US3169485A

US3169485A - Pump construction

Info

Publication number: US3169485A
Application number: US320792A
Authority: US
Inventors: Harry J Sadler; Ernest E Cook
Original assignee: HYPRO ENGINEERING Inc
Current assignee: HYPRO ENGINEERING Inc
Priority date: 1963-11-01
Filing date: 1963-11-01
Publication date: 1965-02-16
Anticipated expiration: 1982-02-16

Description

Feb. 16, 1965 H. J. SADLER ETAL PUMP CONSTRUCTION 2 Sheets-Sheet 1 Filed Nov. 1, 1965 lllll Ill:

INVENTORS. HARRY J. SADLEF? ERNES T E. COOK ATTORNEYS Feb. 1965 H. J. SADLER ETAL PUMP CONSTRUCTION 2 Sheets-Sheet 2 Filed Nov. 1, 1963 INVENTORS. HARRY J SADL ER EgNEST E. COOK ATTOPNE YS United States Patent Ofi'ice 7 means Patented Feb. 16, 1965 3,16%,485 PUT/ll SGNSTRUCHGN Harry J. Sadler, Minneapolis, and Ernest E. Cook, {Icon Rapids, Minn, assignors to Hypro Engineering, Inc., Minneapolis, Minn a corporation of Minnesota Filed Nov. 1, 1963, Ser. No. 329,792 4 Claims. (Cl. 103-4) Our invention relates generally to rotary fluid pumps and more particularly to fluid pumps of this character which are of relatively low-capacity and small of size.

Still more specifically, our invention relates to improvements in rotors for pumps of the type above described whereby the capacity of pumps incorporating same is materially increased.

Still more specifically, our invention relates to fluid pumps of the type utilizing flexible resilient rubber-like vane impeller elements. It is well known that pumps of this character have good self-priming properties, are able to eh'rciently move abrasive materials and are relatively quiet. On the other hand, because or" the well-known tendency of the several vanes of such rotors to flex rearwardly and radially inwardly responsive to similar forced movements of adjacent vanes (caused by engagement with the cylindrical side walls of the pump as they approach the high pressure side of the pump), such pumps have relatively low pressure limits. Roller pumps, on the other hand, are known to achieve higher pressures and to have lower starting torque.

The primary object of our invention is the provision of a pump having a rotor which incorporates the benefits of both the flexible vane and roller-type pumps.

More specifically, it is the object of our invention to provide a rotor which has a plurality of circumferentially spaced flexible resilient rubber-like pocket-forming impeller elements, at least one of said pockets having mounted and guided therein for limited reciprocal movements generally radially or" said rotor a relatively rigid impeller element which is in constant substantial engagement with the cylindrical wall of the casing during rotation of the rotor, and which tends to function as a check valve whereby to break up any tendency of the succeeding flexible resilient impeller elements to flatten out and bypass fluid under progressively higher pressures.

A still further object of our invention is the provision of a device of the class above described which incorporates a minimum of working parts and is relatively inexpensive to produce.

A further object of our invention is the provision or" a pump of the class described which, while retaining the good self-priming features of a conventional rubber impellet-type pump, is capable of operating under pressures far in excess of that achievable through the mediurn of such pumps.

A still further object of our invention is the provision of a pump which is considerably quieter than conventional roller-type pumps.

A still further object of our invention is the provision of a pump of the class immediately above described which is capable of pumping abrasive materials With greater efliciency than a roller-type pump.

The above and still further objects of our invention will become apparent from the following detailed specification, appended claims and attached drawings.

Referring to the drawings, wherein like characters indicate like parts throughout the several views:

FIG. 1 is a View in end elevation of a pump constructed in accordance with our invention;

PEG. 2 is a view in side elevation of the structure of FIG. 1;

FIG. 3 is a view in vertical section as seen from the line 3-3 of FIG. 2 on an enlarged scale, some parts being broken away;

FIG. 4 is a vertical section taken on the line 4-4 of FIG. 1 on an enlarged scale;

FIG. 5 is a view in end elevation of the rotor of our pump, removed from the drive shaft;

FIG. 6 is a view in side elevation of our rotor, mounted on the shaft, portions of which are broken away and shown in section;

FIG. 7 is a view in section taken on the line 7-7 of FIG. 5 and FIG. 8 is an exploded view in of our novel rotor.

Referring with greater particularity to the drawings, the housing of our novel pump, identified in its entirety by the numeral it defines a chamber ll having spaced parallel end walls 12, a cylindrical side wall 13 and diametrically opposed inlet and

outlet ports

14 and 15 respectively which communicate with said chamber 11. In conventional manner, the housing 10 is provided with a removable end plate 16. Journalled for rotation in bearing bosses 17, in radially offset relation to the axis of the cylindrical chamber 11, is a shaft 18 having mounted fast thereon for common rotation within the chamber 11 a rotor 19. V

Rotor 19 comprises a diametrically enlarged hub 29, which is divided into two parts, namely, a relatively rigid tubular core element 21 and a relatively flexible radially outer portion 22. Preferably the core element 21 is formed from suitable steel, whereas the outer portion 22 is formed from rubber-like material capable of being bonded to the core element 21. Core element 2i, on the other hand, is secured fast to the shaft 18 in any suitable manner.

The rotor 19 also includes a plurality of circumferentially spaced flexible resilient vane-like impeller elements 23 which are, preferably and as shown, formed integrally with the radially outer portion 22 of'the rotor 1?. As shown, the normal radial dimensions of the vanes 23 are such that their radial outer limits 23a are in constant sweeping engagement with the cylindrical side wall 13 of the chamber 11 during rotation thereof and are consequently flexed rearwardly in vmying degrees upon rotation of said rotor 19. The entire rotor 19 extends between the end walls 12 of the chamber ll, and consequently the vanes 23 define therebetween circumferentially spaced pockets 24 of varying capacity depending upon their position within the chamber 11.

As above indicated, rotors of the type immediately above described are restricted in capacity because of the tendency of all of the vanes to collapse inwardly in progression, much as though they were in actual engagement with each other (as in the case of dominoes or any objects standing on end in lined up relationship). In order to overcome this tendency and to greatly increase the capacity of pumps equipped with rotors having exible rubberlike vanes, the rotor 19 is formed so as to provide certain circumferentially spaced pockets 24a which are of greater circumferential dimension than the remaining pockets 24 so as to accommodate check valve-acting relatively rigid impeller elements 25. Impeller elements 25, as shown, are in the nature of relatively rigid rollers which extend between the end walls 12 which are mounted for limited reciprocal movements upon rotation of the rotor 19 while in constant contact with the cylindrical side wall 33. As shown, the pockets 24a are diametrically opposed and, to facilitate reciprocal movements of the rollers 25, each thereof is provided with an axially extended radially outwardly opening channel 26 which is formed in the hub 20.

Preferably, and as shown, in order to prevent undue distortion and wear upon the rubber-like portion 22 of the perspective of some parts hub 29, the trailing edges of the channels zd have vult a t V canized thereto axially extended radially projecting bearing flanges 27. Referring particularly to FIG. 8, it will be seen that the bearing flanges 27 have axially spaced radially inwardly projecting legs 28 which are press fit in axially extended radially outwardly opening diametrically opposed slots 29 in the relatively rigid core element 21.

Our invention has been thoroughly tested and found to be completely satisfactory for the accomplishment of the above objects, and while I have shown and described a preferred embodiment, I wish it to be specifically under stood that the same is capable of modification Without departure from the spirit and scope of the appended claims.

What is claimed is:

1. In a fluid pump, a housing defining:

(a) a chamber having spaced parallel end walls and a cylindrical side wall, and having circumferentially spaced inlet and outlet ports communicating with said chamber,

(b) a shaft journalled for rotation in at least one of said end walls on an axis radially offset from the axis of said chamber,

(0) a rotor fast on said shaft within said chamber,

said rotor comprising:

(1) a hub concentric with said shaft and extending between said end walls,

(2) a plurality of circumferentially spaced radially outwardly projecting flexible resilient vanelike impeller elements fast on said hub,

(3) said impeller elements also extending between said end walls and having constant sweeping engagement with said cylindrical side wall during rotation thereof and being flexed rearwardly in varying degrees during such rotation, (4) said impeller elements defining a plurality of circumferentially spaced axially extended pockets of varying capacity, (d) one of said pockets defining a circumferentially and radially enlarged channel, and

(e) a relatively rigid impeller element mounted and guided in said channel for limited generally radial reciprocal movements with respect to said rotor and which during rotation of said rotor is in substantially content engagement with said cylindrical side wall,

(7) the trailing side wall of said channel guiding said impeller element in its generally radial reciprocal movements and positively retaining said impeller element within said channel during said rotation.

2. The structure defined in claim 1 in which the channel defined by said one of said pockets extends between the end walls of said housing and in which said impeller element comprises an elongated roller receivable in said channel.

3. The structure defined in claim 2 in which the radially outer portion of said hub and the vane-like impeller elements carried thereby are integrally formed from rubber-like material and in which the trailing side wall of said channel is formed to provide a relatively rigid generally radially extended bearing flange for said roller.

4. The structure defined in claim 3 in which (a) said hub comprises a generally cylindrical relatively rigid core element which is diametrically enlarged with respect to said shaft,

(b) the peripheral portion of said core element being bonded to the rubber-like portion of said hub, and

(c) in which said bearing flange is carried by and France Jan. 6, 1921 Great Britain Feb. 28, 1939

Claims

1. IN A FLUID PUMP, A HOUSING DEFINING: (A) A CHAMBER HAVING SPACED PARALLEL END WALLS AND A CYLINDRICAL SIDE WALL, AND HAVING CIRCUMFERENTIALLY SPACED INLET AND OUTLET PORTS COMMUNICATING WITH SAID CHAMBER, (B) A SHAFT JOURNALLED FOR ROTATION IN AT LEAST ONE OF SAID END WALL ON AN AXIS RADIALLY OFFSET FROM THE AXIS OF SAID CHAMBER, (C) A ROTOR FAST ON SAID SHAFT WITHIN SAID CHAMBER, SAID ROTOR COMPRISING: (1) A HUB CONCENTRIC WITH SAID SHAFT AND EXTENDING BETWEEN SAID END WALLS, (2) A PLURALITY OF CIRCUMFERENTIALLY SPACED RADIALLY OUTWARDLY PROJECTING FLEXIBLE RESILIENT VANELIKE IMPELLER ELEMENTS FAST ON SAID HUB, (3) SAID IMPELLER ELEMENTS ALSO EXTENDING BETWEEN SAID END WALLS AND HAVING CONSTANT SWEEPING ENEGAGEMENT WITH SAID CYLINDRICAL SIDE WALL DURING ROTATION THEREOF AND BEING FLEXED REARWARDLY IN VARYING DEGREES DURING SUCH ROTATION, (4) SAID IMPELLER ELEMENTS DEFINING A PLURALITY OF CIRCUMFERENTIALLY SPACED AXIALLY EXTENDED POCKETS OF VARYING CAPACITY, (D) ONE OF SAID POCKETS DEFINING A CIRCUMFERENTIALLY AND RADIALLY ENLARGED CHANNEL, AND (E) A RELATIVELY RIGID IMPELLER ELEMENT MOUNTED AND GUIDED IN SAID CHANNEL FRO LIMITED GENERALLY RADIAL RECIPROCAL MOVEMENTS WITH RESPECT TO SAID ROTOR AND WHICH DURING ROTATION OF SAID ROTOR IS IN SUBSTANTIALLY CONTANT ENGAGEMENT WITH SAID CYLINDRICAL SIDE WALL, (F) THE TRAILING SIDE WALL OF SAID CHANNEL GUIDING SAID IMPELLER ELEMENT IN ITS GENERALLY RADIAL RECIPROCAL MOVEMENTS AND POSITIVELY RETAINING SAID IMPELLER ELEMENT WITHN SAID CHANNEL DURING SAID ROTATION.