US2696787A - Rotary pump - Google Patents

Description

J., F. JAwRowsKl Erm. 2,696,787

ROTARY PUMP 6 Sheets-Sheet l Eil'ed June 28, 1948 NORBERT JAwoRowsm ATTOFNW Dec. 14, 1954 J. F. JAwoRowsK| ETAL 2,696,787

` ROTARY PUMP Filed June 28, 1948 6 Sheets-Sheet 2 INVENTORST JOSEPH F. JAwoRowsm u NORBERT .JAwoRowsm BYZ ZZLZ ATTRNE'YS.'

6 Sheets-Sheet 4 INVEN T OFS.

ATTORNEYS ROTARY PUMP J. F. JAWOROWSKI ETAL Dec. 14, 1954 Filed June 28, 1948 JOSEPH F. JAWOROWSKI NORBERT JAwoRowsKl BY Dec. 14, 1954 J. F. JAwoRowsKl ETAI.Y 2,595,787

K ROTARY PUMP Filed June 28, 1948 6 Sheets-Sheet 5 v 33 wwg.

y JNVENTOHS. JOSEPH JAwoRowsKa NORBERT dAwoRowsm WMM ATTORNEYS l J. F. JAwoRowsKl ETAL ROTARY pum;

Dec. 14, 1954 e sheets-sheet Filed June 28, 1948 FE. iO

lllllllll 1L.

f IIN-ll IIIIIIII 'INVENTORS JOSEPH F. JQwoRowsKl NORBERT JAvvoRoWsm BY 9L i ATTORNEY .3f

` United States Patent AOffice 2,696,787 Patented Dec. 14, 1954 ROTARY PUMP Joseph F. `laworowski, Cleveland, and Norbert Jaworowski, Lakewood, Ohio, assignors, by direct and mesne assignments, to Shockey Corporation, Cleveland, Ohio, a corporation of Ohio Application June 28, 1948, Serial No. 35,618

8 Claims. (Cl. 103-42) This invention relates to pumps and more particularly to improvements in rotary pumps of the vane type wherein a rotor, carrying a plurality of circumferentially spaced radially movable blades, is disposed within a pump chamber or cylinder provided with suitable uid inlet and outlet ports.

Various forms of vane type rotary pumps have been employed in the pumping of iluids and it is among the objects of the present invention to provide an improved high pressure, high output, rotary pump which is particularly adapted for pumping -liquids such as oil or the like through pipe lines, and for other heavy duty pumping applications. t

Other objects of our invention include the provision of an automatically reversible rotary pump which may be driven in either direction without change in the arrangement or adjustment of the parts thereof and which is equally eiiicient regardless of the direction of rotor rotation; the provision of a vane type rotary pump in which the discharge pressure is applied to maintain the vanes in proper sealing engagement with the wall of the pump chamber or cylinder and wherein automatic means are provided for maintaining this pressure against the vanes regardless of the direction of rotation of the pump; the provision of a vane type rotary pump of the balanced rotor type having an arrangement of uid ports and passages whereby restriction or resistance to flow of fluid through the pump in either direction is reduced to a minimum; the provision in a vane type pump of means for automatically bleeding the drive shaft stuffing box chamber back to the low pressure side of the pump regardless of the direction of rotation of the pump rotor whereby the stuiiing box or drive shaft seal will never be subjected to the full discharge pressure, thus eliminating leakage therethrough; the provision of a pump structure which incorporates an effective discharge pressure control valve mechanism which may be accurately adjusted to control the maximum discharge pressure of the pump and which may readily be reversed when it is desired to reverse the ow through the pump by changing the direction of rotation of the rotor; the provision of a vane type rotary pump in which the varies are always maintained substantially in pumping position whereby the pump will start pumping immediately even under extreme low temperature and/or high viscosity conditions; the provision of a rotary pump the main bearings of which are effectively lubricated by the fluid being pumped; and the provision of an extremely compact and rugged rotary pump of the type described which may be economically manufactured, assembled and serviced and which vmay be operated under heavy duty service conditions for long periods of time without attention or adjustment.

The above and other objects of our invention will appear from the following description of one embodiment thereof reference being had to the accompanying drawings in which:

Figure l is an end elevation of the pump assembly, looking at the end opposite the drive shaft end.

Figure 2 is a side elevation of the pump assembly shown in Figure l.

Figure 3 is a vertical cross-sectional view of our improved pump taken substantially on line 3-3 of Figures l and 4.

Figure 4 is a transverse vertical cross-sectional view taken substantially on line 4 4 of Figure 2.

Figure 5 is a horizontal cross-sectional view taken substantially on line 5--5 of Figure 2.

Figure 6 is a vertical cross-sectional view taken substantially on line 6--6 of Figure 2 and illustrating the automatic stuing box pressure relief or bleeding arrangement.

Figure 7 is a fragmentary cross-sectional view, taken substantially on line 7--7 of Figure 6, and illustrating the rotor drive shaft, the main shaft bearing and their associated parts.

Figure 8 is a vertical cross-sectional view taken substantially on line 8 8 of Figure 2 and illustrating the automatic control means whereby pressure is maintained against the rotor vanes regardless of the direction of rotation of the pump.

Figure 9 is a detached end elevation of the pump rotor.

Figure l0 is a vertical cross-sectional view taken substantially on line 10-10 of Figure 9.

Referring first to Figures l and 2, our pump assembly includes a main housing H, an end cover and sub-housing P for the vane pressure control mechanism, and an end and drive shaft bearing housing B. As is clearly seen in Figures 3 and 4 the housing H is provided with a central cylindrical bore 1, the left-hand end of which (Figure 3) is closed by the end cover P and the righthand end of which is closed by the end cover B. Suitable screws 2 are employed to secure the end covers P and B to the main housing H. Supported within the cylindrical bore 1 is a sleeve S which is restrained against rotation within the housing H by any suitable means and is provided with an interior pump cylinder or chamber 3 of generally oval cross section as seen in Figure 4, the horizontal dimension of this pump chamber 3 in the sleeve S being greater than its vertical dimension.

In order to permit the passage of fluid into and out of the pump chamber 3 the sleeve S is provided with four circumferentially spaced sets of radially extending slots 4, 5, 6, and 7. Each set, as seen in Figure 5, consists of ve axially spaced slots and it will be understood that these uid passages through the wall of the sleeve S may, if desired, be made in the form of a series of drilled holes or any other suitable shape.

The main housing H is provided with fluid passages to convey the uid being pumped to and from the ports 4, 5, 6, and 7. In describing these passages it will be assumed that the pump rotor is operating in the direction of the arrows on the drawings to draw uid in through the right-hand (Figure 4) opening 8 and discharge same through the left-hand opening 9. Accordingly opening 8 will be referred to as the pump inlet and opening 9 as the pump discharge outlet but it will appear later that, when the rotation of the rotor R is reversed, the opening 9 will become the inlet and the opening 8 the outlet. Fluid which enters through the inlet 8 is divided at the projection 10 on housing H and a part passes upwardly through the curved passage 11 to the transversely extending header chamber 12 which overlies and connects to the radial ports 4 in the sleeve S (see Figure 4). Another part of the entering fluid passes downwardly through the lower inlet passage 13 which, as is clearly seen in Figure 5, extends across the full width of the sleeve S and connects to the radial ports 6 in sleeve S. An upper discharge passage 14 in the housing H, similar in form and disposed in side-by-side offset relation to passage 11, extends from the transverse header chamber 15, which overlies and is connected to the radial discharge ports 7. to the discharge opening 9.4 A lower outlet passage 16, similar in form to passage 13. connects the radial discharge ports 5 in sleeve S to discharge opening 9 and the projection 17 on housing H is similar in arrangement and function to projection 10 previously referred to.

Rotor shaft supporting bushings or bearings 18 and 19 are mounted in the end cover.; members B and P respectively and are held against rotation by suitable pins 20 and 21 (see Figure 5 These bushings 18 and 19 have inner ange portions 18' and 19 which are contoured as indicated in Figure 4 to correspond to the cross-sectional form of pump chamber 3 and serve to support and guidethe rotor vanes as will appear later. The pump rotor, generally indicated at R, is best seen in Figures 9 and l0 and has an axiallylextending bore 22, recessed end portions 23 and 24a center chamber 25, and a plurality of axially extending .holes .26 .into which the .open vended vane carrying slots 27 extend.

When the pump is assembled the rotor R is disposed within .the pump :chamber and Aits .diameter ,is such that a running lit is `provided Ybetween .the rotor and the wall `of ,the Ichamber 3 at the narrowest dimension of the chamber (top and bottom thereof as seen in the drawings). The drive .shaft ,D extends through :the bushing 1S into the bore 22 of rotor fR and is keyed theretoiby suitable keys Zfand 29 (see yFigure 3) which are supported in a novel manner which will be described later. Shaft .D terminates at the center chamber yof the -rotor R .and ahollow `tubular supporting shaft is secured :in the boreZl) ofthe rotor .R .and .extends from the vopposite side 4of .chamber .25 outwardly 4through bearing bushing 19 and connects to a .vane pressure chamber 31 inthe end lhousing P.. As is best seen vin Figures 4 and t5, Evanes .3 2 are disposed vin each .of :the slots 27 of rotor R. These wanes vare of the-samellength as .the rotor yR land the inner edges of their outer end portions extend into the 4recesses ,23 and 24 at the ends ofrotor R. As the vane guide or cam portions i8 vvand 19 of bushings 18 and v19 extend respectively into the recesses 23 and 24 of rotor R the youter ends of the vanes 32 are supported and guided thereby. As these anges 18 :and 19 are contoured .-.to .correspond v.to the cross-sectional form of .the pump chamber 3 they serve tomaintain .the outer edges .of the vanes .32 at all vtimes in y close proximity .to the vwall of the lpump chamber 3.

VThe a-nges 18 and 19 however are .not depended upon to maintain sealing contact between the .edges of the vanes and the pump chamber .as .fluid .pressuremeang to be described in .detail later, is provided for urging the vanes into proper sealing `contact with the wall of the pump chamber.

The outer end portion .of drive .shaft D .may be mounted in an yanti-friction bearing 33 and va stuffing ybox or oil seal of any suitable type is generally indicated at 34 and .is provided :to prevent ,leakage around the shaft to the -outside Yof rthe housing. .A lubricant retaining sea for thefanti-frict'ion bearing 33 .is shown .at '35 in'Figure 3 and the proiect'ing end of shaft D may be keyed at 36 for connection to any suitable source .of power.

Before describing the other features of our invention an `explanation will be given of the operation of the structure vdescribed above to pump a fluid. Assuming that -the rotor R is being .driven in counterclockwise direction as seen in `Figure 4 .and that a supply of duid to be pumped is connected tothe inlet opening 8, as the rotor R rotates the vanes .32 will sweep over the inner surface of the pump ,chamber 3 with vtheir outer edges in engagement therewith and the fluid being pumped will pass from .opening 8 through the passages 11 and 13 tothe inlet ports 4 and ,6 respectively in the sleeve S. Fluid will enter the crescent shaped pumping chamber 37 between the left-hand (Figure 4) side of sleeve S and rotor R through ports 4 and will be picked up by the vanes 32 and discharged through the ports 5 into the outlet passage 16 and out through opening 9. ln like manner a portion of the vfluid entering through opening 8 will pass through the lower inlet passage 13 to the inlet ports 6 and into the crescent shaped chamber 38 between the righthand (Figure 4) side .of sleeve S and rotor R. This fluid will be picked up by the vanes 32 and carried to and forced out through the outlet ports 7 yinto the header 1-5 and outlet passage .14 and out through the discharge opening 9.

By providing diametrically opposed sets of radially extending inlet ports 4 and 6and radially extending outlet ports 5 and 7 the pressures .on the rotor R are balanced, the bearing loads lare reduced, and severe stressing of the parts is avoided thus prolonging the life of the pump. Our novel arrangement of inlet .and outlet ports and passages providesunrestricted fluid inflow and outflow paths through the pump which paths are of ample cross-sectional area throughout their lengths and free from abrupt bends or sha-rp corners and thus offer minimum ow resistance with resulting increase in pump eiciency. Our arrangement permits an exceedingly compact and easily serviced pump structure and achieves a Ysubstantial reduction in the power required to operate ourV pump, lunder any given set of operating conditions, as compared to prior balanced rotor type rotaryl pumps with which we' are familiar. 'It will be understood that if the direction of rotation of rotor R is reversed from 4 that described above the opening 9 will become the pump inlet and opening 8 will become the pump discharge and the inlet ports and passages will become outlet ports and passages and vice versa.

As noted above, the vanes 32 are held in sealing contact with the bore of the pump chamber or cylinder 3 by means of the discharge pressure of the uid being pumped. This fluid pressure his applied through the hollow shaft 30, the center chamber .2S of rotor R, and the holes 26 into which the inner edges of the vanes 32 project (see Figures 3J 4, and l0). .As the end faces of rotor R have a running 4lit with the adjacent end faces of cover housings P and B, the oil or other fluid being pumped which .enters the holes 26 can only escape by leaking past the ends of the rotor R or through the bushings 1S and 19. A .slight leakage at these points is not objectionable as it serves to maintain a positive lubrication of `the relatively moving parts.

Fluid under pressure is supplied to the Ahollow shaft Sill `from vthe -vane pressure chamber 31 (see Figures 3 and '5). This Achamber 31, as is best seen in Figures 4 and 8, is connected to the pump chamber 3 through axiallyextending `spacedports 39 and 40. Port 39 4extends from pressure chamber 31 and enters the crescent shaped chamber 37 on the left-hand (Figure 8) side `of the 4bottom point of engagement yof the rotor R with the pump chamberS. In like manner port 4t) extends from chamber 3-1 and enters ythe crescent shaped vchamber 33 on :the right-hand (Figure 8) side of `the lower contact point zbetween the rotor R and the pump chamber 3. Thus, when the impeller is rotating in the direction indicated by the arrows in Figures 4 and 8, iiuid under high pump discharge pressure will be forced out through port 39 into the pressure chamber 31 and through the hollow shaft 30, chamber 25, and holes 26 in rotor R to the undersides of the -vanes 32, forcing them outwardly into effective sealing engagement with the wall of the pump chamber 3.

As v'is "best seen in Figures 5 and 8 vertical passages 3'9" and 40 yextend from ports 39 and 40 respectively upwardly 'and connect to 'transverse bores '39 and 4% respectively. Acentral web 41 extends into the pressure chamber '31 and is provided with `a bore 42 of the same size as, and 'concentrically arranged with, bores 39 and 40".

In order automatically to insure a supply of fluid under pressure in the vane pressure chamber 31, regardless of the direction of rotation of the rotor R, a piston or plunger type valve 43 is mounted for reciprocating movement in the bores 39, 40", and 42. 'This plunger valve 43 is of such length that it is at all times partially disposed in the bore 42 of web 41 and is longer than the distance between the inner ends of bores 39" and 40 to prevent the possibility of communication between bore 39 and bore 40" (see Figure 8). Endwise movement of .plunger valve 43 is limited by projections 44 and 4S on the end plug screws 46 and 47 respectively and it will lbe seen from Figures 5 and '8 that when the rotor is being driven in the direction indicated (counterclockwise) vliquid under pressure will pass through the port 39, passage 39', and bore 39" ,and act upon the end of plunger 43 to force same to its extreme right-hand position (Figure 8) against the stop projection 45. With plunger 43 in this `position liquid under pressure passes freely through the bore 39" into chamber 3l and on through the hollow shaft 30 as previously described.

If it is desired to reverse the rotation of the pump rotor and thus change the direction of flow through the pump in such a manner that liquid will Abe taken in through the opening 9 and discharged through opening 8, such reversal of the rotation of rotor R will cause the pump discharge pressure to be established in the port 40 and the passage 40. When this occurs the plunger 43 will be moved to the left (Figure 8) against the stop projection 44 thus permitting liquid under pump discharge pressure to enter chamber 31 through port 40 and passage 40. Liquid is prevented by the plunger valve 43 from passing back to the low pressure side of the pump through passage 39 and port 39 and thus the eiciency of the pump is in no way diminished. Our above described. arrangement for supplying liquid under pressure to urge the rotor vanes outwardly .is rugged, fool-proof, inexpensive, and effectively and automatically l functions without any attention from the operator to insure a proper supply of vanesealing pressure regardless of the direction in which the pump is operated.

In the opposite or drive shaft supporting housing B a pair of ports 48 and 49, corresponding in form and location to ports 39 and 40 just described, are provided. These ports are seen in Figures 4, 6, and 7 and it will be observed that port 48 connects to a valve chamber 50 in housing B while port 49 connects to a similar but separate and independent valve chamber 51. The drive shaft D extends through a stufling box or shaft seal chamber 52 in the end housing B (see Figures 6 and 7) and passages 53 and 54 extend from chamber 52 into valve chambers 50 and 51 respectively. The inner ends of passages S3 and 54 are formed as conical valve seats 53 and 54 for the valves 55 and 56 which are here illustrated as ball type valves. A spring 57 urges valve 55 toward its seat 53' and is located by a stud 58 on screw plug 59. In like manner spring 60 urges valve 56 toward its seat 54 and is located by a stud 61 on screw plug 62.

It will be seen from Figures 3, 5, and 7 that the shaft bearing 18 extends into the chamber 52 and the function of the double ball valve arrangement just described is to permit the oil or other liquid being pumped to pass outwardly between the bushing 18 and drive shaft D to provide positive lubrication therefor but to prevent excessive pressure from building up in chamber 52 against the oil seal or stuffing box arrangement indicated at 34 which might cause leakage therethrough. With our ball valve arrangement pressure within the chamber 52 is automatically maintained at or below a desired predetermined maximum value regardless of the direction of rotation of the pump rotor. With the rotor being driven in the direction indicated by the arrow in Figure 6, which is the same direction as indicated in Figure 4, uid under the pump discharge pressure will be forced through the passage 48 into the valve chamber 50 and will tend to maintain the ball valve 55 seated against the seat 53. Liquid which enters the chamber 52 around the shaft D is also under substantially the pump discharge pressure and, when chamber 52 becomeslled with liquid, the ball valve 56 may be pushed downwardly against the spring 60 into open position as seen in Figure 6 permitting the escape of liquid from chamber S2 back into the suction or inlet side of the pump through the passage 49. The spring 60 will, ofcourse, be of such strength and be so adjusted that the valve 56 will open whenever a pressure is built up in chamber 52 such that there is danger of leakage past the oil seal 34. Thus the ball valve 56 in effect becomes a pressure regulating valve for maintaining the pressure which can be built up in chamber 52 below a predetermined safe value.

If the pump is operated in the opposite direction from that indicated in Figure 6 the functions of valves 55 and 56 automatically are reversed and valve 56 becomes effective to seal off the high pressure side of the pump from the chamber 52 while valve 55 acts as a pressure regulating valve to limit the pressure which can build up in chamber 52 and to bleed excess liquid which enters chamber S2 back into the inlet side of the pump.. It will be understood from the above description of our improved automatic bleed valve arrangement that, regardless of the direction of rotation of the pump rotor, a build up of excessive pressure against the drive shaft stufng box or oil seal 34 will be automatically and positively prevented. No attention is required on the part of the operator to effect the change over in functioning of our automatic control when the direction of rotation of the pump is changed and our arrangement accordingly insures positive lubrication of the main shaft bearing in the bushing 18 at all times.

We have also incorporated in the illustrated pump an automatic discharge pressure control means which will now be described. The housing H is formed with a center web 63 (see Figures 3 and 4) which extends in the direction of the axis of rotation of rotor R and separates the passage 13 from the passage 16. It will be noted that these passages have downwardly extending portions 13 and 16' disposed on opposite sides of web 63 and that a communication or by-pass port 64 extends through web,

63 and is adapted to connect passages 13 and 16. Port 64 is formed with oppositely facing valve seats 65 and 66` and the housing H is bored to provide similar cylindrical openings 67 and 68 symmetrically arranged on opposite sides of the web 63 and axially aligned with each other and with the communication port 64.

say

, As illustrated in Figure 4, in which the pump is arranged for rotation of the rotor in counterclockwise direction and uid ow from right to left, a cylinder member 69 having a closed outer end and open inner end is held in position in the opening 67 as by screws 70 and an end cover and spring abutment plate member 71 is secured to housing H, as by screws 72, to close the outer end of cylindrical opening 68. Disposed within the cylinder 69 is a hollow piston or plunger 73 having a closed inner end portion 74 and opening into the cylinder 69 at its opposite end. A suitable piston sealing means, such as a piston ring indicated at 73', is preferably provided to reduce possible leakage past the piston 73 which, as will appear later, is subjected on one end to the relatively low pressure of the pump inlet and on its other end to the relatively high pressure of the pump outlet. Extending from the closed end 74 of piston 73 is a hollow valve stem member 75 which carries a poppet valve 76 having a seating face 77 disposed to coact with valve seat 66 in web 63 to close the communieating port 64 between the passages 13 and 16. The hollow valve stem extends beyond the poppet valve 76, as indicated at 75', and forms a guide for the pressure regulating spring 78 one end of which abuts against the poppet valve 76 kand the other end against an adjustable abutment 79. Adjusting screw 80 extends through the end cover plate 71 and has a flattened outer end portion 81 adapted to be engaged by a wrench or the like. The abutment member 79 has a threaded support on screw 80 and is provided with a lug 82 at its outer periphery which projects into a slot 83 formed in the cup shaped housing 84 which extends inwardly from the end cover plate 71. The degree of preloading of the spring 7S can be adjusted within certain limits by releasing the lock nut 85 and turning the screw 80 by means of its iiat end 81 to cause the abutment member 79 to move axially on screw 80 and thus increase or reduce the compression of spring 78. A tapered shoulder 80 on screw 80 is adapted to seat on a corresponding seat in cover plate 71 and spring 78 tends to hold shoulder 80 seated even when lock nut 85 is loosened, thus preventing leakage at all times. The end 75 of the hollow valve stem 75 opens into the cylindrical chamber or opening 68 and thus is connected directly with the passage 13-13 of the housing H. When the rotor is being driven in counterclockwise direction as seen in Figure 4 passage 13 is one of the low pressure inlets and accordingly the low pump suction or intake pressure will prevail throughout the chambers 13-13, cylindrical opening 68, the interior of tubular valve stem 75, cylinder 69 and against the left-hand (Figure 4) end of piston 73. The pressure on the opposite side of web 63 in passage 16-16 will however be the high pump discharge pressure. This high presure will be effective against the outer surface of the end wall 74 of piston 73 and also against the left-hand side (Figure 4) of poppet valve 76. It will be noted that the area of the poppet valve 76 which is exposed to the pump discharge pressure is greater than the area of the piston 73 which is exposed to the same pressure. Accordingly the pump discharge pressure will exert a force urging the valve 76 towards open position (to the right in Figure 4) which is equal to the difference in the exposed areas of valve 76 and piston end 74 multiplied by the pump outlet pressure in the passage 16. By making the difference in the effective areas of the valve and piston relatively small a relatively small force will be exerted tending to move the valve-piston assembly toward its open position even when the pump is operating at a high discharge pressure such as 800 to 1000 lbs. per square inch and accordingly the pressure regulating spring '78, which opposes opening movement of valve 76, may be made relatively light. This enables the pressure regulating by-pass controls to be made in an exceedingly compact form and susceptible to easy and accurate adjustment.

The operation of our discharge pressure control bypass valve mechanism just described is as follows. lf, for example, it is desired to deliver the pump output at a maximum pressure of 500 lbs. per square inch the spring 78 will be so proportioned and adjusted that when the pressure in the discharge passage 16-16 reaches 5G() lbs. the pressure differential effective to move valve '76 will be sufficient to overcome the spring 78 and open valve 76 permitting fluid to be by-passed from the pump outlet 16 back into the low pressure inlet 13, thus preventing excessive pump discharge pressure. This bypass pressure control is, of course, entirely automatic and the maximum discharge pressure maybe varied by.

come? chan-ging the spring '78 forby uadjustments thereof through the screw `Sila-nd abutment 7-9. v l

Itis a'featu're of our invention'that Athe automat-ic discharge pressure control mechanism ljust described lmay easily be reversed when it -is desired to 'reverse the rotation of the pump rotor. This reversal of the parts is possible -because the "cylindrical "openings 67 and 68 are identical Yand `itis only necessary to "remove the screws 70 and 72,'reverse the `Yvposit-ions of Ythe cylinder 69 and end cover plate 71-and at thesame time reverse the piston 73 a-nd valve 76 so that ythe valve y"I6 will seat upon seat v65 on the opposite side of web 63. This operation may beed'ected 'in avery short time without special equipment or skill. As our improved pump includes automatic controls whereby the pump output .pressure-is applied'to the inner edges 'of the vanes regardless of the direction of pum'p rotation and lautomatic Trneans for control ofthe :bleed-off vof oil passing through lthe ymain shaft bushing regardless of direction of pump rotation, it will be seen that with the :pump 'disclosed herein it is only necessary to reverse the pressure control valve 76 in order to change 'over the Vpump fromoperation-in one direction to operation inthe opposite direction. VFurthermore th'e pump is exactly Vas eiective and 'eiiicient in either direction of rotation. If the .pump dischargepressure 'control is not desired Aor'necessary the valve '76 may be blocked in closed -position by interposing a 'suitable block vmember (not shown.) lbetween 'the screw 80 Vand the end of valve stem extension 75 to hold valve 76 seated on the web `63. When the pump is so operated with valve 76 locked in closed position it may be reversed without any attention whatever on lthe part of the operator. It will also be understood that for someserv'ice requirements cr conditions it maybe desirable to supply pumps in which th'e discharge pressure control by-pass lis omitted in which case the by-pass port 64 will `be omitted and the web 63 leftsolid. Such pumps, of course, retain all of the other advantageous features of our automatically reversib'le vane'type balanced rotor pump.

By providing means for applying vthe pump discharge pressure against the rotor vanes to urge them outwardly into proper sealing contact with the wall of the pump chamber we provide a vane lpump wherein leakage pa'st the vanes is minimized and which `automatically compensates for wear of both the vanes and the pump charnber. The vane cams or end anges 18 and I9' of the bushings '18 and 19 serve to keep the vanes lfrom dropping into the rotor slots when the pump is stopped and to hold the vanes sufficiently close to their pumping positions adjacent the wall of chamber 3 to startfthe pump action land build up initial discharge pressure which will force the vanes out into proper sealing engagement with the Walls ot' chamber 3.y Thus our vane Acams yinsure immediate and positive pumping operation under all service conditions, and particularly at low temperatures or after a pump has been standing idle for a long time.

it will be seen from the above description of our improved :pump that we have provided 'a compact and rugged vane type rotary pump having effective automatic controls for 'the vanepressure 'and stuiiing box bleed-off. We have also provided a 'pressure control bypa'ss'arran`ge ment which eliminates the necessity for heavy 'sp'ringsa'nd may most readily be 'reversed to accommodate `changes' in 'pump rotation.

Another feature of our improved pump design i's the arrangement of the keys 23 and Z9 which etect driving connection between the main shaft D 'and the rotorRv. As is seen in Figure l0 the bore 22 in 'rotor R is provided with a circumferential groove 86. Opposed key slo't's S7 and S5 (Figure 9) are 'also formed 'in :the bore 22 of rotor R and corresponding key slots 89 and 90 are cut into the shaft D. VThe keys 28 and 29 are held in posi'- tion in the slots 87 and 88 of rotor R by a split expansion ring 91, of spring wire orn the like, which engages suitable grooves in the ends of keys 28 and 29 and also lies in the groove 86 of rotor R. This arrangement is clearly illustrated in Figure 3 and it makes it possible to maintain the inner end of shaft D at the full diameter of the bore in bushing 18 while still permitting the shaft to be assembled after the rotor has been installed in the pump chamber 3. With the key support illustrated and described the entire end unit B can be removed by taking out screws 2 and withdrawing the housing B and shaft D from the housing -H. -If the keys '28 and 29 were supported in the shaft the usual manner, -instcad of being held in the vshaft receiving -holelin rotor R, this mode of assembly and disassembly would not be possible.

Although we have described the illustrated embodiment of our invention in considerable detail it will be understood that variations and moditications may be made in the `form, proportions, and arrangement of parts making up our improved pump. Accordingly we do not wish/to be limited'to the speciic structure herein shown and described but' claim as our invention all embodiments thereof coming within the scope or the appended claims.

We claim:

l. A vane type rotary pump including a housing structure having a pump chamber, said pump chamber having an inlet port at a lower pressure portion thereof, and a discharge port at a high pressure portion thereof, a rotor supported substantially in sealing contact with a portion of the wall of said chamber for rotation therein, a vane carried by said rotor for radial movement relative thereto, said housing structure having a vane pressure chamber therein at one end of said pump chamber, a hollow shaft extending from one end of said rotor intosaid vane pressure chamber, said rotor having a fluid conducting passage extending fromsaid hollow shaft to the inner edge of said vane, said housing structure having a iluid passage extending from said pump chamber adjacent to and on one sideorF said sealing contact to said Vane pressure chamber and another duid passage extending from said pump chamber 'adjacent to but on the other side of said sealing contact to said vane pressure chamber, a shiftable sliding plunger valve supported in said vane pressure chamberwith one end exposed to iiuid pressure from said iiuid passage on one side of said sealing contact and its other end exposed to fluid pressure from said fluid passage on the other side of said sealing contact, said plunger valve being adapted to have movement between one position in which said iiuid passage on one side of said scaling contact is connected to said vane pressure chamber and said fluid passage on the other side of said sealing contact is shut ofi from said Vane pressure chamber and another position in which said connections are reversed, said plunger valve being adapted automatically to shi t between said positions when rotation `of said rotor is reversed, a drive shaft extending from the other end of said rotor in axial alignment with said hollow shaft, and bearing means carried by said housing for rotatably supporting said drive shaft.

2. A vane type rotary pump including a housing structure having a pump chamber, said pump chamber having an inlet port and a discharge port, a `rotor supported substantially in sealing contact with a portion of the wall of said chamber for rotation therein, a vane carried by said rotor for radial movement relative thereto, said housing structure having a vane pressure lchamber therein, a hollow shaft extending from one end of said rotor into said vane pressure chamber, said rotor having a iluid conducting passage extending from said hollow shaft to the inner edge of said vane, said housing structure having a fluid passage extending from said pump chamber adjacent to and on one side of said sealing contact to said vane pressure chamber and another fluid passage extend ing from said pump chamber adjacent to but on the other side of said sealing contact to said vane pressure charnber, valve means, responsive to the pump discharge pressure, for automatically connecting said vane pressure chamber to the one of said duid passages which extends from the high pressure portion of said pump chamber and 'shutting said vane pressure chamber off from the one of said fluid passages which extends from the low pressure portion of said pump chamber regardless of the direction of rotation of said rotor, said housing structure having` 'a second chamber therein, a drive shaft extending from the other end o'f said rotor into said second chamber, a bearing for said shaft having one end in said second chamber and its other end in said fluid conducting passage in said rotor whereby said other end of said bearing is subjected to the vsaine pressure as said vane, said housing structure having a uid passage extending from said pump chamber adjacent tc and on 'one side of said sealing kContact to said second chamber and another fluid passage extending from said pump chamber adjacent `to but on the other' side of said sealing contact into said second chamber, Aand independent spring-backed valves. in said last-named lfluid passagesy for automaticall controlling the 'maximum pressure in said second chamber regardless of the direction of rotation of *said rotor.

assays?" 3. A vane typev rotary pump including a housing structure having a pump chamber, said pump chamber having an inlet port and a discharge port, a rotor supported substantially in sealing contact with a portion of the wall of said chamber for rotation therein, a vane carried by said rotor for radial movement relative thereto, cam means carried by said housing structure for maintaining said vane adjacent the wall of said pump chamber during rotation of said rotor, said housing structure having a vane pressure chamber therein, a hollow shaft extending from one end of said rotor into said vane pressure chamber, said rotor having a fluid conducting passage extending from said hollow shaft to the inner edge of said vane, said housing structure having a fluid passage extending from said pump chamber adjacent to and on one side of said sealing contact to said vane pressure chamber and another fluid passage extending from said pump chamber adjacent to but on the other side of said sealing contact to said vane pressure chamber, valve means, responsive to the pump discharge pressure, for automatically connecting said vane pressurechamber to the one of said fluid passages which extends from the high pressure portion of said pump chamber and shutting said vane pressure chamber off from the one of said fluid passages which extends from the low pressure portion of said pump chamber regardless of the direction of rotation of said rotor, said housing structure having a second chamber therein, a drive shaft extending from the other end of said rotor into said second chamber, a bearing for said shaft having one end in said second chamber and its other end in said fluid conducting passage in said rotor whereby said other end of said bearing is subjected to the same pressure as said vane, said housing structure having a fluid passage extending from said pump chamber adjacent to and on one side of said sealing contact to said second chamber and another fluid passage extending from said pump chamber adjacent to but on the other side of said sealing contact into said second chamber, and independent spring-backed valves in said last named fluid passages for automatically controlling the maximum pressure in said second chamber regardless of the direction of rotation of said rotor.

4. In a rotary pump, a housing having a pump chamber of generally oval transverse cross section, a cylindrical rotor supported for rotation in said pump chamber and substantially engaging the wall thereof along diametrically opposed surfaces whereby two generally crescent shaped chambers are formed between said rotor and said wall of said pump chamber, a pluralty of radially movable vanes carried by said rotor, means for urging said vanes outwardly into engagement with said wall of said pump chamber, said housing having inlet and discharge openings symmetrically arranged on opposite sides of the axis of rotation of said rotor, each of said crescent shaped chambers having spaced inlet and discharge ports leading radially thereinto adjacent said surfaces of en gagement of said rotor with said pump chamber, said housing having an inlet passage extending from said inlet opening to the inlet port of the crescent shaped chamber on the opposite side of the rotor axis from said inlet opening and a substantially identical discharge passage disposed in overlapping side-by-side relation to said inlet passage and extending to said discharge opening from the discharge port of the crescent shaped chamber on the same side of the rotor axis as said inlet opening, said inlet and discharge passages each having an axially extending header portion extending under the other of said passages, said housing also having a second inlet passage extending from said inlet opening to the inlet port of the crescent shaped chamber on the same side of the rotor axis as said inlet opening and a substantially identically arranged and contoured second discharge passage extending to said discharge opening from the discharge port of the crescent shaped chamber on the opposite side of the rotor axis from said inlet opening, a wall in said housing separating said second inlet passage from said second discharge passage, said wall having a by-pass port extending therethrough, and spring-opposed discharge pressure control valve means associated with said by-pass port for controlling the flow of fluid therethrough.

5. In a vane type rotary pump, a housing having a pump chamber of generally oval transverse cross section, a cylindrical rotor supported for rotation in said pump chamber and substantially engaging the wall thereof along diametrically opposed surfaces, circumferentially spaced vanes carried by said rotor for radial movement relative thereto, said housing structure having a vane pressure chamber therein at one end of said pump chamber, a hollow shaft extending from one end of said rotor to said vane pressure chamber, said rotor having a fluid conducting passage extending from said hollow shaft to the inner edges of said vanes, said housing structure having a fluid passage extending from Said pump chamber adjacent to and on one side of one of said diametrically opposed surfaces of engagement to said vane pressure chamber and another fluid passage extending from said pump chamber adjacent to but on the other side of said one of said surfaces of engagement, a shiftable sliding plunger valve supported in said vane pressure chamber with one end exposed to fluid pressure from said iluid passage on one side of said one of said surfaces of engagement and its other end exposed to fluid pressure from said fluid passage on the other side of said one of said surfaces of engagement, said plunger valve being supported for movement between one position in which said fluid passage on one side of said one of said surfaces of engagement is connected to said vane pressure chamber and said fluid passage on the other side of said one of said surfaces of engagement is shut off from said vane pressure chamber and another position in which said connections are reversed, said plunger valve being adapted automatically to shift between said positions when rotation of said rotor is reversed, a drive shaft extending from the other end of said rotor in axial alignment with said hollow shaft, and bearing means carried by said housing for rotatably supporting said drive shaft.

6. A vane type rotary pump including a housing structure having a pump chamber, said pump chamber having an inlet port and a discharge port, a rotor supported substantially in sealing contact with a portion of the wall of said chamber for rotation therein, a vane carried by said rotor for radial movement relative thereto, a second chamber in said housing structure, a drive shaft extending from one end of said rotor into and through said second chamber, a bearing for said shaft having its outer end in said second chamber and its inner end subjected to substantially the fluid pressure in said discharge port, said housing structure having a fluid passage extending from said pump chamber adjacent to and on one side of said sealing contact to said second chamber and another fluid passage extending from said pump chamber adjacent to but on the other side of said sealing contact to said second chamber, and independent spring backed valves in said last named fluid passages for automatically controlling the maximum pressure in vsaid second chamber regardless of the direction of rotation of said rotor, said spring backed valves in said fluid passages being adapted to permit the flow of fluid only from said second chamber into said last named passages and to prevent the flow of fluid from said last named passages into said second chamber.

7. A vane type rotary pump including a housing structure having a pump chamber, said pump chamber having an inlet port at a low pressure portion thereof and a discharge port at a high pressure portion thereof, a rotor supported substantially in sealing contact with a portion of the wall of said chamber for rotation therein, a vane carried by said rotor for radial movement relative thereto, said housing structure having a vane pressure chamber therein at one end of said pump chamber, said rotor having a fluid conducting passage extending from said vane pressure chamber to the inner edge of said vane, said housing structure having a fluid passage extending from said pump chamber adjacent to and on one side of said sealing contact to said vane pressure chamber and another fluid passage extending from said pump chamber adjacent to but on the other side of said sealing contact to said vane pressure chamber, a shiftable valve supported in said vane pressure chamber with one end exposed to fluid pressure from said fluid passage on one side of said sealing contact and its other end exposed to fluid pressure from said fluid passage on the other side of said sealing contact, said valve being adapted to have movement between one position in which said fluid passage on one side of said sealing contact is connected to said vane pressure chamber and said fluid passage on the other side of said sealing contact is shut off from said vane pressure chamber and another position in which said connections are reversed, said valve being adapted automatically to shift between said positions when rotation `rassenza? i 1 of said rotor is reversed, a drive shaft for said rotor, :and bearing means carried Iby 'said-housing for rotatably V'supporting said drive shaft.

8. In a reversible, balanced rotor, rotary pump, a main housing member in the form of a hol-low metal casting having oppositely'disposed main inlet and outlet openings for liquid on respective sides of a generally cylindrical opening through the casting, sub-housing members generally closing the ends of the cylindrical opening, la metal sleeve substantially fitting the cylindrical opening and fixed snugly therein against rotation, the sleeve having a bore of generally oval transverse cross section with the long axis of the oval bore directed toward the inlet and outlet openings, a generally cylindrical rotor with radially movable fluid-pumping yvanes, the rotor being supported for rotation by the sub-housing members -coaxially of the cylindrical opening, said rotor being approximately in peripheral sealing Icontact with the oval lbore at diametrically opposite reg-ions of the rotor along the short axis of the oval, thus forming with said bore two symmetrically opposed crescent shaped pumping chambers with their apices adjacent the areas of sealing contact between Vthe rotor and said bore, the sleeve thereby having relatively thin wall portions disposed respec- -tively between the rotor axis and said inlet and outlet `channel-forming passages with branch portions extending partly around the sleeve peripherally thereof, the branches of one passage communicating with the inlet ports of the sleeve and the'branches o'f the other with the outlet ports of the sleeve, and said casting having thickened wall portions adjacent the sleeve on diametrically opposite sides of the sleeve, extending parallel to the axis of said cylindrical opening and of diminishing cross section toward the inlet and outlet openings and respectively approximately aligned therewith to provide fluid guides to and from respective branched passages while buttressing the sleeve at its relatively thin walled portions.

References Cited in the ile of this patent UNITED STATES PATENTS Number Name Date 1,123,977 Baker et al Jan. 5, 1915 1,321,706 Bosch Nov. 11, 1919 1,716,901 Rochford June 11, 1929 1,889,517 Roessler l Nov. 29, 1932 1,898,914 Vickers Feb. 21, 1933 1,980,404 Harman et al. Nov. 13, 1934 1,989,900 Vickers Feb. 5, 1935 2,098,652 Buckbee Nov. 9, 1937 2,157,089 Storch et al. May 2, 1939 2,256,459 Kendrick Sept. 16, 1941 2,319,238 Kendrick May 18, 1943 2,381,628 Thorpe-Woods Aug. 7, 1945 2,411,602 Tweedale Nov. 26, 1946 2,423,271 Talbot July 1, 1947 2,443,994 Scognamillo June 22, 1948 .FOREIGN PATENTSY Number Country Date 318,638 Great Britain 1930

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