US2510903A - Rotary pump or motor - Google Patents

Description

June 6, 1950 F. A. QUIROZ 2,510,903

ROTARY PUMP 0R MOTOR Filed May 8, 1947 2 Sheets-Sheet l {NVENTOR. jzzmgziaca A'. Qqzz'a June 6, 1950 A. QUIROZ 2,510,903

ROTARY PUMP OR MUTOR Filed May 8, 1947 2 Sheets-Sheet 2 INVENTOR. fiaqgiscal Qqz'ra;

Z W422/M Patented June 6, 1950 UNITED STATES. .PTELNT OFFICE ROTARY PUMP R MOTOR Francisco A. Quiroz, Newark, N, ,1, Application May 8, 1947, Serial No. M6 761 13 Claims. 1

This invention relates to improvements in pumps of the variable capacity type.

The invention has for an object to provide a novel construction of variable displacement rotary pump or motor which is of simple and inexpensive construction, and the rotor of which is so hydraulically balanced as to avoid axial thrust.

Further objects of the invention are to provide a novel form of rotor mounted to revolve in an enclosing casing, said rotor having reciprocable piston means and associated means to effect re, ciprocation of said piston means, together with easily and quickly manipulatable means for mod.- ifying the stroke of said piston means for ca,- pacity regulating effect; to provide means for automatically maintaining contact of the rotor with the casing in compensation for wear and so as to prevent leakage and loss .of volumetric ,eificiency; and to provide novel means for transmitting power to the rotor.

Other objects .of the invention, not at this time more particularly enumerated, will be understood from the following detailed description of the same.

Illustrative embodiments of the invention are shown in the accompanying drawings, in which:

Fig, l is an end elevational view of the .pump; Fig. 2 is a longitudinal sectional view of the same; Fig. 3 is a transverse vertical sectional view thereof, taken on line 3-. -3 in Fig. 2; Fig. 4 j,

is another transverse vertical sectional view thereof, taken on line 44 in Fig. 2; Fig. :5 is an end elevational view, similar to that of Fig. 1,, but with parts broken away to disclose internal means for regulating the stroke of the piston means, said regulating means being disposed in a neutral or non-pumping position; Fig. 6 is a detail longitudinal sectional view of the pump rotor per se; Fig. 7 is a view similar .to that of Fig. 5, with the piston stroke regulating means disposed in a pumping position; Fig. ,8 is a diagram showing various positions of the pumppiston stroke regulating means; Fig. 9 is a fragmentary longitudinalsectional View, showing a modified form of means for actuating the pistonstroke regulating means; and Fig. 10 is a fragmentary sectional View showing a modified means for sealing the pump drive shaft.

Similar characters of reference are employedin the above described views, to indicate correspond?- ing parts.

Referring to the drawings, the reference character 19 indicates a casing or housing which is p eferably of cyli dric l S apaand whi h is internally provided with a tapered roto cham e H disposed eccentric to the longitudinal axis of said casing or housing. Said tapered rotor .cham.- ber --II is closed at its end of minimum diameter (hereinafter referred to as the forward end) by an end wall portion 12 which forms an integral part of the forward end of the casing or housing, but is open at its end of maximum diameter (hereinafter referred to as its rearward end) whereby to open outwardly from the rearward end portion .of said casing or housing 1.0. The casing or housing H1 is provided in its rearward end portion with a countersunk seating socket l3 which is concentric to the longitudinal axis of the casing or housing. The rearward end of the-casing or housing is closed by a rotativelyadjustable cover plate [4, which is provided, in extension from its inner face, with a .boss 15 dimensioned to fit into .the annular seating socket 13 of the casing or housing. Formed in the periphery of said boss 15 is an annular seating channel [6 for the reception of a sealing ring or gasket 11, which is adapted to be compressed against the side walls of said seating socket 13, so as to seal the joint between the casing or housing and said cover plate. Said .cover plate M is secured to the casing or housing L0 by a plurality of bolts 1 8, preferably three in number :for small units. Said bolts 18 respectively pass through corresponding arcuate slots 19 with which the marginal portion of the cover plate is provided, so as to screw-into the :body of the casingor housing 1.0.

Mounted within the rotor chamber ll of the casing or housing, so as to rotate therein, is a correspondingly tapered rotor 20. Preferably the taper of the rotor chamber H and of the rotor 2,0 is of degree not less than fitteen degrees or more than twenty degrees. The rotor -21] is of somewhat less axial length than that of the rotor chamber 1 I, .so as .to .be .capable of being urged into close .contact with the rotor chamber walls under resilient axial thrust applied thereto by means hereinafter described, whereby .to com.- pensate for wear incident to rotor operation.

Intermediate its .ends, said rotor 2r is provided wi h a diametrically extending here, the respcc: t ve end portions of which provide cyl nder sham.- ber .21 and 2.2. .slidably reciprocable insaid bore is a single piston element 2.3, the respective .end portions 24 and ,25 ,of which are adapted to .be ope at ve recipra ated Within the res ective yl nder lqhambers .21 and 1.22.

he cas n -.0 housin 1.0 provided at one sid thereo w th :a rad al-intake passage 16 havi is -.a. nt n y sc ew-threaded outer and nor..-

tion 21 to receive connection thereto of a fluid supply conduit or pipe (not shown). In like manner, the casing or housing I is provided at the diametrically opposite side thereof with a radial outlet passage 28 having an internally screwthreaded outer end portion 29 to receive connection thereto of a fluid discharge conduit or pipe (not shown). Said intake and outlet passages 26 and 28 lie substantially in the plane of the diametric cylinder chamber forming bore of the rotor and its piston element 23. Formed in the casing or housing l0 intermediate the intake passage 28 and the rotor is arcuate duct 30 with respect to which the outer ends of the respective cylinder chambers 2i and 22 pass in communication therewith as the rotor revolves; and, similarly, intermediate the outlet passage 28 and the rotor is a like arcuate duct 3| with respect to which the outer ends of the respective cylinder chambers 2| and 22 likewise pass in communication therewith as the rotor revolves. Adjacent ends of said respective ducts 30 and 3| are separated from each other by intervening partition sections 32 which are formed in the body of the casing or housing ID, said partition sections being of circumferential extent not less than the diameter of the rotor cylinder chambers 2| and 22, and preferably somewhat in excess thereof. Suitably formed and located in the body of the casing or housing are air chambers 33 and 34 respectively so arranged that the respective ducts 30 and 3| communicate therewith for purposes hereinafter explained.

Projecting exteriorly from the forward end wall portion I2 of the casing or housing I0 is a stuffing-box extension 35 which is aligned with the axis of rotation of the rotor 20, and which houses a bearing 35 for supporting a power shaft 3']. Disposed within the stufiing-box extension 35, outwardly of the bearing 36, is a packing 38 adapted to be compressed around the shaft 31 by a gland 33 held in engagement therewith by a gland nut 46; said gland nut being adapted to be screwed onto the external screw-threaded end of said stumng-box extension 35. At its inner end, said power shaft 31 is provided with a coupling cross-head 4| which engages in a transverse outwardly open slot or channel 42, with which the forward end of the rotor 20 is provided, whereby to drive the latter. The relation of said coupling cross-head 4| to the receiving slot or channel 32 of the rotor 20 is such that an appreciable amount of axial play between said shaft and rotor is allowed for, whereby to permit wear take-up axial movement of the rotor relative to the shaft.

Means is provided whereby reciprocation of the piston element 23 in the cylinder chambers 2I-22 of the rotor 23 is induced by the rotary movement of said rotor; said means being subject to regulator adjustment whereby to both vary the stroke amplitude of the piston between a substantially neutral or non-pumping condition to a maximum stroke for maximum pumping effect, as well as to reverse the intake-outgo effect of the piston operation relative to the fluid intake and outlet passages of the pump. To this end, the rearward end portion of the rotor 20 is provided with a diametrically extending countersunk slideway 43 of suitable depth, which opens outwardly from the rear end face of the rotor, and which is of somewhat less length than the diametric width of said rear end portion of the rotor. Said slideway extends parallel to the cylinder chamber forming bore of the rotor.

Mounted within said slideway 43, to slide back and forth therein, is a slide member 44. Provided in the body of the rotor 20, intermediate the cylinder chamber forming bore and said slideway 43, is a transverse slot 45 which intersects the axis of the rotor 23. Aflixed to the slide member 44, to extend centrally therefrom through said slot 45 and into the piston element 23, midway of the ends of the latter, is a coupling pin 46. Said slot 45 is of a length limited to accommodate the movement of the coupling pin 46 back and forth therein as reciprocated by the movements of the slide member 44. The relative lengths of said slide member 44 and slot 45 are such,- however, that the former covers the latter at all times, so that no substantial flow of fluid between the cylinder chamber forming bore and the slideway 43 can occur.

countersunk in the inner face of the cover plate l4, which opposes the rearward end of the rotor 20, is a circular bearing chamber 41 which is disposed eccentric to the axis of the casing or housing l0 and its cover plate l4. Journaled in said bearing chamber 4'! is a piston driving and control disc 48. Afllxed to said slide member 44, adjacent an end thereof, is a crank pin 49 which extends into said driving and control disc 48 at a point thereof which is radially offset from its center or axis, and which is normally aligned in parallel plane with the longitudinal planes of the piston element 23 and slide member 44 (see Figs. 2 and 5), when the cover plate l4 occupies its neutral position shown in Fig. l and Fig. 5, i. 8. with the cover plate retaining bolts I8 disposed in mid-position between the ends of the arcuate slots l9. The center or axis of the piston driving and control disc is preferably downwardly offset a small distance relative to the axis of rotation of the rotor 20 (see Fig. 8), whereby to reduce the arcuate displacement of the crank pin 49 under adjustin shift of the piston driving and control disc 48 to an average approximating as nearly as possible a straight line reciprocation of the crank-pin 49, when the disc 48 is disposed to effect maximum reciprocating strokes of the slide member 44 and piston element 23.

Interposed between the piston driving and control disc 48 and the bottom or interior end wall of the bearing chamber 41 is a spring washer 50 which exerts a forward axial thrust upon said disc 48 adapted to be transmitted thereby to the tapered rotor 20, whereby to maintain the latter in close contact with the walls of the rotor chamber II, in manner adapted to take up or compensate for wear of the meeting surfaces of said rotor and walls.

With the piston driving and control disc 48 disposed to position the :crank pin 45 in the hereinbefore stated neutral position (shown in Fig. 5), when the rotor 20 is revolved with accompanying rotation of the disc 48 in the bearing chamber 41, the crank-pin 39 will be revolved through a substantially concentric path about the axis of rotation of the rotor 23, and consequently will not operate to transmit any substantial degree of reciprocatory movement to the piston element 23, and therefore the piston ends 24 and 25 respectively remain substantially stationary within the respective cylinder chambers 2| and 22, and no pumping action accompanics rotation of the rotor. When, however, the cover plate [4 is rotated from its neutral position in clockwise direction, as viewed in Fig. 5,

j the rotative movement of the cover plate will shift the eccentrically related piston driving and control disc :58 in direction whereby to move the crank-pin 49 connected therewith to an operative position (as e. g. shown in Fig. 7) so that it will be revolved through an offset eccentric path about the axis ofthe rotor, and consequently will so position and reciprocate the slide member 44 and through the latter the piston element 23 that the piston ends 2t and 25 will be respec tively reciprocated with fluid pumping effect in the respective cylinder chambers 21 and 22, and respectively in such relation to the intake passage 2-5 and associated duct 3%! andto the outlet passage 29 and associated duct 3!, as to draw in fluid through said intake passage and discharge the fluid from said outlet passage. If, on the other hand, the cover plate is is rotated from its neutral position in counter clockwise direction,.

as viewed in Fig. 5, the rotative movement of said cover plate will shift the ecoentrically re lated piston driving and control disc in direction whereby to move said crank-pin to an operative position so that it will be revolved through an oppositely offset eccentric path about the axis of rotation of the rotor 2d, but so as to position and reciprocate the slide member 4-? and piston element 23 in manner to reverse the flow of fluid through the pump; i. e. so as to draw in fluid from the outlet passage 28 and discharge it through the intake passage 26, thus reversing the functions of said passages.

The degree of shift of the piston driving and control disc and resulting amount of eccentric displacement of the crank-pin 49, in one direction or the other, relative to the rotor axis, will determine the length of piston strokes between neutral or minimum and maximum limits, and consequently will thereby determine the operative capacity of the pump. The lengths of the arcuate slots 59 of the cover plate [4 are so predetermined that abutment of given ends of said slots upon the retaining screws l8 will fix the limits of cover plate adjustment and consequently maximum piston strokes determining shifts of the piston driving and control disc 48 and its crank-pin id. It will be understood, of course, that the casing or housing 10 and cover plate l4 may be provided with cooperative calibrated scale and pointer or indicator mark (not shown), whereby to indicate selected piston stroke varying adjustments of the cover plate intermediate minimum and maximum positions thereof.

As shown in Fig. 4, the ducts 30 and 3| are of such extent as to assure effective communication, at proper times, of the respective cylinder chambers 2i and 22 and their pistons with the respective intake and outlet passages 25 and 28. In order to avoid undue pulsations in the flow of pumped fluid through the pump, and thus maintain such flow at an equalized and substantially uniform pressure, while at the same time cushioning the pump operation against undesirable knocking or hammering, the respective ducts are provided with the respective air chambers 33 and 3:1 in communication therewith.

In order to equalize fluid pressure against opposite ends of the rotor, the body of said rotor is provided with one or more endwise open fluid passages extending longitudinally therethrough.

In order to prevent obstruction or undue resistance to reciprocatory movements of the slide member lid in its slideway 43 due to the presence of fluid within the latter, said slide member 44 is also provided with one or more through passages52 disposed to extend longitudinally there through from end to end thereof.

Preferably the piston driving and control disc 48 is made of hard graphite, whereby to reduce to a minimum frictional resistance to its rotation movement within the bearing chamber 41 of the regulating cover plate Hi.

When the pump is to be used for the pumping of water, gases or other substantially non-lubricating fluids, the rotor is preferably made of hard graphite, a suitable plastic, or hard rubber; when, however, the pump is to be used for pumping of oil or similar fluids capable of lubricating effect, the rotor is preferably made of a selected metal.

In the above described embodiment of my invention, the cover plate 14 is rotatively movable relative to the casing or housing It! so as to directly serve as the piston stroke regulating means. As an alternative to such arrangement, another modified construction of piston stroke regulating means is shown in Fig. 9, wherein a cover plate 53 is immovably afiixed to the casing or housing It. Said cover plate 53 is provided with an inwardly open circular cavity 54 within which is mounted, subject to rotative movement therein about the longitudinal axis of the casing or housing II], a regulator member 55 which is provided with an outwardly projecting shaft 56. Said shaft 55 extends through the bore 51 of a bearing neck or gland 53 with which the cover plate 53 is provided. Afiixed to the outer end of said shaft 55 is a lever arm 59 for rotatively ad.- justing the regulator member 55. Formed in the interior side of the regulator member is a bearing chamber Ell which is eccentrically positioned relative to the axis about which said regulator member turns. Journaled in the bearing chamber 60 is the piston driving and control disc 48 which is associated with the rotor 28 and its parts in the same manner as already above described. It will be obvious that by imparting rotative movement to the regulator member 55, in selected direction by means of the lever arm 59, the piston driving and control disc 48 and the crank-pin 49 connected therewith may be shifted relative to the axis of the rotor 20, in the same manner and for the purposes hereinabove explained.

In Fig. 10 there is shown a modified means for joiu'naling the rotor drive shaft 31 in an extension 35 of the casing or housing IE3, which at the same time provides a highly efficient shaft seal; said modified means being alternative to the stufling box type of journal and seal above described. Said modified journaling and sealing means comprises the provision of a graphite bearing and seal member 5| mounted within the extension 35. Said member 6! is provided with an axial bore through which the drive shaft 31 extends, and the latter is provided at its inner end, intermediate the same and the coupling cross head 4|, with an annular conical portion 52 to fit into a-conical recess provided in the end of said member 5|. The outer end of the drive shaft is provided with a channel or spline Eli, and mounted on the shaft is a seating washer 55 having an internal key 65 to engage in said channel or spline '64, whereby said seating washer will rotate with the shaft. Mounted around said shaft and seated against said seating washer 65 is a compression spring 6? which thrusts against a thrust washer 68 fixed on said shaft by a cotter pin 58, or other suitable holding means. It will be obvious that the outward thrust exerted by the spring on the shaft operates to draw and 7 keep the conical portion 62 of the shaft tightly against the conforming recessed end of the seal member 6| with highly efficient shaft sealing effect.

Having now described my invention, I claim:

1. A pump comprising a casing having a rotor chamber entering one end thereof and disposed eccentric to the longitudinal axis thereof, said casing having diametrically opposed fluid induction and discharge passages respectively entering opposite sides of said rotor chamber, a rotor in said rotor chamber, means to rotate said rotor, said rotor having a cylinder bore extending diametrically therethrough in the transverse plane of said induction and discharge passages, a piston element reciprocable in said cylinder bore, said rotor having in an end thereof a slideway parallel to said cylinder bore, a slide member reciprocable in said slideway, means to transmit the movement of said slide member to said piston element, a piston driving and control disc, a crank-pin interconnecting said disc with said slide member, said casing having a regulator means rotatively adjustable about the longitudinal axis of said casing, and said regulator means having an eccentrically disposed bearing chamber in which said disc is journaled, the normal position of said regulator means being adapted to so dispose said disc that the crank-pin will revolve in a substantially concentric path about the rotor axis without inducing substantial reciprocation of said slide member and piston element, whereas rotative adjustment of said regulator means shifts said disc so that the crank-pin will revolve in an eccentric path about the rotor axis with reciprocating effort upon said slide member and piston element.

2. A pump comprising a casing having a tapered rotor chamber entering one end thereof and disposed eccentric to the longitudinal axis thereof, said casing having diametrically opposed fluid induction and discharge passages respectively entering opposite sides of said rotor chamber, a correspondingly tapered rotor in said rotor chamber, means to rotate said rotor, said rotor having a cylinder bore extending diametrically therethrough in the transverse plane of said induction and discharge passages, a piston element reciprocable in said cylinder bore, said rotor having a slideway in its rearward end parallel to said cylinder bore, a slide member reciprocable in said slideway, a coupling pin adapted. to join midportions of said piston element and slide member, said rotor having a slotway intermediate said cylinder bore and slideway to accommodate movement of said coupling pin, a piston driving and control disc, a crank-pin interconnecting said disc with said slide memher, said casing having regulator means rotatively adjustable about the longitudinal axis of the casing, and said regulator means having an eccentrically disposed bearing chamber in which said disc is journaled, the normal position of said regulator means being adapted to so dispose said disc that the crank-pin will revolve in a substantially concentric path about the rotor axis without inducing substantial reciprocation of said slide member and piston element, whereas rotative adjustment of said regulator means in one direction or the other shifts said disc so that the crank-pin will revolve in an eccentric path about the rotor axis with reciprocating effect upon said slide member and piston element.

3. A pump as defined in claim 2, wherein the means for rotating the rotor comprises a. shaft journaled in the casing and means for so coupling said shaft to the forward end of the rotor as to permit axial movement of the rotor relative to the shaft, and tensional means acting on the rearward end of the rotor whereby to exert forward axial thrust upon said rotor for wear compensating effect.

4. A pump as defined in claim 2, wherein the means for rotating the rotor comprises a shaft journaled in the casing, said rotor having a diametrically transverse channel in its forward end, and said shaft having a cross head so engaged in said channel as to permit axial movement of the rotor relative to the shaft, and tensional means acting on the rearward end of the rotor whereby to exert forward axial thrust upon said rotor for wear compensating effect.

5. A pump as defined in claim 2, wherein the means for rotating the rotor comprises a shaft journalecl in the casing, said rotor having a diametrically transverse channel in its forward end, and said shaft having a cross head so engaged in said channel as to permit axial movement of the rotor relative to the shaft, and spring means within the bearing chamber behind the piston driving and control disc adapted to transmit forward axial thrust through the latter to said rotor for Wear compensating effect.

6. A pump as defined in claim 2, wherein the means for rotating the rotor comprises a shaft journaled in the casing, said rotor having a diametrically transverse channel in its forward end, and said shaft having a cross head so engaged in said channel as to permit axial play of the rotor relative to the shaft, tensional means acting on the rearward end of the rotor whereby to exert forward axial thrust upon said rotor for wear compensating effect, and said rotor having at least one endwise open fluid passage extending longitudinally therethrough whereby fluid pressure against opposite ends of the rotor is equalized.

'7. A pump as defined in claim 2, wherein the means for rotating the rotor comprises a shaft journaled in the casing, said rotor having a diametrically transverse channel in its forward end, and said shaft having a cross head so engaged in said channel as to permit axial movement of the rotor relative to the shaft, spring means within the bearing chamber behind the piston driving and control disc adapted to transmit forward axial thrust through the latter to said rotor for wear compensating efiect, and said rotor having at least one endwise open fluid passage extending longitudinally therethrough whereby fluid pressure against opposite ends of the rotor is equalized.

8. A pump as defined in claim 2, wherein the rotor is provided with at least one endwise open fluid passage extending longitudinally therethrough whereby fiuid pressure against opposite ends of the rotor is equalized.

9. A pump comprising a casing having a rotor chamber entering one end thereof and disposed concentric to the longitudinal axis thereof, said casing having diametrically opposed fluid induction and discharge passages terminating in transverse arcuate ducts respectively contiguous to and communicating with opposite sides of said rotor chamber, said casing having air chambers to respectively communicate with said ducts, a rotor in said rotor chamber, means to rotate said rotor, said rotor having a cylinder bore extending diametrically therethrough in the transverse plane of said induction and. discharge passages and their ducts, a piston element reciprocable in said cylinder bore, said rotor having in an end thereof a slideway parallel to said cylinder bore, a slide member reciprocable in said slideway, means to transmit the movement of said slide member to said piston element, a piston driving and control disc, a crank-pin interconnecting said disc With said slide member, said casing having a regulator means rotatively adjustable about the longitudinal axis of said casing, and said regulator means having an eccentrically disposed bearing chamber in which said disc is journaled, the normal position of said regulator means being adapted to so dispose said disc that the crank-pin will revolve in a substantially concentric path about the rotor axis without inducing substantial reciprocation of said slide member and piston element, whereas rotative adjustment of said regulator means shifts said disc so that the crank-pin will revolve in an eccentric path about the rotor axis with reciprocating effect upon said slide member and piston element.

'10. A pump comprising a casing having a tapered rotor chamber entering one end thereof and disposed eccentric to the longitudinal axis thereof, said casing having diametrically opposed fluid induction and discharge passages terminating in transverse arcuate ducts respectively contiguous to and communicating with opposite sides of said rotor chamber, said casing having air chambers to respectively communicate with said ducts, a correspondingly tapered rotor in said rotor chamber, means to rotate said rotor, said rotor having a cylinder bore extending diametrically therethrough in the transverse plane of said induction and discharge passages and their ducts, a piston element reciprocable in said cylinder bore, said rotor having a slideway in its rearward end parallel to said cylinder bore, a slide member reciprocable in said slideway, a coupling pin adapted to join midportions of said piston element and slide member, said rotor having a slotway intermediate said cylinder bore and slideway to accommodate movement of said coupling pin, a piston driving and control disc, a crank-pin interconnecting said disc with said slide member,

said casing having regulator means rotatively adjustable about the longitudinal axis of the casing, and said regulator means having an eccentrically disposed bearing chamber in which said disc is journaled, the normal position of said regulator means being adapted to so dispose said disc that the crank-pin will revolve in a substantially concentric path about the rotor axis without inducing substantial reciprocation of said slide member and piston element, whereas rotative adjustment of said regulator means in one direction or the other shifts said disc so that the crank-pin will revolve in an eccentric path about the rotor axis with reciprocating effect upon said slide member and piston element.

11. A pump as defined in claim 10, wherein the rotor is provided with at least one endwise open fluid passage extending longitudinally therethrough whereby fluid pressure against opposite ends of the rotor is equalized.

12. A pump as defined in claim 10, wherein the means for rotating the rotor comprises a shaft journaled in the casing and means for so coupling said shaft to the forward end of the rotor as to permit axial movement of the rotor relative to the shaft, and tensional means acting on the rearward end of the rotor whereby to exert forward axial thrust upon said rotor for wear compensating effect.

13. A pump as defined in claim 2, wherein the means for rotating the rotor comprises a shaft journaled in the casing, said rotor having a diametrically transverse channel in its forward end, said shaft having a cross-head so engaged in said channel as to permit axial movement of the rotor relative to the shaft, a journaling and sealing element around said shaft within the casing, said shaft having a conical enlargement and said journaling and sealing element having a conical recess in its inner end to receive said enlargement, and means to exert outward axial thrust upon said shaft to maintain its conical enlargement in sealing relation to said journaling and sealing element.

FRANCISCO A. QUIROZ.

No references cited.

Images