipe connection 39 communicates for conveying the working fluid from the unit. Formed as a part of the end plate 25 is a bearing boss 41, in which the drive shaft 42 is journalled. This bearing is preferably packed by a suitable gland packing 43 adapted to be taken up by an adjustable packing nut 44 having threaded engagement with the bearing boss 41. The drive shaft 42 extends transversely through the casing and has a reduced portion 42 at its other end extending into a bearing boss 46 projecting from theother end plate 26. A bearing bushing 47 is adjustably mounted in the boss. 46 for receiving the reduced shaft end 42. The end of said bearing boss is sealed-by a cap nut 48 screwing over the boss and compressing a gasket ring 49 against the end of the boss. a

The rotor is designated 52 in its entirety and comprises a hub 53, which is secured to the drive shaft 42 by a key 54. Interposed between one end of the hub 53 and the bearing boss 41 are washers or bearing rings 55, and engaging with the other end of the hub 53is any suitable means for holding the rotor against displacementalong the shaft, such as the two lock nuts 56 screwing over the threaded portion 42 of the drive shaft. A plate member 58 is interposed between these nuts and the end of the hub 53, such plate member being secured to the drive shaft by the key 54 and comprising part of a ball valve cage, as I shall presently describe.

The rotor comprises a relatively narrow web portion 61 extending outwardly from the hub 53, and a relatively wide body portion 62 extending outwardly from this web portion. Projecting outwardly beyond the periphery of the body portion 62, at each side thereof, are side walls or flanges 64. These annular side walls may be in the form of separate plates rigidly secured to the body portion 62,-or they may be in the form of integral extensionsof the'body portion. A plurality ofirelatively small vanes or fins 66project outwardly from. these, side flanges at spaced the periphery of the rotor body portion 62 and extend from side to side across the channel area 68, between the inner sides of the lateral flange portions 64. These baflles or dividing walls may be formed integrally with the rotor body portion or with the side flanges 64, or they may consist of separate plates recessed into the rotor body portion and having tight-fitting engagement against the inner sides of the flange portions 64. The arcuate spaces between such dividing walls 69 constitute working chambers 72, in which the working fluid is compressed. It will be noted that the dividing walls do not extend out to the peripheral edges of the flanges 64, but have their outer edges spaced inwardly considerably from the flange peripheries.

This permits a displacement member to be extended into the channel area 68, in close proximity to the outer edges of the dividing walls 69 and the working chambers 7 2 for securing an efficient pumping displacement of the liquid ring, as I shall presently describe.

Extending inwardly from each pumping chamber 72 is an exhaust passageway 7 3, which is normally closed at its inner end by a ball valve 74 seating in the end of said passageway. These ball valves are disposed in an annular pocket 75 defined within the center of the rotor body portion 62, The balls are held against displacement in one direction by the web portion 61 and in the other direction by the plate 58, suchplate serving as a valve cage and having ribs 7 6 extending from the inner side thereof and serving as spacers between the balls for holding them in proper alignment with their respective discharge passageways 7 3. In the operation of the. device, the balls are normally held pressed outwardly against theinner ends of the passageways 73 under the action of centrifugal force and are unseated from these passageways by the pressure of the fluid being compressed in the working chambers 72. The working fluid, after being discharged past these ball valves'enters the interior of the casing and then passes out through the dishaving the outwardly acting centrifugal 88 thereof is a displacement member 79 in the form of a ring .or segment secured to the cylindrical casing portion 21. This displacement .member acts on the intermediate or inner leg of the liquid ring rotating between the side flanges 64 of the rotor, such displacement member being spaced from the inner sides of the flanges to permit the inward and outward flow of liquid along the sides of said member. Also mounted in the casing on opposite sides of the rotor are

displacement members

81, 81 which act on the outer legs of the liquid ring. These lateral displacement members are spaced slightly from the edges of the vanes 66. Referring to Figure 1, it will be seen that the inner surface of the intermediate displacement member 79 is of a maximum radius at the intake point of the rotor cycle and from this point spirals inwardly through a gradually diminishing radius to the discharge zone of the rotor cycle, at which point such inner surface just clears the outer edges of the dividing walls 69. From this zone or point of small radius, the inner surface of the displacement member then extends outwardly at the shoulder or offset portion 83, to the larger radius at the intake zone of the cycle. The working fluid is introduced into therotor through an inlet port-85 communicating with the fluid inlet connection 36 and opening into't-he channel area of the rotor through the offset angle portion 83.

In the operation of the device, as the rotor 'is brought up to speed, the pumping liquid is whirled outwardly under the action of centrifugal force and assumes approximately the condition or form illustrated in Figures 1 and 2. The revolving liquid ring may be regarded as being divided into three main volumes or quantities, at least during the compression stage of the cycle, consisting of the intermediate volume or leg a" rotating within the channel periphery of the rotor and the two outer volumes or legs y, 3 rotating on the outer sides of the rotor. It will be noted that the intermediate leg 00 has the relation of one leg of a U-tube with respect to each outer leg y. That is to say, by

pressures of the two outer legs 3/ preponderate over the outwardly acting centrifugal pressure of the intermediate leg as, an in- Wardly acting compression .pressurecan be created between the inner end of the leg 02 and the bottoms of the working chambers '"2. Such preponderating' centrifugal pres sure of the two outer legs may be obtained by making each outer leg of greater depth at this point in the cycle so that centrifugal force acting on this greater radius of liquid'wi'll tend to force the intermediate leg 02 to the same balancing radius. These differential radii or levels of the three legs are attained by the displacementmembers in the -.casing.;,

Referring to Figure ,1,'that portion of the casing .at the left-hand'side of the rotor may be regarded as the intake stage of the cycle, and that portion on the right-hand side of the rotor may be regarded as the compression or exhaust stage of the cycle.

At the intake stage or zone, the inner :surface of the intermediate displacement memher 7 9 recedesaway from the rotor so that in this part of the casing, the intermediate liquid leg a is whirled outwardly clear of the dividing walls 69-and working chambers 72. At this intake zone, the two outer displace;

ment members

81, 81 also recede outwardly to lower or diminish the height of the two outer liquid legs 3 3/, thereby assisting in permitting the intermediate liquid leg :1: to be whirled out clear of the dividing walls 69. The inlet port 85 opens into the channel area 68 between the side flanges 64 and the working fluid which is drawn in through this port bubbles through the intermediate leg w of the liquid pumping ring, substantially as indicated in Figure l. The pumping ringeof liquid will, in all instances, be of higher specific gravity than the fluid being. pumped or compressed by the unit and hence such working fluid will pass inwardly through the rotating ring of liquid and will collect in the descending pockets or working chambers 72 at the left-hand side of the rotor, Figure 1. At this time, the ball valves 74 are seated on the inner ends of the fluid passageways 73, serving as check valves between each pumping chamber and the dischargepressure within thecenter of the easing. The working fluid fills each chamber 72 and passageway 73 in the downward rotation thereof, and as each pocket approaches the bottom of the rotor, the approachinglevel of the inner leg as contacts with the outer edge of the dividing wall 69 at the rear ofthe chamber, thereby sealing the working fluid therein. The diminishing radius of the intermediatedisplacement member 79 tends to force the intermediate leg of the liquid ring into the working chambers, thereby compressing the trapped fluid therein.

The decreasing radii of thetwo outer displacement members 81 also coact on the outer legs y to produce the desired differential or unbalance between the intermediate and outer legs for obtaining the compression pressure. The volume of liquid displaced from the channel area 68 by the decreasing radius of the intermediate displacement member 7 9 augments the quantity of liquid available in the outer legs 2 for producing a large differential between the legs during the compressionstage. Attention is also directed to the fact that the pressure at which the working fluid is discharged from the; device is effective on the outer legs 3 during this compression stage'of the cycle. When the pressure in'each working chamber reaches the desired 'efxhaust pressure, the ball valve 74L is forced from its seat and the working fluid is discharged into the central space within the casing, from whence it is conducted to its point of use throughthe outlet connection 39.

It will be seen that by virtue of having the side flangesGl, 64 project outwardly beyond the outer edges of the dividing walls 69 the admission ofthe working fluid can be made to occur directly into the peripheral channel 68 of the rotor through a stationary inlet duct 85 projecting into this channel. The peripheral edges of said

flanges

64, 64 are indicated in dotted lines in Figure 1 and it will be seen that these flanges prevent the working fluid which is being admitted through the port 85 from bubbling across or around the edges of the rotor at the intake 'zone,-the exhaust pressure eflective on the outer legs 3 also aiding in preventing this.

When the inner'leg w passes the offset portion 83 it is thrown outwardly from each chamber by centrifugal and tangential force, thus creating a rarefied condition in that chamber which aids in effecting a quick admission of the working fluid thereto. The admission of the working fluid directly into the peripheral channel of the rotor enables the entire interior of the casing, within the rotating liquidpumping ring, to be used as an exhaust chamber for all the working chambers.

It will be understood that the radius of the rotor and the shape and proportions of the three displacement members 7 9, 81 and 81 may be changed for obtaining any desired dlfi'erential between the inner and outer legs will be understood that at the intake stage,

these lateral displacement members are of lesser depth even than the portions illusused for different pressures.

The use of mercury is typical, permit-ting the attainment of relatively high pressures in a unit of small radius, such pumping liquid also being substantially inert in most instances to chemical reaction with the working fluid being pumped.

In using mercury, the metallic construc tion of the device would, of course, be such as not'to va'malgamate with the mercury. Obviously, water or any of the other liquids of lower or higher specific gravities may be used as the pumping liquid. Liquids of high specific gravities, which might be used, are represented by acetylene tetrabromide, lead chloride, lead bromide and bismuth bromide. In Figures 3 and 4 I have illustrated other embodiments wherein one valve function utilizes a liquid ring which is contained entirely within the rotor.- This valve function may be either for the inlet oroutlet of the working chambers, but is preferably for the outlet discharge from these working chain'- bers, and possesses the advantage of affording a liquid seal whereby the working fluid, discharged from the working chambers, can be conducted from the hollow interior of the rotor to a point outside of the main pump casing without having to pass through a gland packing or other rotating joint such as might be susceptible to leakage.

I Referring to the construction shown in Figure 3, and wherein parts similar to parts of Figures 1 and 2 have been given the same reference numerals with the appendix 9, the rotor has the previously described arrangement of peripheral pumping chambers 72 which are preferably arranged to emerge from the pumping ring of liquid 00, y to have admission occur across the periphery of the rotor, although it will be understood that admission may be arranged to occur in accordanoe with the method employed in the embodiment of Figures 1 and 2. Instead of employing displacement members to cause the pumping ring to exert pumping impulses in the rotor chambers, I have, in this embodiment, shown the rotor 52 as being eccentrically disposed in the housing. Hence, the rotor is caused to dip into the rotating ring of pumping liquid at the near side of the housing, which is preferably the bottom, and in thus dipping into the liquid a certain amount thereof is displaced to establish the prepon derating outer legs 3 3 in the pumping ring. At the upper side of the housing the rotor emerges from the pumping ring for permitting the intake of the working fluid across the periphery of the rotor and into the pumping chambers. That is to say, the quantity of liquid making up the liquid pumping ring is so proportioned with reference to the volumetric displacement of the rotor, the degree of its eccentricity in the housing, etc., that at the intake stage of the cycle the liquid pumping ring separates completely from the peripheral edges of the rotor, so that the working fluid can enter the pumping chambers around such peripheral edges.

It will be seen that the construction shown in Figure 3 has in common with the construction shown in Figures land 2 the admission of the working fluid peripherally to the working chambers, i. e., in each of these embodiments the working fluid is introduced into the working chambers at the periphery of the rotor. The peripheral admission in Figure 3 differs from that of Figures 1 and 2 in that it occurs from the sides of the rotor across the edgesof the channel flanges instead of from an inlet duct extending into the rotor channel. It will also be noted that in the construction shown in Figure 3, the

easing enclosure or area within. the *liquid pumpingring is at admission pressure, whereasin Figures 1 and 2 this area is at exhaust pressure, being sealed off. from the peripheral channel by the side legs; of the liquid pumping ring. In Figure 3 the working fluid is admitted to the interior ofthe housing through the inlet, connection 36 opening into the side thereof. e

The driving shaft 42 is rigidly secured to one of the side plates 64 of the rotor, such being shown as theright-hand plate.

Any suitable couplingmeans, generally indicated at 121, may be employed for connecting this shaft to the plate in driving relation, this coupling means sealing the joint between the shaft and plate to prevent leakage from the interior of the rotor outwardly along the shaft. The left-hand side plate 64 of the rotor has a central opening 122 therein through which liquid is automatically supplied from the main pumping ring a7, y to the interior of the rotor for replenishingthe sealing. ring and inner valve ring, which I shall presently: describe. Extending inwardly from each working chamber 72 is a discharge tube 96 the discharge. end of which is doubled, back to face in: an outward direction. vliev'olving with the rotor, inside thereof, is the valve ring of liquid .2. C0- operating with the discharge end of each tube 96 is a valve cup 124 which is partly immersed inthe valve ring 2'. Each of these valve cups preferably has a washer 125 of rubber or like pliable material in the bottom thereof in'order more effectively to seal the discharge end of the tube, 96 when'the valve cup is pressed in an inward direction against such discharge end. It will be evident that the pressure established in the liquid valve ring 2 by centrifugal force, will normally tend to force the'valve cup in an inward direction against the. discharge end of the tube when the rotor is revolving.

The discharge pressure of the working fluid, which may be relatively high, prevails within the interior of the'rotor, and, this pressure acting on the valve ring 2" also tends to' ring a and in the valve cups go up together and hence variations of speed do not appreciably aflect the valve function. The annular flange portion of each cup is spaced from the outer wall of the tube to permit ready egress of the working fluid when the valve is unseated and any suitable guide stem or like guide means 127 may be provided for retaining-the valve cups in operative alignment with the discharge ends of said tubes. When the working fluid in'each working chamber is placed under pressure in the bottom part of the rotation of the rotor,-.'this pressure forces the valve cup 12 away from the discharge end of the tube 96 in an outward direction in the ring of liquid a, substantially as illustrated of the lower valve cup in Figure 3., The hollow interior of the rotor forms a manifoldarea 129f-into which allof the working'chambers, discharge in this same manner as they revolve down through the bottom of the rotor cycle.

Such 'nside manifold area-is sealed at left-hand side of the rotor by'a disk 131 which is spaced inwardly slightly from the adjacent side plate 64 of the rotor. The periphery of this diskis also spaced slightly from. the drum portion defining the bottoms of the working chambers. A sealing ring of liquidz rotates in the annular'space between the disk 131 and the adj acentside plate 64;, thisring of liquid sealing the interior manifold area 129 from communication with the interior of the housing, outside of the rotor; 1 I

The inner leg of this annular liquid seal is subjected to the discharge pressure prevailing in the manifold area 129 and the outer leg is only subjected to'the admission pressure prevailing in the interior of the housing, and hence the latter leg will have to extend inwardly toward the center of the rotor toa greater distance to balance the pres.- sureleg. If desired, a ring 132 may be dis posed as a spacer betweenthe inner leg of this sealing ring 2'- and. the body of liquid forming the valve controlling ring a. i

The. disk 131 may be arranged for rotatio with the rotor, in which case it would be connectedtherewith bysuitable bridge or spider members, or suchdisk may beheldstation'ary within the rotor, the latter practice being preferable. Said disk is secured to the flanged end of a tube 134 extending out through the side wall of the housing,-the disk-having a centralopening therein communioating with the bore of the tube.v

The working fluid under pressure is dis chargedvfrom the device through this tube 134;. When the disk is to rotate with the -rotor, such tube is rotatably mounted in the 1 bearing 135' which is secured to the side wall of thehousing, and when such disk is to remain stationary thistubeis rigidly secured in said'bearing.v a

When the rotor is started, the sealing and valvecont'rolling rings of liquid 2" and-z are brought to theproper levels and are maintained at these levels through an automatic replenishing and overflow action utilizing a tube 137 which is secured, as by a bracket 138, to the left-hand wall of thehousing. I

The outer inlet end of this tube extends into the ring of pumping liquid and has'its end bent to dispose the opening of the tube the valve controlling ring .2, are both maintained substantially at the same level.

If this level should be too low or recede oecause of insufiicient liquid, the preponderating outer leg of the sealing ring will immediately replenish these inner bodies of liquid, being in turn replenished through the tube 137, and if this inner sealing leg and valve controlling ring should have an excessive amountof liquid producing an objectionably high level, the discharge pressure of the working fluid acting thereon will cause such excess liquid to be forced back into the outer leg of the sealing ring for spilling over through the opening 122 back into the pumping ring.

InFigure 4: the pumping ring of liquid at, 3/ is given its pumping impulses through the action of the displacement members 79 81 although'it will be evident that these pumping impulses may be obtained by disposing the rotor eccentrically in the housing as is shown in Figure 3. The intake occurs transversely across the periphery of the rotor, but, here again, the intake may be arranged to occur in accordance with any of the previously described embodiments. The, discharge tubes 96 extend inwardly towards the center of the rotor to a greater distance than in Figure 3, and have their outlet valve function controlled directly by the valve ring of liquid 2. 7

The ends of the discharge tubes are im mersed only slightly in this valve ring, so that when the working chamber associated with one of the tubes is in its pumping or compression cycle the working fluid can readily blow over or out through the end of the discharge tube and up through the ring of pumping liquid, into the interior of the r0- tor. When such working chamber is moving'through the intake stage of its cycle a portion of the liquid rin'g is sucked into't-he end of the discharge tube, substantially as illustrated at the upper part of Figure 4. The centrifugal force of this liquid leg pro; vents the liquid from being carried over into the working chamber, and the volume of liquid in the ring 2 is such that the relatively small quantity of liquid sucked into'such discharge tubes does not materially lower the level of the valve ring.

The liquid sealingring a is illustrated as being of greater depth and of greater diameter. That is to say, the adjacent wall of the working chambers is extended outwardly beyond said working chambers in the form of an annular plate 139, which is secured to the outer, left-hand rotor plate 64 as by providing both of these plates with laterally extending flanges, and securing the same together over the disk 131. This disk 131 may rotate or may be held stationary. It is preferably held stationary, and has a liquid replenishing or supply tube 142 secured to the upper portion thereof by a bracket 143.

The valve ring of liquid 2 is at a diflerent level than the inner'leg of the sealing ring .2 and the tube 14.2 has its inlet end facing counter to the direction of rotation of the sealing ring so that liquid is continuously supplied through said tube to the valve ring a, the overflow from such latter ring spilling over the wall 132 back into the sealing ring. This sealing ring is continuously replenished from the liquid pumping ring through the tube 137 substantially as described of Figure 3, the overflow from this sealing ring spilling through the opening 122 back into the pumping ring. The manner in which the working fluid is conducted into the housing through the inlet connection 36 is pumped or compressed in the working chambers, and is discharged through the outlet connection 134:,

will be apparent from the preceding descripopens into the housing on one side of the rotor,

and the outlet connection 39 opens into the housing on the other side of the rotor.

One of the side plates or flanges 64 of the rotor is of sufiicient diameter to accommodate the necessary difference of levels on opposite sides thereof for sealing the intake side from the outletside, the pumping ring of liquid also serving as a sealing ring in cooperation with this flange or plate.

I The working fluid is admitted to the working chambers through tubes 145, there being one of these tubes for each chamber extending through the'inner or top wall of the chamber edge of each dividing wall 69 separating the working chambers, so that when the pumping ring has made contact with the two end walls 69 of a particular working chamber for sealing the bottom of the chamber the pumping ring has also contacted with the outer end of the tube 145 so that such tube is sealed against egress of the working fluid. 'It will be evident thatas the: pumping ring surges inwardly into the working chamber and builds up its pressure therein suchpressure merely causes the liquid of the pumping ring to flow inwardly to a greater extent in the tube 145. The centrifugal force of the leg of liquid in-this tube maintains the tube closed w and performs the valve function.

If desired, the outer end ofeach tube 145 may terminate at a shorter radius. so that the device can be designedor the pumping ring proportioned whereby such ring will never separate from contact with the outer edges of the transverse dividing walls 69 but will always remain in sealing engagement with these walls for maintaining a constantliquid seal between adjacent working chambers. In either construction, when the workingchamber revolves into the intake stage of itscycle the pumping ring recedes out of contact with the outer end of the tube 145, thereby opening said tube to the admission of the working fluid through the inner end thereof and into the working chamber.

The discharge occurs; through passageways 96 extending from the working chambers andopening outwardly through the opposite face or side of the rotor. In. this instance. the valve function is shownas being'performed by a continuous ring' member 147 which is mounted on the side of the rotor to overlie the outlet ends of all of these passageways. This annular valve member has its inner peripheral edge seating on an annular shoulder 14-8, and is retained in position by an outer ring 149 which overlies the inner edge of the valve ring member 147, such retaining ring 149 being secured to the rotor by screws or'in, any other suitable manner.

The valve member 147 may have a slight amount of lateral play bet-ween the rotor and the retaining ring 149. Such valve ring 147 preferably consists of a very thin metallic ring, of only a few thousandths of'an inch thickness. Where the workingchambers are moving through the intake stage of their cycle, this ring will beheld pressed tight against the ends of the discharge passageways 96 by the difference of pressures between such chambers and the discharge chamber area to the left of the rotor. Where the working chambers are moving through the pumping or compression stage of their cycle, this ring will flex away from the outlet ends of said passageways under the pressure of the working fluid being discharged through said passageways. Such fiexure will be in the form of a wave motion inthe ring. It will be noted that such form of valve means is not influenced by centrifugal force 1101' variations in the rotor speed. This formof outlet valve means maybe employed with different forms of rotors having difierent intake valve functions. For example, suchoutlet valve, means maybe employed in embodiments wherein the intake of the workingfluidoccurstransversely across the. periphery of the rotor at one side thereof, as illustrated in Figure 4. This also applies to the other embodiments previously described, the inlet valve functions or rotor and the casing, and without having to resort to' movable abutments, rotating metallic pistons, etc. Hence, there are no parts to wear or to require lubrication or replacement, and leakage is practically eliminated.

The avoidance of lubrication and leakage particularly adapt this construction to use as a compressor for handling refrigerant in domestic or commercial refrigerating apparatus; but, it will, of course, be understood that the construction is also adaptable to use as an air or gas compressor, and can also be used for pumping liquids. 'In one" use :as a liquid pump, the rotating liquid pumping ring 00, y, 1 would be ofhigher specific gravity than the liquid being pumped. In another use of the device as a liquid pump, the liquid being circulated through the device could function as its own liquid pumping ring w, y, 'y. In this regard, when used as a refrigerant compressor, some of the refrigerant in the liquid state could beused as the pumping ring, which would be continuously replenished by the entering refrigerant.

Aside from its use as a pump or'compressor, there are numerous features of my construction which can be, adapted to rotary internal combustion engines, and I have phrased some of the appended claims to cover such possible adaptations.

While the general construction which I have disclosed constitutes one of the preferred embodiments of the invention, nevertheless, it willbe understood that such is merely exemplary and that numerous modificationsand rearrangements may be made without departing from the essence and broad scope of the invention. 5

I claim: i

1. In a .device of the class described, the combination of acasing, a rotor therein having two laterally spaced annular flanges projecting therefromto form a peripheral channel in the rotor, an inlet and an outlet for the pumped fluid, means defining working chambers in said channel, separate. working fluid passageways in said rotor communicating witheach of said chambers, a liquid adapted to be revolved within said casing by said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, and a displacement member extending into the peripheral channel between said flanges for causing piston surging of the liquid ring in said channel 2. In a device of the class described, the combination of a casing, a rotor therein having two laterally spaced annular flanges projecting therefrom to form a peripheral channel in the rotor, an inlet and an outlet for the pumped fluid, means defining working chambers in said channel, separate working fluid passageways in said rotor communicating with each of said chambers, a liquid adapted to be revolved within said casing by said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with'said working chambers, said liquid ring in one part of the rotor cycle forming an inner liquid leg within the peripheral channel of said rotor and outer liquid legs on the outer sides of said rotor acting in centrifugal pressure opposition to said inner leg, and displacement means on the outer sides of said rotor for increasing the radial depth of said outer legs relative to the radial depth of the inner leg. 7

3. In a device of the class described, the combination of a casing having an inlet and an outlet for the pumped fluids, a rotor therein having two laterally spaced annular flanges projecting therefrom to form a poripheral channel in the rotor, means defining workin chambers in said channel, separate 1 working fluid passageways in said rotor communicating with each of said chambers, a liquid adapt-ed to be revolved within said casing by said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, said liquid ring in one part of the rotor cycle ,formingan inner liquid leg within the peripheral channel of said rotor and outer liquid legs on the outer sides of said rotor acting in centrifugal pressure opposition to said inner leg, a displacement member relatively to which said rotor revolves and extending into the peripheral channel between said flanges for causng piston surging of the inner leg of said liquid ring, and displace ment means disposed on the outer sldes of said rotor for increasing the radial depths of said outer legs relatively to the radial depth of the inner leg to produce a centrifugal pressure differential between said outer and injecting therefrom to form a peripheral channel in the rotor, means defining working chambers in said channel, separate working fluid passageways in said rotor communicating with each of said chambers, a liquid adapted to be revolved within said casing by said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working'chambers, and a stationary displacement member in said casing having an inner surface of gradually de creasing radius extending into the peripheral channel between said flanges for causing an inward compression surging of the liquid ing with each of said chambers, a liquid adapted to be revolved within said casing by said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, said liquid ring in one part of the rotor cycle forming an inner liquid leg within the pe ripheral channel of said rotor, and also forming two outer liquid legs on the outer sides of said-rotor acting in centrifugal pressure opposition to said inner leg, and stationary displacement surfaces of gradually decreasing radius disposed on the inner and outer sides of the said peripheral channel for creating a centrifugal pressure differential between said outer and inner legs in the compression stage of the rotor cycle.

6. In a device of the class described, the combination of a casing having an inlet and an outlet for the working fluid,a rotor therein having two laterally spaced annular flanges projecting therefrom to form a peripheral channel in the rotor, means defining working chambers in said channel, separate working fluid passageways in said rotor communicating with each of said chambers, a liquid adapted to be revolved within said casing by said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers,

and liquid governed centrifuge-11y acting,

valve means controlling said working fluid passageways.

7. In a device of the class described, the combination of a casing, having an inlet and an outlet for the working fluid, a rotor therein having two laterally spaced annular flanges projecting therefrom to form a peripheral channel in the rotor, means defining working chambers in said channel, separate working fluid passageways in said rotor communicating with each of said chambers, a liquid ton coaction with said working chambers,

and valves normally lhBld closed by the centrifugal force of a liquid ring arranged for controlling said working fluid passageways.

8. In adeviceof the class described, the combination of a casing, a rotor therein havingtwo laterally spaced annular flanges projecting therefrom to form a peripheral channel in the rotor, means defining working chambers in said channel, separate working fluid passageways in said rotor communicating with each of said chambers, a liquid adapted to be revolved within said casing by said rotor-and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, a displacement member extending into the periph-' eral channel betweensaid flanges for causing 7 piston surging of the liquid ring insaid channel, a working fluid inlet port opening into said channel through said displacement memher, and an outlet from said casing for the working fluid.

9. In a device of the class described, the combination of a casing having an inlet and an outlet for the working fluid, a rotor therein having two laterally spaced annular flanges projecting therefrom to form a peripheral channel in the rotor, means defining working chambers in said channel, separate working fluid passageways in said rotor communicating with each of said chambers, aliquid adaptedtobe revolved within said casing by said .rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, liquidsealing means in said rotor controlling the flow of working fluid through said passageways, and means automatically governing the height of said liquid sealing means.

10. In a device of the class described, the combination of a casing having an inlet and an outlet for the working fluid, a rotor therein having two laterally spaced annular flanges projecting therefrom to form a peripheral channel in-the rotor, means defining working chambers in said channel, separate working fluid passageways in said rotor communicating with each of said chambers, a liquid adapted to be revolved within said casing by said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, liquid valve means comprising a rotating ring of liquid in said rotor for controlling the flow of workingfluid through said passageways, and means automatically governing the depth of said latter liquid ring in rotation.

11. In a device of the class described, the combination of a casing having an inlet and an outlet for the working fluid, a rotor therein having two laterally spaced annular flanges projecting therefrom to form a pcripheralchannel in'the rotor, means defining working chambers in said channel,'separate working fluid passageways in said'rotor communicating at one end with each of said chambers, a liquid adapted to be revolved within said casingby said rotor and producing under the action of centrifugal force a liquid ring havingpiston coaction with said working chambers, the other ends of said working fluid passageways rotating in 00- operating relation to a rotating liquid ring, and valve means cooperating with said latter llquid ring for sealing the latter ends of said passageways.

'12. In a device of the class described, the V combination .of a casing having an inlet and an ,outletfor the working fluid, arotor therein having two laterally spaced annular flanges projecting therefrom to form a peripheral channel in the rotor, means defining working chambers .in said channel, separate working fluid passageways in said rotor communicating with each of said chambers, a liquid adapted to be revolved within said casing by said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, a series of rotating discharge ports connecting with said working fluid passageways and cooperating with another rotating liquid ring, and means for displacing liquid from said first liquid ring to replenish the supply of liquid insaid other liquid ring.

13. In a device of the class described, the combination of a casing having an inlet and an outlet for the working fluid, a rotor therein, dividing walls extendin transversely of the periphery of the rotor i or dividing said periphery into a plurality of working chambers,-two laterally spaced annular flanges on said rotor and extending outwardly therefrom beyond said dividing walls to form a pcri-pheral rotor channel in the plane of said working chambers of greater depth than said working chambers, .a liquid adapted to be revolved within said casing and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, and means for controllin the discharge of working fluid from said c ambers comprising a liquid ring revolving'in said rotor.

.14.;1113 device of the class described, the combination of a casing, a rotor therein, means definlinga plurality of working chambers in the'perip'hery of said rotor, working fluid passagewaysfni said rotor communicating with said chambers, a liquid valve ring in said rotor controlling one of said working Lfluid passageways, means for supplying the \working .fiuid to the interior of said casing, "an outlet for the working fluid, a

centrifugal force a liquid ring coacting with said rotor, and means for causing said liquid ring to exert pumping impulses in said working chambers and to recede from said working chambers for permitting the working fluid to enter said chambers peripherally of the rotor from the interior of said 1 casing.

' ing chambers, means for admitting the working fluid into the interior of said casing, means for conducting the exhaust working fluid from the interior of said rotor, and liquid sealing means separating the interior of said casing from the interior of said rotor.

16. In a device of the class described, the combination of a stationary casing, a'rotor therein having a plurality of working chambers formed substantially in the periphery ofsaid rotor, an inlet and an outlet for the working fluid, the sides of said rotor being spaced from the sides of said stationary casing, a liquid adapted to be revolved within said casing approximately at the speed of said rotor and producing under the action of centrifugal force a liquid ring having piston coaction with said working chambers, said liquid ring being adapted to extend into the lateral spaces between the sides of said rotor and the sides of said stationary casing for sealing said rotor, and a coacting liquid sealing ring revolving within said rotor.

17. In a device of the class described, the combination of a casing, a rotor therein, an inlet and an outlet for the working fluid, means defining a working chamber in said rotor, a liquid ring revolving within said casing, exteriorly of said rotor, a second liquid ring revolving inside of said rotor, one of said liquid rings exerting pumping impulses in said working chamber, and a valve passageway leading from said working chamher and cooperating with the other liquid ring.

18. In a device of the class described, the combination of a casing, a rotor therein, an inlet and an outlet forthe pumped fluid means defining a working chamber in said rotor, a liquid ring revolving within said casing exteriorly of said rotor and creating pumping impulses in said working chamber, a valve passageway communicating between said working chamber and the interior of said rotor, a closure member, and a liquid ring revolving inside of said rotor and cooperating with said closure member for casing and producing under the action of creating pumping impulses in said working chamber, and a working fluid passageway in said'rotor havin a port communicating with said working chamber at a point where saidport will be immersed and sealed by said liquid ring substantially in the initiation of the pumping impulse in the working chamber.

20. In a device of the class described, the combination of a casing, a rotor therein, an inlet and an outlet for the working fluid, means defining a plurality of working chambers in said rotor, a liquid ring revolving within said casing and creating pumping impulses in said working chambers, discharge passageways leading from said working chambers and discharging from one side of said rotor, and a relatively thin flexible valve member-carried by the rotor and adapted to close the discharge ends of said passageways, said valve member flexing away from the ends of said passageways when the working fluid is discharged therethrough and being disposed substantially radially of the rotor so as to remain substantially uninfluenced by variations of centrifugal force.

21. In a device of the class described, the combination of a casing having an inlet and an outlet for the working fluid, a rotor in said casing, means defining a plurality of working chambers in said rotor, a liquid ring revolving within said casing and creating pumping impulses in said working chambers, discharge passageways in said rotor leading from said working chambers, and valve means for said discharge passages carried by said rotor and arranged whereby the functioning of said valve means and the pressure required to open said passages remain uninfluenced and substantially constant during any variations of centrifugal force resulting from different rotor speeds.

In witness whereof, I hereunto subscribe my name this 25th day of January, 1930.

WILLIAM P. DALRYMPLE.