US2319856A - Rotary pump - Google Patents

Description

E. FOWLER ROTARY PUMP Filed Dec. 1, 1939 Milly 25. 1943.

3 Sheets-Sheet l n YJ r N A H .41 1I|Jb|-l|| lll.A Il ---d N om D NN N wlL v 1NVENTR ELBRT FowLER BY RNEYg.

May -25, 1943.

E. FowLER ROTARY PUMP filed Dec. 1, 1959 ssheets-sheet 2 ELBERT FowLl-:R

E.` FowL'ER ROTARY PUMP May 25, 1943.

Filed Dec. l, 1959 3 Sheets-Sheet 3 i 4nwENr-ok Y ELBERT FowLER @MM-L,

ATTORNEYS Patented May 25, 1943 lUNITED `STATES PATENT OFFICE ROTARY PUMP Elbert Fowler, East Cleveland, Ohio,- assi'gnor of .one-half to Belen Eaton Brennan, Cleveland,

Ohio

Application December 1, 1939, Serial No. 307,101 s' claims. (ci. los-121i) This invention relates, as indicated, to rotary pumps and the like, it being apparent from the following description that the principles ofthis invention are in general applicable also to motors, meters and similar devices.

Rotary pumps have long been employed for a variety of uses among which the' pumping of fuel in the feed line of internal combustion engineshas become one ofthe most important. Such pumps are small and compact, requiring no valving means, have relatively few moving parts and may be operated at very high speeds. In the past, however, various operating dlillculties have been encountered. among which may be mentioned the alternative properties of either pulsating delivery or mechanical shock to the vanes of the pump, excessive wear of the vanes due tofcentrifugal force which causes rubbing between the extremities of tendency to cause overheating and vapor lock when handling volatile liquids.

It is an object of the present invention to provide a rotary pump suitable for pumping fuels to internal combustion engines. for example, and

, which will be substantially free fromfthe above enumerated disadvantages.

Another object of this invention is to provide a Y' rotary pump which may be automatically adjustable as to discharge sure obtained.

' Other objects of this invention will appear as depending on the line pres- Ithe description proceeds To the accomplishment of the foregoing and related ends, said invention. then, consists of the means `hereinafter fully described and Particularly pointed out in the claims.

'Ihe annexed drawings andthe following de-- scription set forth in detail certain mechanism embodying the invention, such disclosed means constituting. however. but one of various mel chanical forms in which the principle of the invention may be used.

In said annexed drawings: Fig. l is an. enlarged fragmentary view in cross section along the line i-l of Fig. 3;

Fig. 2 is a further fragmentary cross sectional i view of the device indicated in Dart in Fig. l, taken along the line 2-2 of Fig. 3;

F18. 3 is a side elevational view of the device of this invention;

' Fig. 4 is a view in cross section taken along the line4-4 on Fig. l; Y

Fig. 5 is a view taken along the line 5 5 on Fig. i in the same plane as line 4-4 .l Fig. 6 is a view taken along the 6*-8 on Fig. 1 with the casing removed, showing the inlet and outlet ports; f

Iiig. 7 shows one of said ports in section along the line 1- 1 on Fig. 8;

Fig. 8 is a lview in cross section along the line B I on Fig. 3 and line l-I onFig.7; and

Fig. 9 is a view in cross section of one form of automatic discharge regulator designed to operate in conjunction with the pump of this invention.

Referring now more specifically to the above figures and especially Figs. 1 to 8, one preferred embodiment of the present invention will be de' scribed below. As best shown in Figs. l, 2 and 3, the outer casing of the pump proper consists of two tightly fitting members I and 2 held in close engagement by bolts '3. Journalled in one end of casing member i is the drive shaft 4 to the inner end of which is keyed floating member l in turn keyed to shaft l which is iournalled in bushing 'l inmember I and bushing l in-member 2. :in this manner a lost motion connection on the order of a universal Joint is provided 'so that unequal wearing of the bearings will not result from any slight misalignment with the driving means.` A coll spring I serves to hold member l tightly seated on bushing l to 4reduce any leakage past such bushing'of the liquid being pumped and likewise' keeps shaft 4 tightly seated on thrust bush- A channel Il in casing member i leadsing Il. todrainage orince I! adapted to be closed by a screw plum By this means the casing may be drained of any liquid which may seep'past said member l.

Integral with shaft l is l substantially hemispherical shell I! in which the rotor i4 of the pump is secured. The manner of assembling /ard inserting said' rotor and associate parts /is as follows. Said rotor comprises a cored hemisphere formed in two halves to permit assembly about the flaring skirt il of the non-rotating cam carrying member or statorl II. Said rotor is furthermore slotted to receive a plurality of blades or vanes il smiled t0 be held between Said skirt I5 and the cam surface il when in position for operation.

but in the non-rotating position by ball bearings which engage grooves 2| in the upper portion of said member and engage similar grooves in the lower surfaces of internal bosses 22 on casing member 2 which may nowbe bolted in place. A certain degree of Variable inclination of member I6 is therefore possible for reasons explained below.

As viewed in Fig. 1, the cam face is shown in section midway in the pumping zone and midway in the sealing zone between the intake and discharge ports. .Intake port 23 and discharge port 24 (see Fig. 5) are located in the axially curved portions of said cam face I8. Between said ports are the so-called at cam surfaces 25 and 26 of the pumping zone and sealing zone respectively, where the vanes neither recede nor advance from the rotor. It is obvious from the above description that the flow of liquid may be reversed simply by reversing the direction of rotation of said rotor.

As best illustrated in Figs. 6, 7 and 8, port 23 communicates with outer port 21 and port 24 with outer port 28 in the upper surface of meme i' bei" I6. aOn eithenside of. said outer. ports are flanges 29 parallel to grooves 2|, said flanges making a sliding t with coupling members 30 and 3| (see Fig. 3). A leak-proof seal may be obtained by means of packing 32 against which said coupling members are tightly held by screws 33 bearing on strips of bearing metal 34. The engaging surfaces of the holding ring I9 and member I6 are spherical in contour to allow universal movement of the member I6 relative to the ring I9. The ball bearings 20 and associated grooves` prevent relative rotational movement between these parts while permitting a relative rocking movement in the plane of Fig. 1. Thisrocking movement is likewise permitted by the sliding t with the coupling members 30 and 3|. It will be obvious from the above that the flow of liquid through the pump maybe regulated As viewed in Fig. '1, the cam faces I8 are positioned y by varying the inclination'of member. I6.

for maximum discharge. By inclining said stator, member I6, the degree of extension of the blades I1 in the pumping zone' may be decreased and the degree of extension in the sealing zone in- I creased. When the extension of the blades from the rotor is equal in'both zones the effective discharge will, of course, be zero. Further inclina-` tion will then cause the pump to discharge in the opposite direction since the former sealing zone will become the pumping zone, and vice versa. It is, therefore, apparent that the pump ofthe present invention may'bereversed without reversing the direction of rotation of the rotor.

The means provided for thus varying the de- 'gree of inclination of the cam carrying member I6 and hencel the discharge of the pump will now be described in detail. As best shown in Figs. 1 2 and 6, the central opening in member I6 extends sufliciently in line with groovesm2| to permit thedesired range of inclination.A Of

' course, when the cam face I8 rests on the surface of the rotorl member I4 no further inclination is possible in that direction. Thedischarge line 36 leading from port 36 has a branch line 36 I A 2,319,856 The method of assembly is now apparent: saidl which passes through casing head 31. branch line 36 communicates with an inner casing 38 containing a Sylphon 39. Adapted to be moved by `expansion or compression of said Sylphon is a piston 4I! acting on a lever 4I pivotally mounted on a boss in casing 2. An arm, 42 integral with said lever engages a rock member 43 formed on member I6 by which said member I6 may be tilted in accordance with the degree of expansion or compression of said Sylphon. A guide member 44 extends from adjacent boss 22 beneath said rock member and an open collar 45 partially embraces shaft 6 to hold member I6 in position. i

A spring 46 is housed in a hollow exterior boss 41 with onel end bearing on the end of lever 4I opposite to that acted on by piston 40. The compression of this spring may be regulated by adjusting screw-48 and lock screw 49. Said housing is closed by screw cap 59. By means of this spring member I6 is held in position for maximum discharge except when there is sunlcient pressure acting on said Sylphon to overcome said spring.

A further device is illustrated in Fig. 9 to be used to magnify variations in pressure in line 35 and pass such magnified effect on to the discharge regulating means above described. Said device comprises a fluid filled Sylphon 5| in a casing 52, said Sylphon being connected by piston 53 to diaphragm 54. Said diaphragm comprises a circular depressed member of synthetic rubber (Duprene) secured about its edge between cas` ing members 55 and 56 and sheathed between metal plates 51 and '58 except for a. relatively small area about its circumference. A s a result it may be calibrated within narrow limits. .The

device is attached to line 35 at inlet 59 and stead of branch line 36 shown in Fig. 3, Sylphon 5I is connected through coupling 63 to casing 38,

the whole being lled with a substantially noncompressible liquid. It is now readily apparent that even a. slight fluctuation in pressure in line 35 will be suiicient to cause a compensating adjustment in the discharge` of the pump.

The flow of liquid being pumped from supply tank 64 Will then be to inlet 3|, cam face port 23, pumping zone 25 (as shown in Figs'. 5 and 1) cam face port 24, outlet port 39, line 35, pressure magnifying device, and on to the engine or other destination.

To prevent mechanical shock to the vanes and yet obtain a non-pulsating .delivery it is necessary that the cam face I8, except in the pumping and sealing zones, be a curve such .that the sum of the retractive velocities of the vanes on the discharge side will be a constant; that is, the algebraic sum of the accelerations of retractionA It will also benecessary that two or more vanes be traveling across said curve at the same time; i. e.. that there be at least six equally spaced vanes in the rotor. Of course, it is also desirable for similar reasons that the camcurve on` the suction side besuch that the algebraicsum of the accelerations of advancement of the blades from the rotor equal zero. As the pump is reversible both cam curves ,will generally be so' plotted .in any case.

Said

While'spring means or the like 'may employed to urge the vanes against the cam face,

y,axis of the shaft 8 is suiilcient to hold the vanes in close contact with the cam face. lOf course, the inner and outer edges of said vanes comprise arcs concentric with the curve of ring I9.

Certain advantages of the above described construction are at once apparent. While centrifugal force is relied upon to hold the radially disposed substantially axially reciprocable vanes in close contact with the cam face nevertheless they are not impelled thereagainst with a force comparable to that in the case of pumps wherein the vanes oscillate toward and away from the center of rotation of the rotor. As a result, there is4 less wear of casing and vane ends, greater efficiency of operation, and less tendency to generate'heat with resultant vapor lock in the case of the more volatile liquids.

Furthermore, in the case of the pumpof the present invention the pressures on the bearings are much more constant than they have been with pumps of the prior art since the vanes do not move appreciably "off-center from sealing zone to pumping zone.

As the vanes do notcross 'each other there is no violent working of entrapped liquid which is so likely to cause vapor lock. i

When the device is employed as a motor there is, of course, no need to provide variable discharge means and the stator member may be fixedly positioned without .provision for tipping. As abovenoted, although generally described and claimed as a pump, it is intended to include the device, as defined. within the scope of the claims whether it be employed as a motor, meter, or for ment of saidV vanes, and means for varying the inclination of said stator with respect to the axis of rotation of said rotor to vary the rate of discharge of said pump.

2. In a rotary pump, a rotor, a stator,` a plurality of sector-shaped vanes carried by and movable with respect to said rotor, said vanes other similar purposes. As a motor, it may often be advantageously employed in driving pumps also constructed in accordance with the present invention.

Various other combinations are obvious, such as that obtained, for example, by mounting the rotors of two pumps on the same drive shaft.

Other modes of applying the principle oi the invention may be employed, change being made as regards tle details described.'` provided the features-.stated in any of the following claims, or the equivalent oi' such, be employed.

I therefore particularly point out and distinctly claim as my invention:

l. Inma rotary pump, a rotor, a stator, said l stator and'rotor having annular end surfaces axially spaced from and facing each other, a plurality of vanes carried by and axially movable with respect to said rotor. means maintaining said vanes in engagement with said-stator surface, adjacent pairs of said vanes cooperating with said. surfaces to define expansible pumping chambers therebetween, each of said vanescooperating to define a pump chamber of different volume from one of the pump chambers defined `by a next adjacent vane. said-stator surface having diametrically opposed camming surfaces adapted to impart axial movementto said vanes upon movement of said vanes thereover, a fluid inlet port in one of said camming surfaces occupying positions lying in planes containing the axis of said rotor and being pivotal about their sector centers toward and away from said stator, said stator. having an annular shaped surface facing said rotor and engageable with said vanes, means maintaining said vanes in engagement with said annular surface, adjacent pairs of vanes cooperating with said rotor and said annular surface `to define v expansible pumping chambers therebetween, each of said vanes cooperating to define a pump chamber of different volume from one of the pump chambers defined by a next adjacent vane, said annular surface having diametrically opposed camming surfaces adapted to impart pivotal movement to said vanes upon movement ofl said vanes thereover, and intermediate surfaces spacing said camming surfaces from each other, Isaid intermediate surfaces being so formed to define the outer and vinner limits of pivotal movement of said vanes with respect to said stator, a fluid inlet port in one of said camming surfaces and a iiuid discharge port in the other of said camming surfaces, and means mounting said stator for adjustable rocking movement with respect to said rotor to vary the position of said camming surfaces and thereby the rate\of pump discharge.

3. .In a rotary pump, a rotor, a stator, a plurality of sector-shaped vanes carried by and movable with respect to said rotor, said vanes occupying positions lying in planes containing the axis of saicl rotor and being pivotal about their sector centers toward and away from said stator. said stator having an annular shaped surface facing said rotor and engageable with said vanes,

and means maintaining said vanes in engage-- ment with said annular surface, adjacent pairs of vanes cooperating with said rotor and -said annular surface to define expansible pumping and a fluid discharge port in the other of said s camming surfaces, and intermediate surfaces spacing said camming surfaces from each other, said intermediate surfaces being so formed lto define the outer and inner limits of axial movechambers therebetween. each of said vanes cooperating to' define a pump chamber of different 'volume from one of the pump chambers defined by a next adjacent vane, said annular surface having diametrically opposed camming surfaces adapted to impart pivotal movement to said vanes upon movement of said. vanes thereover, and intermediate surfaces spacing said camming surfaces from each other, said intermediate surfaces being so formed to define the outer and inner limits of pivotal movement of said vanes with respect to said stator..a fluid inlet port in one of said camming surfaces and a fluid discharge port'in the other of said camming surfaces, saidvanes being arranged on said rotor to provide at least two vanes in contact with said last named camming surface at all times, said last named camming surface being constructed discharge pressure for effecting a rocking movement of said stator.

5. Apparatus as claimed in claim 2 Vtogether with fluid pressure meansfor effecting a rocking movement of said stator, and means responengagement with said annular surface, comprising a tail portion on said vanes spaced from said stator and to one side of the vane pivot center, 'said tail portion being operative to position the center of gravity of said vanes to such side whereby centrifugal force due to rotation of said vanes about the axis of said rotor will. be operable to move said vanes pivotally outwardly toward said stator, adjacent pairs of vanes cooperating with said rotor and said annular surface to define expansible pumping chambers therebetween, each of said vanes cooperating to define a pump chamber of dierent volume from one of the pump chambers defined by a next adjacent vane, said annular surface having diametrlcally opposed camming surfaces adapted to impart pivotal movement to said vanes'upon movement of said vanes thereover, and intermediate surfaces spacing said camming surfaces from each other, said intermediate surfaces being so formed to dene the outer and inner limits of pivotal movement of said vanes with respect to said stator, a uid inlet port in one of said camming surfaces anda uid discharge port in the other of said camming surfaces, and means mounting said stator for adjustable rocking movement with respect to said rotor to vary .the position of said camming surfaces and thereby the rate of pump discharge.

7. In a rotary pump, a rotor, a stator, a plurality of sector-shaped vanes carried by and movable with respect to said rotor, said vanes occupying positions lying inplanes containing the axis of said rotor and being pivotal about their sector centers toward and away from said stator, said stator having an annular shaped surface facing said rotor and engageable with said vanes, means maintaining said vanes in engagement withsaid annular. surface, said means comprising a part secured to said stator and presenting an engaging surface facing said stator surface engageable with said vanes at a point to one side of said stator and rotor surfaces, adjacent pairs of vanes cooperating with said rotor and said annular surface to define expansible pumping chambers therebetween, each of said vanes cooperating to denne a pump. chamber of different volume from-one of the pump chambers dened by a next adjacent vane, said annular surface having vdiametrically opposed,

camming surfaces adapted to impart pivotal movement to said vanes upon movement of said vanes thereover, and intermediate surfaces spacing said. camming surfaces from each other, said intermediate surfaces being so formed to denne the outer and inner limits of pivotal movement of said vanes with respect to 4said stator, a fluid inlet port in one of said camming surfaces and a fluid discharge port in the other of said camming surfaces, and means mounting said stator for adjustable rocking movement with respect to said rotor to vary the position of said camming surfaces and thereby the rate of pump y discharge. 1

8. In a rotary pump, a rotor, vanes having concentrically curved inner and outer edges radially disposed about the axis of said rotor and arcuately reciprocable axially of said rotor, a stator having an annular cam face positioned to contact ends of said vanes and cause their reciproeation upon rotation of saidrotor, inlet and'outlet ports in said cam faceand means for tilting said stator and cam face relative to the axis of rotation of said rotor to vary the reciproeation of said vanes.

9. In a rotary pump, a rotor, a stator, said stator and rotor having annular end surfaces axially spaced from and facing each other, a plurality of vanes carried by and axially movable with respectA to said rotor, adjacent pairs of said vanes cooperating with said surfacesto define expansible pumping chambers therebetween. said stator surface having diametrically opposed camming surfaces adapted to impart axial movement to said vanes upon movement of said vanes thereover; uid inlet and outlet ports respectively leading from the spaces between said rotor and said camming surfaces respectively, and intermediate surfaces spacing said camming surfaces from each other, and means for varying vthe inclination of said stator with respect to the ELBERT FOWLER.

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