US2293268A

US2293268A - Rotary pump

Info

Publication number: US2293268A
Application number: US389521A
Authority: US
Inventors: Quiroz Francisco Angel
Original assignee: Individual
Current assignee: Individual
Priority date: 1941-04-21
Filing date: 1941-04-21
Publication date: 1942-08-18
Anticipated expiration: 1959-08-18

Description

Augyl, 1942. v F. A. QUIROZ v .l 2,293,268 A ROTARY PUMP l Filed April 21, 1941 2 sheets-Sheet' 1' l I l i [IIIA .nllmll I ulllllll lil u l @nl L l. l .d 1 /'lll/I/YIJvmllllnllrllllll d 72 7 i 65 INYENTOR. www.' had mavfx A Aug'. 185 1942. F. A. QulRoz Ronny PUMP Filed April 2'1, 1941 2 Sheets-Sheet. 2

z INVENT OR.

Patented Aug. 1s, 1942 vROTARY PUMP Francisco Angel Quiroz, Newark, N. J. Application April 21, 1941, Serial No. 389,521

9 Claims. (Cl. 103-117) This invention relates to rotary pumps andits 4principal object is to provide an eflicient single screw rotary'pump of simple construction, to pump clear and thin liquids as well as viscous and thick liquids, and liquids which may contain solid and abrasive material and may be corrosive.

Another object is to provide a pump of relatively large capacity andof compact design suit'- ed for operation in a reduced space, particularly in the cylindrical space of the casing of a deep well.

A further object is to provide a pump of the rotary type which is silent in operation, inexpensive to manufacture, easy to vrepair and high- 1y resistant to wear, regardless of the nature of the liquid to be pumped.`

Rotary pumps in use today whether` they are of the screw, gear, or vane type, are suitable only for pumping clean and non-corrosive liquids, mainly viscous oils `and lubricants. 'Ihei' are not suited for pumping. gritty liquids, because of the grinding action that takes-place where the impellers interengage, resulting in rapid Wear, loss of eiciency, and noisy operation. My improved pump is .notseriously affected by abrasive matter in the liquid, because' it operates on such matter with a wiping action,

rather than a crushing action. The impeller of my pump being of elastic composition, 'thin liquids lubricate it as well as viscous liquids.

Other advantages of my invention will become apparent to those skilled in the art, from the following specification wherein I shall first describe an elementary form of pump embodying my invention, .to show its principle of operation, and then describe a form of my pump showing the best mode in which I have contemplated applying that principle.` I

In the drawings- Fig.v 1 is a longitudinal section of the impeller and part of the cylinder of an elementary form of pump embodying my invention;

Fig. 2 is a cross section of an improved form of pump embodying my invention, on the line 2-2 of Fig. 6, only the liner of the cylinder being shown;

Fig. 3 is a longitudinal'sectionof thatpart of the pump shown in Fig.r2, the impeller appearing f in sideelevation and inthe same position as in Fig. 2: v

Fig. 4 is a Across sectionfsmilar to Fig. 29, but with the impeller advanced one-sixteenth of a turn;

40 to as the wider part of the cylinder space.

but with the impeller in the same position as shown in Fig. 4;

Fig. 6 is a longitudinal section of a complete pump of the kind shown in Figs. 2 to '1, the im,-

5 peller. appearing in side elevation, from the opposite side to that shown in Figs. 3 and 5;

Fig. 'I is a cross section on the line 1,-1 of Fig. 6;

Fig. 8 is an elevation of one section of the 10 impeller shown in Fig@ 6, looking at a side face of the section; and

Fig. 9 is a plan view of the impeller section shown in Fig. 8.

In its construction and principle of operation,

my `improved Apump might be described as a modified Archimedean screw, since it employs a single screw impeller operating in a cylinder. .It is distinguished from the Archimedean screw by the fact that its screw impeller is eccentric in the cylinder and has one or more resilient helical vanes which are pressed against the body of the impeller as they traverse that part of the cylinder wall' nearest the impeller axis, thereby completely closing the helical channels formed by i the groove or thread of the impeller, along a line parallel to the axis of the cylinder. Thus, in Fig. 1, which shows an elementary form of my invention, an impeller I, of elastic composition, molded onto a bushing 2, which is keyed at 3 to a shaft 4, ismounted eccentrically in a cylinder 5, so that its helical vanes 6 and 1 are pressed tight against the body of thel impeller at the bottom of the cylinder, which is nearest the axis of the :impeller shaft 4. For convenience of description, the part of the cylinder space between the impeller axis and the bottom ofthe cylinder will be referred to as the narrower part of the cylinder space while that between the impeller axis and the top of the cylinder will be referred The right end of the cylinder 5 is connected `vwith the inlet opening (not shown) of the pump,"w hile the left end is connected with the delivery pipe (not shown).

from the body of the impeller, expand from the axis of the impeller shaftas they move away from the narrower part of the cylinder space, maintaining contact with the cylinder wall at 50 al1 times. The bearings in which the shaft 4 is journalled' and held eccentrically in the cylinder do notappear in the drawing.

Fig. 5 is a longitudinal section similar to Fig; 3, 554 twodistinct helical vanes, convolutions of which The vanes, being of elastic material, and, in their free condition, standing out,

portions 1a and 6b, which is open at the inlet end of the cylinder space and which extends aroundl the far side of the impeller, being dammed in the narrower part of the cylinder space by the compression of the vane portion 1b against the body of the impeller. The direction of rotation of the impeller is indicated by the arrow Ii. As the vane portion 1a approaches the bottom of the cylinder, it is pressed into. the

same position represented by the van'e portion 6a in Fig. 1, thus sealing the inlet end of the helical channel I0. Meanwhile, the dammed end of the helical channel I nearest the delivery end of the pump has progressed from the position 1b to the position 6c, the vane portion 1c having assumed the position of the vane portion 6c shown in Fig. l. Upon further rotation of the impeller, the sealed helical channel l0 progresses toward the left and eventually opens into the space at the delivery end of the cylinder. Further rotation of the impeller conchannel 8 toward the left and eventually the fluid which was contained in this channel is forced into the cylinder space at the delivery end. Two other helical channels, i2 and I3, move leftward simultaneously with the channel i8, conveying their charges of fluid in the same way.

The form of the impeller shown in Fig. 1 leads to practical diiculties, due to the continuity of the vanes, which causes buckling of the vanes as they pass through the narrower part of the cylinder space, with resultant loss of efficiency and hard and irregular action. This diiculty is removed by the construction shown in the other gures of the drawings, which will now be described, referring rst to Figs. 6-9. A cylinder casting 28 is provided with a liner 2| and has an inlet chamber 22 and an outlet chamber 23. An inlet opening 24 is provided with screw threads for connection of a suction pipe, but the whole pump can be immersed in the uid to be pumped and the suction pipe omitted. A delivery opening 25 is provided with threads to receive the` threaded end of a delivery pipe, which is not shown in the drawing. The inlet chamber 22 is closed by the cover plate 26 and the delivery chamber 23 is closed by a cover plate 21, the former being held in place by screws Y tinues the movement of the rear seal of the 2,293,268 Y appear alternately along any line parallel to the being held against shoulder 42 by a nut 43 screwed onto a threaded portion 44 of the shaft. A setscrew 45 holds the nut 44 against loosening. The balls of the thrust bearing are shown at 46. Felt washers 41 and 48 are retained by rings 49 and 5l!l at the extremities of the bearing box. The opposite end 5I of shaft 3| is held in a plain bearing 52 on cover plate 21. The shaft 3| can be driven by any suitable means (not shown) connected to its protruding end 53.

In order to avoid the diiiculties attending an impeller with continuous vanes, the impeller` of the pump shown in Fig. 6 is made up in sections. This has the additional advantage that the molding of the impeller becomes much easier. The detailed form of the sections, in their natural condition, is shownmost clearly in Figs. 8 and 9. An elastic body 60 is cast upon a keyed bushing 6|. Each section has two

elastic ngers

62 and 63, which are molded so that they normally stand out from the body of the section. 'I'he latter has recesses S4 and 35 adapted to receive the

ilngers

62 and 63, when they are pressed against the body of the section. Series of

ngers

62 and 63 of the assembled sections combine tov form helically disposed propulsion means, which have the same function as the vanes 6 and in Fig. l, and which are herein also referred to as vanes. Theoretically the vimpeller can be composed of a large number of sections, but as a practical matter each section should be suiciently vthick to prevent it from buckling and losing its operative position in the cylinder. In the pump shown in Rg. 6, eight sections complete one turn ofv a single vane. Since there are two fingers 32 and 63 on each section, and consequently two vanes on the asmined by a key way 66 in the bushing 6|, into in Fig. 6. The

fingers

62 and 63 have cham-k 28 and the latter by screws 29. An impeller, in-

dicated generally by the reference character 30, is eccentrically mounted in the cylinder 20. The impeller has a shaft 3|, one end of which extends through a packing box 32 on the cover plate 26, to a thrust bearing indicated generally by the reference characterv 33. The thrust bearing is secured in a cup-shaped extension 34 of the cover plate 26,v the outer race 35 of the thrust bearing being pressed against a shoulder 36 of the cup 34 by a ange 31 of a cap 38. The cap 38 is secured to the cup 34 by screws 39. The inner race 40 of the thrust bearing 33 is xed to a reduced portion 4| of the shaft 3|,

which ts a key 61 held in a key way 68 of the shaft 3|) To provide the four diierent angular positions of the sections on the shaft 3|, the bushings 6i are molded into the sections in different angular relations to the ngers 62. When the sections are assembled on the shaft, cor-'- responding index points, such as 69 and 18, ofl successive sections are disposed around the axis of the shaft 3| along two helical lines, as shown fered end faces 1| and 12, which face toward the delivery end of the pump. The end faces 13 and 14 of the body part of the section are Achamiered to match the end faces`1| and 12.

'Ihe sections are packed on the shaft -3| between end plates 15 and 16, the plate 15 bearing against f a shoulder 11 of vthe shaft and the plate 16 being pressed in by a nut 18 screwed onto a threaded portion 13 of the shaft 3|.

'I'he operation of the pump will now be described, with particular reference to Figs. 2 to 5 of the impeller-just after the helical channel 6U has been sealed, by rotation 'of the impeller through 221/2 from the position shown in Fig. 3.

Figs. 2 and 4 show the angular positions of the impeller in Figs. 3 and 5, respectively. Fig. 7

These sections dier only in respect to "shows still another` angular position of the im- '.peller. Let it be assumed that the impeller is starting in the position shown in Fig. 7 and is rotating in clockwise direction, as indicatedby the arrow 82. The finger 88 will move outward as it travels upward along the left wall of the cylin der, passing through the positions shown at 88 in messes the recesses 84 and 65 of the en d sections 68.

Fig. 2, at 84 in Fig. 4, and at 85 in Fig. 7, eventually arriving Vat the position shown at 88 in Fig.

. and by additional fingers continuing in the same helical line around the back side of the impeller shown in Fig. 3. Itisalso Abounded by the dam 81 formed by the contact of the body portion of the first three sections of thempeller with the bottom `part of the cylinder wall, as well as by the fingers 82d, 62e, 62j, and additional fingers of the same helical series, which do not appear in Fig. 3, and', finally, by another dam, similar to the dam 81, at the forward extremity of the channel, which does not appear in Fig. 3. The channel 80 is still open at the inlet end of the cylinder, as indicated at 88. Since'the channel has a length equal to the pitch length, or one full` turn of the helix, plus the width of .the channel .parallel to the impeller axis, this width being equal to one-half the pitch length, the pump cylinder and impeller must have a length at least one and one-half times the pitch length of the helix. As seen in Fig. 2, the finger 63a is being pressed toward the axis of the impeller andis in contact with the cylinder wall along somewhat more than 45. The

fingers

62 and 83 are preferably of arcuate shape, the radius of the arc being slightly greater than the radius of the arc of the recesses 64 and 65 into which they fit. Therefore, .'when a finger is pressed into its recess, it is curved to a smaller arc, and this results in compressing thel material at the inner side 82a and ,expanding the material at the outer side B2b of .the finger. The end 1| of the finger is accordingly shaped so lthat the points 62c and 82d will just meet the points 88 and 68a, allowing for the compression and expansion of the inner and outer sides of the finger. In other wor-ds, the inner side 62a of the-finger is a little longer than it will be when the finger is pressed into the recess 84, while the outer side B2b is a little shorter than it will be when the finger is .pressed into the recess. The length of the fingers may also be slightly exaggerated,` in some cases, to compensate for shortening caused by back pressure of the liquid.

' In Figs. 4 and 5 the impeller has turned one sixteenth of a revolution from the position shown in Figs. 2 and 3 and the gap at 88 has been substantially closed up by the movement of the tip of finger 83a downto the dam line 81. The finger 63a is being pressed closer to the body of the impeller and the recess at 88 is being closed up. As the rotation vif the impeller continues, the chamfered end faces 'l2 ofthe fingers 83 move down progressively to the dam line 81 and thus the rear end of the helical channel`88 travels toward the right, forcing the `fluid in thatV direction. ,

Y Arcuate ports

88 and 8| are provided in the from thebody of the impeller, after passing said 'These portssaiford passage for the liquid directly to and from` the recessesunder the fingers. I have shown a `pump adapted to be mounted ona foundation 85 by a pedestal 96 and having inlet and outlet openings directed transversely to the longitudinal axis of the pump, but it will be` evident that by slight modification the pump can be adapted to fit into the inner space of a wall casing and utilize that space most efficiently.

I am aware that single screw rotary pumps are known comprising an eccentric impeller having radially movable non-elastic vanes.` These have the disadvantage that such vanes cannot conform to the cylindrical wall surface throughout their rotation, due to the eccentricity of the -impeller 'in the cylinder. Serious leakage is the result.` The elastic vanes which characterize my invention adapt themselves to the cylinder wall at all times and maintain a close seal.

I claim: t

1. In a pump, an impeller comprising a generally cylindrical body and resilient, helically disposed propulsion means resiliently joined to said cylindrical body and normally standing out therefrom, but adapted to be pressed flush with the surface of the cylindrical body of the impe1ler; a cylinder in which said impeller is eccentrically, 'rotatably mounted, with the body of the impeller in contact with a band of the cylinder Wall parallel to the cylinder axis, whereby said propulsion means is pressed flush with the cylindrical surface of the body of the impeller, in passing said band of the cylinder wall as the impeller rotates, forming a dam parallel to the cylinder axis, at one side `of the impeller; saidpropulsion means being adapted to move out band of the cylinder wall, to form a helically disposed vane, the outermost surface of which re mains in contact with the cylinder wall throughout the rotation of the impeller to maintain an uninterrupted helical seal against the cylinder wall.

2. A pump as described in claim 1, wherein said propulsion means is composed of a plurality of individually movable ngers having side faces in mutual contact in planes perpendicular to the impeller axis.

3. A pump as described in claim 1, wherein said propulsion means is composed of a plurality of individually movable fingers having side faces in mutual contact in planes perpendicular to the impeller axis, each finger being -joined to the body of the impeller so that its outer end leads itsK juncture with the body of the impeller as the latter rotates.

endplates 15 and I8 opposite the inner part of 75 4. A pump as described in claim 1, wherein said impeller is composed of sections having fingers which form said propulsion means, said sections and their fingers having flat side faces in mutual contact in planes perpendicular to the impeller axis.

5. A pump'as described in claim 1, wherein said impeller is composed of a shaft and a plurality of sections mounted on said shaft, said sections having fingers which form said propulsion means,

said sections and their fingers having iiat side faces in mutual contact in planes perpendicular to the axis of said shaft, said sections having recesses for their fingers to t into when compressed toward the axis of the impeller. and end plates between which said sectionsl are clamped on said shaft, said end plates having openings opposite the recesses of the end sections.

7. A pump as described in claim 1, wherein said impeiler is composed of sections having fingers which form said propulsion means, said sections and their ngers having fiat side faces in mutual contact in planes perpendicular to the impeiler axis, said sections having recesses for their ngers to fit into when compressed toward the axis and their fingers having at side faces in mutual contact in planes perpendicular to the impelier axis, said fingers having chamfered ends facin toward the delivery'end of the pump.

9. A pump as described in claim i, wherein said impeller is composed of sections having fingers which form said propulsion means, said sections and their lingers having fiat side faces in mutual contact in planes perpendicular to the impeller axis, said sections having recesses for their ngers to nt into when compressed toward the axis of the Aimpeller, said fingers and recesses being of arcuate shape and the radius of the arc of said ngers being greater than the radius of the arc of said recesses, the ends of said fingers being shaped to allow for a contraction of the inner part. and an expansion of the outer part, of each finger as it moves into its recess.

FRANCISCO ANGEL QUIROZ.