US3138109A - Pump - Google Patents

Description

C. E. BECK June 23, 1964 PUMP 2 Sheets-Sheet 1 Filed April 2, 1963 INVENTOR. CARL E BECK BY 19%,

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United States Patent 3,138,109 PUMP Carl E. Beck, 317 th St., San Francisco, Calif., assignor of ten percent to Carl R. Beck, 'San Carlos, Calif. Filed Apr. 2, 1963, Ser. No. 270,041 8 Claims. (Cl. 103-427) This invention relates to positive displacement pumps in general and specifically this invention relates to positive displacement pumps wtih face-to-face contact blades.

This invention provides a simplified positive displacement pump which is capable of pumping large volumes of fluids at high pressures. This is made possible by a structure including impellers facing each other at an angle of axial inclination, the facing or front surfaces of which are shallow cones with radial grooves formed in the faces thereof. Radial finger shaped blades project radially from each groove, and complement the corresponding radial blade in the groove of the opposing impeller, the number of grooves and positioning on each impeller being identical. Pumping occurs when the impellers with their blades always in face-to-falce contact rotate in a housing, intake occurring as the conical impeller faces move away from each other and discharge occurring as they move toward contact.

The history of the development of pumps and the pumping arts has been a long and gradual one. As the major pump concepts have been discovered with the advent of pumps powered by motors and engines, small advantages and improvements have been sought after and special pumps for special purposes are constantly being designed. However, in the design of modern pumps, particularly for pumping liquids in limited quantities, a number of requirements are evident which must constantly be considered. Specifically, compactness and simplicity are sought after, which requirements in turn dictate a minimum number of parts, moving or stationary. Capacity should be high per power requirement to operate. Practical problems such as case of lubrication and wear must be considered. Most of all, the specific use must be considered, e.g., accuracy in delivering specific amounts of liquid or ability to pump viscous liquids.

With respect to gear type pumps, a satisfactory pump has never been developed which will deliver large volumes of liquid at high pressure yet operate without mechanical difiiculties. Such pumps in the older art operate on the positive displacement principle whereby liquid confined in a cylinder, channel, trough, groove, keyway or other space is forced out by the entrance of solid mating material arranged within the space in regular sequence and short intervals. This requires close working tolerances, particularly in that liquids being forced out by a cylinder, a gear or other component will tend to bypass the component and return to exterior spaces where not confined. Accordingly, in the gear pumps of the past there have tended to be large friction forces and wearing of parts.

In the further development of gear pumps there are generally provided two bodies rotating on axes at an angle to each other, although in the same plane. By fitting one or both forward faces with complex shaped surfaces and/ or by utilizing the cooperation of sliding or matching parts, e.g., blades in slotted discs, acting between the two bodies, a fluid is forced around the impellers thus formed by the constantly changing size and shape of the spaces indicated by the then attitude of the components. Again, however, the cooperating blades, ribs, discs, and other parts, under constant movement relative to each other, and cycle after cycle produces rubbing, galling and other friction movements which soon wear away the parts. From the foregoing it may be seen that there exists a need in the art for a pump which operates simply and with a minimum of contacting parts, whereby the efiiciency of this type of pump can be developed to its maximum extent.

The present invention provides a positive displacement pump of simplified design and operation. Two substantially identical heads having shallow conical opposed faces rotate at an angle to each other, the angle being represented by the angle of inclusion of the cone. The conical faces are further in touching relation at the midpoint between the outlet and intake. The top faces are each radially grooved to a substantial depth and width and preferably in an even number of symmetrical matching positions. A radial blade of a finger shaped cross section adapted to overlap the facing blade in the opposed face at all times is held by each groove. As the blades rotate away from the inlet, the matching fingers spread apart while still touching. As the blades approach the outlet the fingers close together into the portion of the grooves provided, whereby a pumping action is brought about. Only one head need be driven. A valve is also provided which diverts the flow into channels for greater pressure with less flow.

An advantage of the invention is that the pump may be constructed small and compact, the impellers need be only a few inches in diameter for example, yet easily scaled up to bigger sizes. The mechanism is inherently simple since only a few moving parts are required and the tolerances are easily provided. Volume capacity is larger than that of almost any pump of corresponding size or power rating. The pump works nearly independently of liquid viscosity, and so is useful for viscous liquids.

Accordingly, an object of the invention is to provide an improved pump for pumping liquids.

Another object of the invention is to provide an improved positive displacement pump of high capacity and lower power requirements for operation.

Further objects are to provide a construction of maximum simplicity, economy and ease of assembly and disassembly, also such further objects, advantages and capa bilities as will fully appear and as are inherently possessed by the device and invention described herein.

The invention further resides in the combination, construction and arrangement of parts illustrated in the accompanying drawings, and while there is shown therein a preferred embodiment thereof, it is to be understood that the same is illustrative of the invention and that the invention is capable of modification and change and comprehends other details of construction without departing from the spirit thereof or the scope of the appended claims.

Referring now to the drawings, in which:

FIGURE 1 is a vertical cross sectional view with the pump head in elevation, of the pump of the invention, showing the angular disposition of the drive and driven shafts;

FIGURE 2 is a plan view of the pump of the invention taken along the line IIII of FIGURE 1, and looking in the direction of the arrows;

FIGURE 3 is a fragmentary vertical sectional view of the invention diagrammatically showing, in part, the re-.

lationship of parts, particularly the contact of the finger shaped blades at the end of the suction stroke;

FIGURE 4 is a fragmentary vertical cross-sectional view of the invention showing, in part, the relationship of parts, particularly the contact of the finger shaped blades at the end of the discharge stroke;

FIGURE 5 is a fragmentary sectional view of the volume control valve showing the operation when two channels are blocked;

FIGURE 6 is a fragmentary sectional view of the;

volume control valve showing the operation when one channel is blocked; and

FIGURE 7 is a fragmentary sectional view of the :3 volume control valve showing the operation when none of the channels is blocked.

Referring now more particularly to the drawings, and with special reference to FIGURES 1 and 2, there is shown a pump housing of two substantially identical facing members It) and 11 enclosing a pump cavity illustrated generally by the number 12 with shaft housings 12a and 12b. Impeller shafts 14 and 15 are angularly disposed with respect to each other but are in the same vertical plane. Each of the shafts 14 and 15 turn in suitable thrust bearings 16, the shaft 14 being driven by means exterior to the pump (not shown) and the shaft 15 being the driven shaft. The shafts 14 and 15 are set or mounted at an angle of inclination to each other forward from the horizontal, and corresponding to the angle complementing the conical faces of duplicate impellers 17 and 18 mounted for rotation on the ends of shafts 14 and 15.

Duplicate or substantially identical impellers 17 and 18 mounted on shafts 14 and 15, each have shallow conical faces 19 and 20. Since the shafts 14 and 15 are inclined vertically downward, the conical faces 19 and 20 touch along a vertical line 21 as can be seen from FIGURES l and 2, the line of contact 21 being halfway between the inlet and outlet ports 22 and 23 respectively, of the housing 10 and 11, upwardly to and including central ball 24 mounted in central sockets 26 at the center point of each impeller.

A pair of radial grooves 27 of rectangular crosss section are disposed in the faces of each impeller on opposite sides of ball 24, 180 out of phase with each other. In the grooves 27 are anchored identical finger blades 28a, 28b, 28c and 28d. The anchor may be a counterset fastener 30 extending through bore 29 in each impeller, or any other suitable secure but removable means. Each of the finger blades 28a, b, c and d, comprises a horizontal web section 31 flat along the bottom of the groove and an upstanding finger section 32 protruding in a taper from the groove 27 above the conical faces 19 and 20, and gradually diminishing toward the central ball 24. The finger blades 28 are so shaped in cross section that the faces of the contacting blades will undercut the other when the impellers 17 and 18 are fitted together and at the same time, and regardless of the angularity at any particular moment will not touch the edge of the opposite groove. Obviously additional grooves may be utilized in each impeller, but they should be symmetrically distributed radially about the impeller to balance the same and in the same positions on each impeller so that the protruding finger blades of one will fit snugly into the opposing groove of the opposing impeller.

Inlet 22 and outlet 23 are each disposed tangentially at the lower portion of the pump as shown in FIGURE 2, with parallel channels but differing in direction of fiow by 180". While other angles may be used, it will be seen that this position permits suction and discharge strokes of equal maximum length, i.e., each corresponds to approximately one-half revolution of the impellers. The tangential relation further improves the efficiency of the pump.

Any number of blades 28 may be used, but 2, 3, or 4 in each impeller face have been found particularly suited and have sufiicient capacity for any type of service. The blades must be of a suitable size, shape and length and must match or complement each other in length above the conical surface of the impeller so as to fit snugly together in face-to-face touching relationship during the entire pumping cycle. The relationship between matching blades is illustrated in FIGURES 3 and 4 but with the shafts 14 and 15 in axial alignment. As illustrated in FIGURE 3, at the end of the suction stroke, the blades 28 are spread apart the maximum distance, the teeth having gradually spread along the shaped undercut until substantially only the tip portions are touching. In FIGURE 4, at the end of the discharge stroke, the blades 4 intermesh, snugly fitting together in the undercut portion well within the groove 27.

In order to avoid undue wear caused by the lateral and axial pressure on impellers 17 and 18, a Water cushion is provided in the space 51 between the respective impellers and the inside surface of each portion 10 and 11 of the housing. Specifically, thrust bearings 16 are constructed to hold the impellers in spaced relation from the housing 11 so that seepage of fluid from cavity 44 gradually builds up an amount of pumping fluid in the space 51 having a pressure equal to that in the pumping cavity 44. This fluid pressure acts as a cushion against lateral and axial forces and resiliently holds the impellers from the cavities in portions 10 and 11 of the housing with a minimum of wear.

Valve means 33 for regulating the pressure of the liquid flowing from the pump is seen at the top of the pump on the opposite side from outlet and inlet ports 22 and 23. The valve comprises a simple journaled rotating body member 34 at the head of three inlet passages 36, 3'7 and 38 extending upward from the discharge side of the pump just above the chamber 44 and formed by the partition members 40, 41 and 42. The journal is between opposing halves 43 of housing 11 so that the valve means 33 extends across the space 44 between impellers when they are furthest apart. The body member 34 is generally in the form of a segment of a circle in cross section, the rounded portion 46 sealing off passages 36, 37 and 38 when in facing position. By turning the body 34 with the handle 47 through the journal 48, one, two or three of the passages can be opened. The passages open in the direction of the arrows. The flow through the passages 36, 37 and 33 is delivered to passage 49 which empties behind the blade on the intake side as shown in FIGURE 2.

In the operation of the pump, liquid is taken in at inlet 22 when the shaft 14 is turned in a counterclockwise direction. The pump need not be primed in any way, and being of the positive displacement type, gases as well as liquids will be moved as long as tolerances are maintained reasonably close. Since the relative positioning of the blades 28 are moving from a position similar to FIGURE 4 to that shown in FIGURE 3, as they pass inlet 22, liquid is drawn in to take up the space opened up by the rotation. As the blades 28 approach the point at which they will be farthest apart, shown in FIGURE 3, the second set of blades approach the point at which they are closest together, shown in FIGURE 4. When the second set in turn passes upwardly, it retains the water pulled in by the first set of blades until the first set reaches the discharge side of the pump, at which time the second set is in the compression stage and forces water out the outlet 23.

In the operation of the valve 33, both the pressure and the volume or amount of flow at outlet 23 is regulated by turning the handle 47 in a counterclockwise direction. More specifically, in the normal operation of the pump the valve handle is turned to the off position as shown in FIGURE 2, i.e., there is no flow at all possible through the channels 36, 37 and 38 because the handle 47 is turned to the vertical off position, turning the surface 46 of the valve against each of the channel outlets into backside 49. However, when it is desired that the pump deliver less flow at greater pressure, the handle 47 is turned to the horizontal to open one, two or three channels, namely channels 36, 37 or 38. As seen from FIGURE 5, when channel 36 is open the pressurized liquid being forced counterclockwise by blades 28 is free to migrate or pass back toward the outlet 49. This means that the volume is only that from the land 41 to the outlet 23 and that the pressure has the shortened distance, i.e., from land 41 to the outlet 23 to build up pressure. When channels 36 and 37 are both opened, a portion of the flow is diverted behind the blade 28, and both pressure and volume are only those increments represented by the distance from land 41 to outlet 23.

Likewise, when all three channels 36, 37 and 38 are open, the volume and pressure is still further reduced. However, it should be understood that the backward flow through any or all of passages 36, 37 and 38, does not completely bleed out the flow since the following blade 28 passes the inlet 22 as the first one is passing channels 36, 37 and 38.

I claim:

1. In a positive displacement pump the combination of a housing having an inlet and an outlet, two opposed impellers mounted for rotation therein, said impellers each having shallow conical opposed faces and mounted axially at an angle to each other, said angle being the angle of inclusion of the cone, said impellers being in full radial contact at the midpoint between the inlet and outlet, and not more than four fixed radial blades set in the bottom of grooves on each conical impeller face, said blades having substantially identical curved faces c0- operating in continuous moving contact with identical blades set in grooves on the opposed face, said grooves being deep enough to receive the entire projecting blades in full radial face to face contact at the time of said full radial contact between the conical faces.

2. In a positive displacement pump the combination of a housing having an inlet and an outlet, two opposed impellers mounted for rotation therein, said impellers each having shallow conical opposed faces and mounted axially at an angle to each other, said angle being the angle of inclusion of the cone, said impellers contacting each other radially at the midpoint between the inlet and outlet, and not more than four fixed radial, symmetrical blades projecting from and secured in the bottom of radial grooves in each conical face of said impellers, said blades complementing the blades and grooves on the opposed face, providing continuous radial contact of the blades during rotation, said grooves being deep enough to receive the entire projecting blades in full radial face to face contact at the time of said full radial contact between the conical faces.

3. In a positive displacement pump the combination of a housing having an inlet and outlet ports, two opposed impellers mounted for rotation in a chamber within said housing and with their bottom faces spaced from said chamber, said impellers each having opposed shallow conical faces mounted in axial angularity, the angle being the angle of inclusion of the cone with said impellers fully contacting each other radially at the midpoint between the inlet and outlet ports, a plurality of radial symmetrical grooves thereon, said grooves in said opposed conical faces matching each other, and a plurality of fixed blades having shaped faces secured in the bottom of and projecting above said grooves, said blades being so shaped to maintain touching full radial contact at all positions of said impellers with the substantially identical blades on the opposed face and to fit in full radial face to face contact within said opposing grooves when said impellers are approaching the intake.

4. The positive displacement pump of claim 3 in which said inlet and said outlet ports are both tangential to the pumping chamber in said housing for the impellers and at an angle of with respect to each other, to provide inlet to the impellers during the first quadrant and outlet therefrom during the last quadrant, and provide tan-- gential flow to and from said pumping chamber.

5. The positive displacement pump of claim 3 where the impellers are mounted on rotating shafts and where one shaft is a driving shaft.

6. The positive displacement pump of claim 3 in which said blades'have substantially identical carefully shaped faces finger-like cross sections which overlap and maintain touching full radial contact at all times in moving engagement to full radial face to face contact at the point of of full radial contact between the said impellers.

7. The positive displacement pump of claim 3 in which said blades are two in number on each impeller face.

8. The positive displacement pump of claim 3 in which said grooves on the impeller conical faces are further square in cross section and said blades occupy less than one-half the width thereof, to provide space for the continuous change in the full radial overlapping contact of the opposed blades due to the angularity of rotation, up to the full radial face to face contact at the point of full radial contact between the two conical faces.

References Cited in the file of this patent UNITED STATES PATENTS 32,372 Jones et a1. May 21, 1861 769,082 Hendricks Aug. 30, 1904 1,376,397 Bylger May 3, 1921 2,482,325 Davis Sept. 20, 1949 2,674,952 Jacobsen Apr. 13, 1954 3,088,658 Wagenius May 7, 1963 3,093,961 Pisa June 18, 1963 FOREIGN PATENTS 9,318 Great Britain of 1885 420,501 Great Britain Dec. 3, 1934

Claims (1)

1. IN A POSITIVE DISPLACEMENT PUMP THE COMBINATION OF A HOUSING HAVING AN INLET AND AN OUTLET, TWO OPPOSED IMPELLERS MOUNTED FOR ROTATION THEREIN, SAID IMPELLERS EACH HAVING SHALLOW CONICAL OPPOSED FACES AND MOUNTED AXIALLY AT AN ANGLE TO EACH OTHER, SAID ANGLE BEING THE ANGLE OF INCLUSION OF THE CONE, SAID IMPELLERS BEING IN FULL RADIAL CONTACT AT THE MIDPOINT BETWEEN THE INLET AND OUTLET, AND NOT MORE THAN FOUR FIXED RADIAL BLADES SET IN THE BOTTOM OF GROOVES ON EACH CONICAL IMPELLER FACE, SAID

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