US3255701A - Vortex pump - Google Patents

Description

June 14, 1966 T. E. BENNETT ETAL 3,255,701

VORTEX PUMP 5 Sheets-Sheet 1 Filed Sept. 30, 1963 &

INVENTORS VAL 5. LOBA/VOFF THOMAS E'. BENNETT ATTO EY June 14, 1966 T. E. BENNETT ETAL VORTEX PUMP 5 Sheets-Sheet 2 Filed Sept. 30, 1963 INVENTORS 48;, if VAL S. LOBANOFF THOMAS E BENNETT TO RN June 14, 1966 T. E. BENNETT ETAL 3,255,701

VORTEX PUMP Filed Sept. 30. 1963 5 Sheets-Sheet 5 FIG. 4

36 IO PUMP DISCHARGE LINE REsERvoIR PUMP SUPPLY LINE PUMP 35 F/Gx5 INVENTORS VAL SI LOBA/VOFF THOggAS E BENNETT ATT RNEY United States Patent 3,255,701 VORTEX PUMP Thomas E. Bennett, Massapequa, N.Y., and Val S. Loban- 01f, Washington, N.J., assignors to Ingersoll-Rand Company, New York, N.Y., a corporation .of New Jersey Filed Sept. 30, 1963, Ser. No. 314,576 6 Claims. (Cl. 103104) This invention relates to pumps and more particularly to a pump which is capable of pumping two or three phase pumping mediums, such as liquid and solids, or slurry, liquid and gas, or liquids, solids and gas.

Heretofore, it has been known that when rotary pumps are utilized to pump a pumping medium comprising a liquid containing entrained solid material therein, the solid material, usually moving at greater velocities, exerts an abrasive action upon the impeller, which abrasive action drastically reduces the life of the impeller. In addition standard rotary pumps require a high net pump suction head in order to deliver a high discharge head. This means that the pump suction reservoir must be positioned high above the pump in order to provide the required net pump suction head. The location of the pump suction reservoir therefore, when standard rotary pumps are employed, is a complicated problem which often necessitates an expensive solution.

It is the general object of the present invention to avoid and overcome the foregoing and other difliculties of and objections to prior art practices by the provision of a pump which is capable of pumping two or three phase pumping mediums.

Another object of the present invention is to reduce the pump inlet velocities of the pumping medium and thus reduce the resultant abrasive action of the solids entrained in the pumping medium with attendant reduced pump wear.

Still another object of the present invention is to pump by centrifugal vortex having uniform velocities at both sides of the pump casing.

Yet another object of the present invention is to provide a pump with complete hydraulic balance having zero axial thrust, reduced vibration with resultant reduced bearing load and attendant greater bearing life.

A further object of the present invention is to provide a pump suitable for low net pump suction head and high discharge head.

The aforesaid objects of the present invention, and other objects which will become apparent as the de scription proceeds, are achieved by providing a centrifugal pump for pumping a pumping medium of liquid, solids and gas. The centrifugal pump has a casing. Impeller means rotatably mounted in the casing for pumping the pumping medium. The impeller means defining with the casing two pumping chambers to receive the pumping medium on opposite sides of the impeller means. In addition inlet means are provided associated with the pumping chambers for admitting the pumping medium in the pumping chambers at low inlet velocities thereby substantially reducing abrasive action by the solids on the impeller means.

For a better understanding of the present invention reference should be had to the accompanying drawings, wherein like numerals of reference indicate similar parts throughout the several views and wherein:

FIGURE 1 is a side elevational view partly in section of a centrifugal pump embodying the present invention illustrating an impeller having vanes back to back;

FIGURES 2 and 3 are views similar to FIGURE 1 illustrating alternative embodiments of the present invention;

FIGURE 4 is a view similar to FIGURE 1 illustrating a multi-stage pump embodying the present invention;

3,255,701 Patented June 14, 1966 'ice FIGURE 5 is a diagrammatic view illustrating a pumping system.

Although the principles of the present invention are broadly applicable to rotary pumps employed in pumping liquids, and solids; and liquids, solids and gases; the present invention is particularly adapted for use in conjunction with centrifugal pumps and hence it has been so illustrated and will be so described.

With specific reference to the form of the present invention illustrated in the drawings, and referring particularly to FIG. 1, a centrifugal pump (FIG. 1) is indicated generally by the reference numeral 10. The centrifugal pump 10 has a casing 12.

Impeller means, such as an impeller 14 (FIG. 1) is disposed in the casing 12. The impeller 14 is rigidly secured by a key (not shown) or other suitable means to a driving shaft 16 (FIG. 1) which driving shaft 16 extends into the casing 12. The driving shaft 16 is rotated by any number of well known methods such as a standard electric motor (not shown), and thereby imparts rotary motion to the impeller 14.

The impeller 14 associates with an internal portion or wall 18 (FIG. 1) of the casing 12 to form two pumping chambers 20 and 22 (FIG. 1) and chambers 20a and 20b of FIGS. 2 and 4 respectively.

In order to admit a pumping medium composed of a liquid containing solids immersed therein, or slurry, liquid and gas, or liquid, solids and gas, in the pumping chambers 20 and 22, each of the pumping chambers 20 and 22 are supplied with inlet means such as inlets 24 and 26 (FIG. 1) in opposed end Walls, as shown. Inlet 24 communicates with the pumping chamber 20 through a passage 28, and the inlet 26 communicates with the pumping chamber 22 through a passage 30. The inlets 24 and 26 are wide (as shown in FIG. 1) and are otherwise unrestricted to allow heavy slurries to pass unrestricted therethrough. In addition the central inlet passages 28 and 30 (FIG. 1) of the inlets 24 and 26, directly adjacent to the pumping chambers 20 and 22, are of relatively large inside diameters and are provided with circular walls 32 and 34 as shown in FIGURE 1. It will be understood by those skilled in the art that the circular walls 32 and 34 will allow easier flow of the pumping medium through the inlet passages 28 and 30, to reduce radial pump loads and thus improve the overall efiiciency of the pump 10. Further the circular walls 32 and 34 will permit the smooth passage and admittance of the pumping medium into the pumping chambers 20 and 22 with a resultant reduction of the abrasive action of the solids in the pumping medium on the Walls 32 and 34 and attendant decrease in the pump friction loads.

In order to drive the pumping medium, the impeller 14, which is of a thickness substantially equal to that of wall 18, is provided with driving means and opposite faces carrying vanes 67 FIG. 1) formed between a series of angularly spaced recesses disposed on both sides of the impeller 14. The impeller 14 and the vanes 37 are recessed into the internal portion 18 of the casing 12. Therefore, although the impeller 14 and the vanes 37 communicate with the pumping chambers 20 and *22, the impeller -14 and the vanes 37 are wholly outside of the pumping chambers 20 and 22 thereby substantially reducing contact between the pumping medium and the vanes 37 with resultant reduction of abrasive action and wear on the impeller 14 and the vanes 37 by the solids and slurry in the pumping medium with attendant prolonging the life of the pump.

In order to discharge the pumping medium from the pumping chambers 20 and 22, outletmeans, such as an outlet 40 is provided. The out-let 40 communicates with the pumping chambers 20 and '22. The outlet diameter is equal to the diameter of the pump-ing chamber 20 and ot the pumping chamber 22 and is not otherwise restricted to allow the smooth discharge of the slurries and the solids contained in the pumping medium.

It will be understood by those skilled in the art that the combination of the large twin or split inlet single outlet will result in the generation of a large vortex diameter and high outlet velocities of the pumpingmedium, with attendant higher pump discharge heads for a given impeller diameter. Since this centrifugal pump 10 can generate high discharge heads it can be effectively utilized in pumping systems where the pumping medium is supplied, through conduit means such as a pipe 35, to the pump inlets 20 and 22, from a supply reservoir, such as a tank 36 (FIG. 5), with low net pump suction head. With the present invent-ion the pumping medium can be supplied to the centrifugal pump '10 with low net pump suction head, and the centrifugal pump can still discharge the pumping medium'with a high pump discharge head. Further, it can be seen that the reduced inlet velocities of the flow of the pumping medium, results in decreased abrasive action by the solids in the pumping medium against the central inlet passages 28 and 30 andthe vanes 37 and attendant decreased wear and longer pump life.

It will be understood by those skilled in the art that as shown in FIG. 1, the location of the impeller 14 in the center of the casing l12, with the pumping chambers and 22 disposed on opposite sides of the impeller '14, will resuit in the centrifugal pump 10 being completely hydraulically balanced having zero axial thrust, with attendant reduction of the bearing load and lengthening bearing life.

As shown in FIG. 1, the impeller 14 is the only rotating part in the wet area of the centrifugal pump 10, and all wear rings have been eliminated thereby increasing the pump efii-ciency. In order to provide lubricant between the outer surface 38 of the impeller ;14 and the mating internal surface or cylindrical bore 41 the internal portion 18 of the casing 12 a conduit 42 ('FIG. 1) is disposed in the internal portion 18 of the casing 12. The conduit 42 communicates with the inlets 24 .and 26 to supply pumping fluid to lubricate the outer surface 38 of the impeller.

Alternative embodiments It will be understood by those skilled in the art that alternatively, as shown in FIG. 2, a vortex impeller 14a with rings or means 44a can be provided. The vortex impeller rings 44a have vanes 46a and are attached to an impeller hub 48a by ribs 50a located at the outer periphery of the vortex impeller rings 44a. The driving torque is transmitted to the vortex impeller 14a through the shaft 16a to the impeller hub 48a and through the ribs 50a to each of vortex impeller rings 4411'. The vortex impeller rings 44a are mounted symmetrically on each side of the impeller hub 38a. This arrangement produces equal vortexes and pump velocities for ultimate pump efficiency.

Further alternatively as shown in FIG. 3, the impeller 14b has rings or means 44b, with vanes 46b, which are attached to an impeller hub 48b by radial ribs 50b located in the central inlet passages 28b and b. It should be understood that impeller 14b may be divided transverse to its axis of rotation, each portion thereof would include one of the rings or means 44b.

Alternatively as shown in EFIG. 4, the principle of the present invention can be applied to a multi-stage pump. The impeller 14c cooperates with an internal portion 1*8c of the casing 120 to define a low pressure pumping chamber 520 and a high pressure pumping chamber 540. The pumping medium, such as a liquid having solids entrained therein; or slurry, liquid and gas; or liquid solids and gas; is supplied through the inlet 560 to the low pressure pumping chamber 52c for the first stage of the pumping cycle. The vanes 600 on the impeller 14c communicating with the low pressure chambers 52c move the pumping medium from the low pressure pumping chamber 520 through a wide :l'low passage 580 into the high pressure pumping chamber 540 for the second stage of the pumping cycle. The vanes 620 on the impeller 14c communicating with the high pressure chamber 540 move the pumping medium from the high pressure pumping chamber 540 and discharge the pumping medium through the outlet 640 of the centrifugal pump 10c. All the wet passages are circular and are not restricted allowing heavy slurries to pass through the pump 10s unrestricted and to reduce radial loads and improve pump efficiency.

The impeller 14c and the vanes 60c and 620, for the respective pumping chamber 520 and 540, are recessed in the internal portion of the casing 12c. The vanes 60c and 62c are therefore removed from the pumping chambers 52c and 540 thereby substantially reducing abrasive action between the solids in the pumping medium and the vanes 60c and =62c. 'Ihus it will be understood that the two-stage pump 10c can generate high discharge pressures while pumping a pumping medium composed of a liquid, solids and gases, and at the same time substantially reducing the abrasive action of the solids on the impeller 140.

Still further alternatively a multi-stage pump can be provided which multi-stage pump would have any number of pumping chambers in series. A series of impellers rotatably mounted in the casing defines with the casing, the series of pumping chambers. Essentially the multistage pump would be a series of the hereinbefore described two-stage pumps shown in FIG. 4.

It is understood that each of the pumping chambers of the multi-stage pump is under higher pumping pressure than the precedent pumping chamber. The impellers, each of which impellers define and communicate with two pumping chambers, drive a pumping medium, such as liquid and solids, or slurry, liquid and gas, or liquid, solid and gas, from one pumping chamber to the next adjoining pumping chamber through conduit means, such as a series of wide circular conduits provided in the pump casing. The impellers are recessed in the pump casing and are substantially removed from the pumping chambers to reduce abrasive action by the solids in the pumping medium on the impellers. It will be understood by those skilled in the art that as the pumping medium is driven from pumping chamber to pumping chamber and the number of the pumping chambers are increased, the pumping medium will be imparted with increasing velocities and increasing pressures. At increased velocities and pressures the abrasive action of the solids in the pumping medium will be likely to cause great damage to interfering elements of the pump. It is therefore understood that the wide circular shape of the conduits and the impellers being recessed in the casing and being removed from the pumping chambers, will greatly reduce the abrasive damage to the conduits and to the impellers.

Inlet means, such as a wide inlet and outlet means, such as a wide outlet, are provided. The inlet communicating with the first of the series of pressure chambers, which pressure chamber is under the lowest pumping pressure, to admit the pumping medium in the multistage pump, andthe outlet communicating with the last of the series of pressure chambers, which last pressure chamber is under the highest pumping pressure of the series of pumping chambers, to discharge the pumping medium from the multi-stage pump.

It will be recognized by those skilled in the art that the objects of the present invention have been achieved by providing a pump capable of pumping two or three phase pumping mediums. The pump reduces inlet velocities thus reducing the resultant abrasive action of the solids entrained in the pumping medium with attendant reduced pump wear. In addition the pump has uniform velocities at both sides of the pump casing resulting in complete hydraulic balance with attendant greater hearing life. Further the pump is able to discharge the pumping medium with a high discharge head even if the pumping medium is delivered to the pump inlet with low net pump suction head.

While in accordance with the patent statutes a preferred and alternative embodiments of the present invention have been illustrated and described in detail, it is to be particularly understood that the invention is not limited thereto or thereby.

We claim:

1. A centrifugal type vortex pump comprising:

a casing having a pair of axially spaced pump chambers each defined by one of a pair of opposed end walls, a smooth surface annular wall and a wall axially spaced between the pair of opposed end walls and common to both chambers;

each of the chambers having an inlet in the associated wall of the pair of opposed end walls to receive a medium to be pumped, and a peripheral outlet in the associated annular wall for such pumped medium;

the wall common to the pair of chambers having a cylindrical bore therethrough axially alined with the pair of chambers;

an impeller rotatably disposed in the cylindrical bore and having a pair of faces each in unrestricted communication with one of the axially spaced pump chambers for producing a vortex flow in such chambers when the impeller is rotated; and

the impeller having a diameter substantially equal to the diameter of the cylindrical bore and a thickness substantially equal to the thickness of the wall common to both pump chambers.

2. The centrifugal type vortex pump in accordance with claim 1; wherein each of the pair of impeller faces includes an annular series of spaced recesses therein providing a series of spaced vanes each between two of the recesses, the vanes being wholly outside of the pump chambers.

3. The centrifugal type vortex pump in accordance with claim 1; wherein the casing is provided with an outlet in communication with the outlets of both of the pair of pump chambers to provide a common discharge for such pumped medium. 4.. The centrifugal type vortex pump in accordance with claim 1; wherein the casing has an inlet in communication with the inlets of .both of the pair of pump chambers and adapted to receive a medium to be pumped to provide such medium to both of the pair of pump chambers. 5. The centrifugal type vortex pump in accordance with claim 4; and

the casing has an inlet in communication with the inlets of both of the pair of pump chambers and an outlet in communication with the outlets of both of the pair of pump chambers to flow connect such pump chambers in parallel with one another.'

6. The centrifugal type vortex pump in accordance with claim 1; wherein the inlet of one of the pair of pump chambers is in communication with the outlet of the other of the pair of pump chambers to flow connect such pump chambers in series With one another.

References Cited by the Examiner UNITED STATES PATENTS SAMUEL LEVINE, Primary Examiner.

HENRY F. RADUAZO, Examiner.

Claims (1)

1. A CENTRIFUGAL TYPE VORTEX PUMP COMPRISING: A CASING HAVING A PAIR OF AXIALLY SPACED PUMP CHAMBERS EACH DEFINED BY ONE OF A PAIR OF OPPOSED END WALLS, A SMOOTH SURFACE ANNULAR WALL AND A WALL AXIALLY SPACED BETWEEN THE PAIR OF OPPOSED END WALLS AND COMMON TO BOTH CHAMBERS; EACH OF THE CHAMBERS HAVING AN INLET IN THE ASSOCIATED WALL OF THE PAIR OF OPPOSED END WALLS TO RECEIVE A MEDIUM TO BE PUMPED, AND A PERIPHERAL OUTLET IN THE ASSOCIATED ANNULAR WALL FOR SUCH PUMPED MEDIUM; THE WALL COMMON TO THE PAIR OF CHAMBERS HAVING A CYLINDRICAL BORE THERETHROUGH AXIALLY ALINED WITH THE PAIR OF CHAMBERS; AN IMPELLER ROTATABLY DISPOSED IN THE CYLINDRICAL BORE AND HAVING A PAIR OF FACES EACH IN UNRESTRICTED COMMUNICATION WITH ONE OF THE AXIALLY SPACED PUMP CHAMBERS FOR PRODUCING A VORTEX FLOW IN SUCH CHAMBERS WHEN THE IMPELLER IS ROTATED; AND THE IMPELLER HAVING A DIAMETER SUBSTANTIALLY EQUAL TO THE DIAMETER OF THE CYLINDRICAL BORE AND A THICKNESS SUBSTANTIALLY EQUAL TO THE THICKNESS OF THE WALL COMMON TO BOTH PUMP CHAMBERS.

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