Patent Application
20180119698
The field of the present invention is pumps which are magnetically engaged.
Pumps that utilize an open/semi-open impeller need a means to adjust the impeller axially relative to the pump case. As the impeller and case wear over time, the clearance between the impeller and the case opens up. This degrades performance; the pump efficiency decreases; and the produced pump pressure can decrease. The impeller is then set to the appropriate clearance from the case during each maintenance cycle, using the external provisions of the pump, thereby not requiring the pump to be taken out of service. The concept of having a rotor that is externally adjustable is industry standard for normal sealed pumps. The mechanisms accompanying axial adjustment in a sealed pump are generally located in the power frame. This is possible with a sealed pump because the impeller is mechanically connected to the ball bearings (in the power frame) through the shaft, etc.
Other features are commonly employed. Shunted process fluid is frequently used for lubrication of bearing surfaces. In magnetically coupled sealless pumps, the bearing surfaces and the interior magnets of the magnetic coupling conventionally are wetted, while the exterior magnets are in atmosphere. Such arrangements require bearing and magnetic mountings on multiple elements.
Rub rings are commonly employed with a component to restrict eccentric rotation upon catastrophic bearing failure. Such rotation can damage sealing canisters. Plates are also used to protect workers from catastrophic component failure. Often, component complexity in arranging these and other details is dictated in magnetically coupled pumps by the pump drive being concentrically outwardly of the driven rotor assembly, usually including an impeller shaft.
The present invention is directed to a magnetically driven centrifugal pump including a pump case, an impeller, a stuffing box and magnetic coupling between an impeller rotor and a drive. A canister extends through the magnetic coupling to form a barrier between the impeller rotor side and the drive side of a pump.
In a first separate aspect of the present invention, the stuffing box includes a stuffing box outer fixed to the pump case and a stuffing box inner threadedly engaged with the stuffing box outer about the axis of impeller rotation. The impeller rotor is axially fixed relative to the stuffing box inner. Rotation of the stuffing box inner relative to the stuffing box outer can then adjust the impeller clearance in the pump case.
In a second separate aspect of the present invention, an annular rotor bushing is between the rotor and the stuffing box inner; an annular impeller bushing is between the impeller hub and the stuffing box inner and two opposed thrust bushings are between the stuffing box inner and the rotor. All may be mounted exterior to the drive. This common access simplifies the stuffing box and facilitates ease of service.
In a third separate aspect of the present invention, the drive is fixed relative to the pump case and includes a drive output. A rub ring is mounted to the stuffing box and extends inwardly to circumferentially surround the drive output to protect the canister. The rub ring closes the end of the stuffing box around the drive output by extending inwardly from a periphery of the stuffing box.
In a fourth separate aspect of the present invention, a process fluid shunt extends in seriatim through the annular impeller bushing, a first of the thrust bushings, the annular rotor bushing, a second of the thrust bushings and the magnetic coupling outwardly of the canister. The arrangement provides further component simplification.
The foregoing separate aspects are contemplated to also be employed in combination with one another. Accordingly, it is an object of the present invention to provide an improved magnetically coupled centrifugal pump. Other and further objects and advantages will appear hereinafter.
Turning in detail to the drawings, the Figures each show the surface of sections through the access of impeller rotation 10. The major components except for the pump case and the pump housing, which are asymmetrical because of volutes and mountings, respectively, are substantially symmetrical about the axis of impeller rotation. The first embodiment,
A pump case 12 defining an impeller cavity and a volute is further defined by a housing structure 13. The pump case 12 surrounds an open vane impeller 14 while the housing structure 13 extends over a stuffing box 16. The impeller 14 includes an impeller hub 15 extending away from the vanes of the impeller 14. The pump case 12 and housing structure 13 are conventionally assembled with bolts. The housing structure 13 is shown in this instance to have an open arrangement with holes about the circumference.
The stuffing box 16 includes a stuffing box outer 18 which is a collar with an outer flange 19 engaging the pump case 12 and held in place by the housing structure 13. The stuffing box 16 further includes a stuffing box inner 20 engaged with the stuffing box outer 18 at a threaded engagement 22. The threaded engagement 22 provides for the stuffing box inner 20 to be rotated relative to the stuffing box outer 18 to allow axial translation of the stuffing box inner 20 relative to the stuffing box outer 18 and in turn the pump case 12. After the desired axial position of the stuffing box inner 20 is achieved, the rotational position of the stuffing box inner can either be held by thread friction or by an external set screw. The stuffing box inner 20 extends from the threaded engagement 22 as a cylinder to a stuffing box inner detachable cap 24. The stuffing box inner detachable cap 24 is held in place by fasteners.
A rotor 26 is located within the annular cavity defined within the stuffing box inner 20. The rotor 26 is also cylindrical with a front wall. A mounting hub 27 fixed on the cylindrical front wall threadedly engages the impeller hub 15 so that the impeller 14 is detachably fixed to the rotor 26. With the rotor 26 located in the annular cavity with thrust bushings described below, the rotor 26 moves axially with the stuffing box inner 20 relative to the stuffing box outer 18. With the stuffing box outer 18 engaging the pump case 12 and the rotor 26 being engaged through the mounting hub 27 with the impeller hub 15, the axial adjustment of the stuffing box inner 20 relative to the stuffing box outer 18 is used to create an appropriate clearance between the impeller 14 and the pump case 12.
A drive 28 is arranged inwardly of the rotor 26. The drive 28 includes a drive output 29 that is cylindrical with an engagement to receive a drive shaft coupled with a motor (not shown) for torque transfer. The drive further includes a drive shaft power frame 30 with a shaft conventionally arranged in with bearings as shown to transfer rotary power from the motor. The housing is conventionally coupled with the housing structure 13 by bolts.
Power to the rotor 26 from the drive 28 is transmitted through a magnetic coupling 31. The magnetic coupling 31 is traditional including driving magnets 32 associated with the drive 28 and driven magnets 34 associated with the rotor 26. A canister 36 extends through the magnetic coupling. The canister 36 is integrally formed with the stuffing box inner detachable cap 24. The stuffing box inner detachable cap 24 and the associated canister 36 are retained by fasteners at the end of the stuffing box inner 20. Thus, the canister 36 does not rotate with either the rotor 26 or the drive 28 but remains stationary in the pump unless the impeller 14 is being axially adjusted. The canister 36 includes a concave end which results in less distortion of the canister 36 under pressure loads from the pump process fluids.
In the preferred embodiment, the rotating components within the stuffing box 16 are mounted through bushings. The bushings used in these embodiments are bushing pairs each with a static bushing associated with the stuffing box inner 20 and a dynamic bushing each associated with the rotor/impeller assembly 26/14. These components are held in place by conventional means. An annular rotor bushing 38 is located between the stuffing box inner 20 and the rotor 26. The annular impeller bushing 40 is between the stuffing box inner 20 and the impeller hub 15. In the first embodiment as illustrated in
A forward thrust bushing 42 is arranged between the stuffing box inner detachable cap 24 and the rotor 26. A rearward thrust bushing 44 is located between the stuffing box wall 25 and the rotor 26. The thrust bushings 42, 44 thus retain the rotor 26 fixed axially within the stuffing box inner 20. Again, all of the annular and thrust bushings are traditionally placed within the pump.
A process fluid shunt 46 lubricates the bushings located about the rotor. A shunt inlet 48 is located outwardly of the impeller hub 15 to extend through the annular impeller bushing 40. A gap between the rotor 26 and the stuffing box wall 25 directs process fluid through the rearward thrust bushing 44. An annular gap between the stuffing box inner 20 and the rotor 26 then permits the shunted process fluid to move to and through the annular rotor bushing 38. An annular cavity adjacent the annular rotor bushing 38 defined in the stuffing box inner detachable cap 24 then directs the shunted process fluid through the forward thrust bushing 42. The shunted process fluid is then released to around the canister 36 where it passes by the wetted magnets 34 and then to the shunt return 50 along the access of impeller rotation 10. The shunt inlet 48 is located outwardly on the open vane impeller 14 of the shunt return 50 located along the access of impeller rotation 10. Thus, rotation of the impeller 14 is able to drive circulation of the shunted process fluid.
A rub ring 52 closes the drive end of the stuffing box inner 20 by extending inwardly to the drive 28. In addition to closing the stuffing box inner 20, the rub ring 52 is associated with a circumferential ring 54 located on the drive 28. The maximum compressive deformation in the ring 54 is less than the gap between the canister 36 and either of the magnet assemblies 32, 34. This prevents damage to the canister 36 by catastrophic failure of any of the bearings.
Thus, an improved magnetically coupled centrifugal pump is shown and described. While embodiments and applications of this invention have been shown and described, it would be apparent to those skilled in the art that many more modifications are possible without departing from the inventive concepts herein. The invention, therefore, is not to be restricted except in the spirit of the appended claims.
This Application claims priority to U.S. Provisional Application 62/416,059, filed Nov. 1, 2016, the disclosure of which is incorporated herein by reference in its entirety.
| Number | Date | Country | |
|---|---|---|---|
| 62416059 | Nov 2016 | US |
