US1839485A

US1839485A - Pump

Info

Publication number: US1839485A
Application number: US370589A
Authority: US
Inventors: Willard E King
Original assignee: Individual
Current assignee: Individual
Priority date: 1929-06-13
Filing date: 1929-06-13
Publication date: 1932-01-05
Anticipated expiration: 1949-01-05

Description

Jan. 5, 1932. w. E. KING 1,839,485

PUMP

Filed June 15, 1929 a Sheets-Sheet 1 Infant w. E. KQINGY 1,839,485

PUMP

Filed June-l3, 1929 s Sheets- Sheet 3 Jan. 5, 1932.

z ,W fl hw. u w 5 W/ V 3 E I. r I fl m a Patented Jan. 5, 1932 UNITED STATES WILLARD E. KING, OF DOWNERS GROVE, ILLINOIS rum Application filed June 13,

My invention relates to pumps of the type involving a rotary piston or impeller arranged, preferably, eccentrically in a cylindrical chamber, to which the liquid, lubricating oil, for example, is drawn, and from which it isexpelled by action of the impeller. One of the objects of the invention is to provide certain improvements in a pump of this type whereby the pressure of the outgoing fluid may be increased without increasing the velocity of the impeller.

Another object is to provide means whereby the tendency of the pump to whip the liquid, especially in the case of a lubricating oil, to a froth, thereby lessening or stopping entirely the flow of the oil, is counter-acted and the operation of the pump at high efliciencyds assured. I Further objects of the invention areto provide certain, novel and improved constructions, devices and arrangements for a pump of this type which will obviate the necessity of using packing in connection with the moving parts; which will reduce to alminimum end thrusts, that is, pressure along the axis of therotor element; and which will permit the impeller parts to yield, in case. of a stoppage in the pressure line, while the rotor continues to turn. Other incidental objects will be referred to in the following description of the preferred embodiment of the inventiondisclosed in the drawings. 7

Referring to the drawings: I Fig. 1 is an end view of the pump with the end or cover plate removed to show the working parts of the pump. 1

- Fig. 2 is a longitudinal sectional view on .line 2 -2 of Fig. 1, but showing the cover plateinplace.

. Fig. 3 is a cross-sectional view of the pump casing taken on a plane parallel to the plane of Fig.1, showing a part of the rotor.

Fig. 4 is a sectional view on line 44 of Fig. 1, the rotor being omitted.

1929. Serial No. 370,589.

Fig. 5 is a fragmentary sectional view on line 55 of Fig. 1.-

i Fig. 6 is a view in perspective of the rotor. Fig. 7 is a similar view of the reciprocating piston or impeller.

Fig. 8 is a similar view of one of the sealing lugs for the reciprocating piston.

Fig. 9 is a viewsimilar to Fig. 1, but show ingqthe moving parts in positions different from those of Fig. 1, and

Fig. 10 is a sectional view, but with the cover plate in place, on line 1010 of Fig. 9.

In the pumps of the type referred to, which, when the rotary impeller is not provided with blades, are sometimes designated cam type pumps, the rotation of the eccentrioally placed piston or impeller creates suction and pressure spaces in the pump chamber, one of which increases as the other diminishes; the

oil or other liquid being drawn into the space 5 of increasing volume, which is then a suction space, andis swept out of this space, by the turning of the impeller, as the space dimin ishes from maximum to minimum volume.

In a pump operating on this principlethe pressure created depends upon the velocity with which the rotor sweeps the liquid through the diminishing pressure space and out through the discharge outlet. If, however, the impeller is given a very high velocity, oil or a liquid of that character is likely to be whipped'to a froth, with the result that the pump ceases functioning.

According to my invention," the pump is.

- provided, inaddition to the rotary impeller,

with a reciprocating impeller or piston which creates a pressure 1n a secondary pressure chamber, so as to force liquid from said secondary chamber into the main pump chamber on the pressure side of the rotary impeller, thereby accomplishing two functions :the increase of fluid pressure at the eduction port of the pump and the'injection into the oil body subject to the whippingor whirling action of the rotary impeller, of a body of whipping action, so that if therebe any tendency of the liquid body to be frothed by action of the rotary impeller, this tendency is counter-acted and the pump kept filled with 'suificient liquid at the density necessary to insure the proper and eflicient operation of the pump.

This principle of operation could be embodied, it is conceived, in a variety of difl'en ent mechanical forms. In thepreferred embodiment of the invention illustrated in the drawings hereto appended, the reciprocating impeller is carried by the rotary impeller and is reciprocated, due to the eccentricity of the rotary impeller with respect to the chamher in which it operates, by contact with the circumferential wall of said chamber and; the pump casing is provided with an inner chamber, which will be referred to as, a sec{ spaces by a web on the shaft, of the rotor, the

term rotor being intended to designate the rotary structure or elementof the pumpas a whole. The reciprocating impeller draws oil from each of the spaces of the secondary chamber, in alternatlon while such space' is filling, and then forces it back into the said '1 I spaces while the space is cut ofi from the inlet, creating a pressure which, when said s ace is ported to the main pump chamber rives a stream of oil into the whirling stream of oil under compression by the rotary impeller, thereby accomplishing the two functions above referred to. In the particular arrangement shown .in the drawings, the-reciprocating "impeller also creates a direct pressure, bydisplacement, against .the body of oil onlthe compression side of the rotary impeller. That is, the reciprocating impeller works in the main pump chamber :and is 'timed to supplement the displacement effected by the rotary impeller, thereby increasing the pressure" of the outgoing fluid stream. In thesame way, in an inverse sense, the rec1procat1ng nnpe ler increases the sucr tion produced, on its suction side, by the rotary impeller.-

- It is realized that the principle of the inventlon might be embodied. in mechanical constructions quite different from that shown ing box 15 on the end'wall 16 of the casing 10; a circular web;17 which lies against the inner wall of the housing; a partition web 18 peller 19 is eccentrically placed in the main pump chamber 11; a indicating in Fig. 1 the center of the chamber and b, the axis of the rotor. I

Arranged in the slideway 20 of the rotary impeller 19 is a reciprocating impeller 24 (Fig. 7) recessed at 25 to extend over the cross web 21 of the rotary impeller and with its upper surface 26 flush with the upper surfaces of the end members 27 27 of the rotary impeller. The recess 25 is considerabl g wider thanthe width or thickness of the we ondary pressure chamber, divided into two 21}, permitting lengthwise movement of the notches 28 in opposite ends for sealing blocks 29*; 29",whic' h.are' pressed outwardly against the circumferential wall 30 of the side Wall of thecasing 10so as lead to the secondary pressure or pump chamber 12. The wall of the casing is formed at this point with a groove or passage 36, leading also from the inlet 35 to the main pump chamberll. Diametrically opposite the passage .36 also in the casing wall is another groove or a port'37 forming a by-

pass connecting chambers

11 and 12. An outlet nipple 38 is tapped into the side wall of the casing so as to communicate with the main pump chamber 11. The circumferential wall of chamber 11 is preferably 'rooved or cut away adjacent outlet 38, as indicated at 39. The outlet nipple 38 is preferably of smaller diameter than the inlet nipple 35. 0,pe1'a'tz'on.It will be assumed that the 2 and 3, and is moving in a clockwise direction, as indicated by the arrow, Fig. 1. This movement of the rotor has caused the oil to be drawn from inlet nipple 35 through port 36 into the space 11 on the suction side of the rotary impeller. This continues until port 36 is closed by the sealing block 29 the space 11 becoming gradually larger and larger, until it reaches its maximum size, when the rotor is about in the position shown in Figs. 9 and 10. The liquid in the main pump chamber 11 which is in advance of the sealing blocl r29 is being swept around toward the eduction .port 38 of the pump ma in pump chamber bycoiled springs 31 arrang'ed in sunken spring'seats 32 in the rotor is in the position shown in Figs. 1,. 1n the drawings and referred. to in the'above 1 brief summary. Therefore I wish to be uni derstood asQintending'to cover by patent all' modifications and structural variations of the through a pressure space 11 whichis gradually diminished and disappears, substantially, when the rotor reaches the position of Figs. 9 and 10. The spaces 12*, 12 are filled with oil replenished as they pass the inlet duct 35 through operation of the reciprocating impeller 24, as will be described.

Referring again to Figs. 1, 2 and 3, the reciprocating impeller 24 is shown in one extreme position providing a space 25 constituting an auxiliary pumping chamber in the slide way 20 of maximum width within the impeller and on one side of the cross web 2i and providing only a small cushioning space 25 on the other side of the web .21 in the slideway 20. The space 25 has been filled with oil from space 12 through port 23, by the suction produced by the previous movement of impeller 24. As the rotary impeller rotates from the position shown in Fig. 1, toward the position shown in Fig. 9, the reciprocating impeller 24 is moved to the right (Fig. 2) to compress the oil'in space 25. Back pressure on the inlet duct 35 is cut off byweb 18 passing this duct; and, as soon as this web opens duct 37, the oil theretofore compressed by pressure through port 23 from space 25 in the space 12 is forced up through port 37 into the space 11 on the pressure side of the rotary impeller. In Figs. 9 and 10, the reciprocating impeller 24 is shown in an intermediate position. The impeller is moving to the left (Fig. 10) and oil is flowing from-the space in the secondary chamber 12 on one side of web 18 into the auxiliary pumping space 25 in the reciprocating impeller. The oil in space 25 is being forced into the s ace in the secondary chamber 12 on the other side of web 18 to create a pressure in said space which will be relieved when this space is opened to the by-pass duct 37. With the rotor in the position shown in Figs. 9 and 10, .both

passages

36 and 37 are covered. The dividing web in chamber 12 is in the position shown in dotted lines (Fig. 3). r

In case of a stoppagein the discharge line connected with nipple 38, the sealing blocks 29, 29 will yield against their springs, some clearance existing between the blocks and reciprocating impeller at all positions of the impeller. Thus the pump will not be called upon to carry a load which might endanger it and, moreover, the maximum pressure which the pump is capable of developing can be regulated by providing springs 31 of such stifiness as may be required.

The function of the circular web .17 is to relieve the cover plate 33 of end thrust by .the rotor since this web 17 receives the downward thrust'and is like the rotor rigidly fixed on'the shaft. The moving parts of the pump require no packing. The liquid leak- 65 ing back over the upper face of the rotor and impeller under the cover 33 acts as a packing and also as a cushioning means.

It will be observed that the reciprocating on the pressure .side of the pump; and it also acts, by displacement, to exert of itself a direct pressure upon the liquid being expelled from the main pump chamber. That is, as the space 11 (referring to Fig. 1) is diminished by the rotation of the rotary impeller, it is still further diminished by the straight line movement of the reciprocating impeller, the two impellers acting together to produce a very rapid displacement of the liquid on the pressure side of the pump. The two. impellers operate in just the reverse manner to increase the suction of the pump by producing a rapid increase in the size of the space on the suction side of the rotor.

The oil packing between the rotor structure and the casing and its cover plate results from the fact that the leakage streams of oil from the two impellers are opposed one to another, that is, the leakage up from the auxiliary pumping chamber in slideway 2O meets the leakage from the main pumpchamber flowing back over the upper faces of members 27 on the rotor,to thus provide a liquid seal and cushion.

I claim:

1. In a pump, the combination of a casing providing a main pump chamber and a secondary chamber; a rotor in said chambers comprising a shaft, a web extending diamet rically across the secondary chamber and an impeller head eccentrically arranged in said main chamber and formed with a slide way, with a cross web and with ports on opposite sides of the cross web connecting the slideway with the secondary chamber; a combined reciprocating impeller and valve in said slide way and extending across said cross web; said casing being formed with an inlet port therethrough communicating with the main and secondary chambers, a by-pass port between the secondary chamber and the main-chamber and an outletport through the casing communicating with the main chamber.

2. In a pump, the combination of a casing impeller head eccentrically arranged in said main clfamber, said impeller head being formed with a slide way, a cross web andports on opposite sidesof the cross web connecting the slide-way with the secondary chamber; and a reciprocating impeller and ,Valve in said slide way extending across said cross web; said casing being formed with an inlet port leading to the secondary chamber,

chamber concentric therewith and an impeller head eccentrically arranged in said main chamber, said impeller head being formed with a slide way, a cross web therein and ports on opposite sides of the cross web connecting the slide-way with the secondary chamber; and a reciprocating impeller and valve in said slide way and extending across said cross web; said casing being formed with an inlet port leading to the secondary chamber, a passage from said port to the main chamber, a by-pass from the secondary chamber to the main chamber and an outlet ort from the main chamber adjacent said y-pass whereby the total discharge pressure is increased and the said circular web receives the axial thrust of the pump to provide substantial axial balance for the rotor.

4. In a pump, the combination of a casing providing a main pump chamber and a secondary chamber; a rotor in said chambers comprising a shaft, a web extending diametrically across the secondary chamber and an impeller head eccentrically arranged in, said main chamber, said impeller head being formed with a slide way, a cross web therein and ports on opposite sides of the cross web connecting the slideway with the secondary chamber; and a reciprocating impeller and valve in said slide way and extending across said cross web operated by contact with the circumferential wall of the main chamber; said casing being formed with an inlet port communlcating with the main and secondary chambers, a bypass port between the secondary chamber and the main chamber and an outlet port through the casing communicating with the main chamber.

5. In a pump, the combination of a casing providing a main pump chamber and a secondary chamber; a rotorkin said chambers comprising a shaft, a web extending diametrically across the secondary chamber and an impeller head eccentricallv arranged in said main chamber, said impeller headbeing formed with a slide way, a cross web therein in said slide way and "extending across said ber and an outlet port through the casing communicating with the main chamber.

6. In a pump, the combination of a casing providing a main pump chamber and a secondary chamber; a rotor comprising an operating shaft, a web extending diametrically across the secondary chamber, a circular web 'at the inner end of the secondary chamber,

and an impeller head on said shaft eccentrically arranged in said main chamber said impeller head being formed with a slide way, a cross web therein and apertures on opposite sides of the cross web connecting the slideway with the secondary chamber; and a reciprocating impeller and valve in said slide way and extending across said cross web 'operated by contact with the circumferential wall of the main chamber; sealing lugs movable at the ends of said reciprocating impeller; and an end cover for the casing said casing being formed with an inlet port communicating with the main and; secondary chambers, a by-pass port between the secondary chamber and main chamber and an outlet port from the main chamber, said circular web serving to relieve axial thrust of the rotor against the end walls of the casing.

7. In a pump, a casing containing a main pump chamber and a secondary chamber, a rotor mounted in the chambers and comprising a web dividing the secondary chamber into high and low pressure chambers, and a head eccentrically positioned in the main pump chamber, a slide carried'by the head and functioning as a rotary impeller in the main pump chamber andas a reciprocating impeller for alternately applying pressure to the liquid in the two secondary pressure chambers, a liquid inlet communicating with the main and secondary chambers, a discharge outlet leading from the main chamber, and a discharge passage leading from the secondary to the main chamber so positioned that the reciprocating impeller 'will force liquid from the secondary chamber into the main pump chamber'on the pressure side of the rotary impeller after the impeller approaches the outlet for the discharge of liquid from the main chamber. i

8. In a pump, a casing containing a main pump chamber and a secondary chamber, a rotary head positioned eccentrically in the main pump chamber, a slide carried by the head and functioning as a rotary impeller in the main pump chamber and as a reciprocatingimpeller for applying pressure to the liquid in the secondary chamber, a liquid inlet communicating with the main and secondary chambers, a discharge outlet leading from the main chamber, and a discharge passage leading from the secondary chamber to the main chamber and so positioned that the 5 reciprocating impeller will force liquid from the pressure chamber into the main pump v chamber on the pressure side of the rotary impeller at a point adjacent the discharge outlet, whereby the total discharge pressure is increased and leakage from the secondary chamber opposes leakage from the main chamber to provide a fluid seal for the pump.

\ WILLARD E. KING.