WO2018085293A1 - Magnetically coupled sealless centrifugal pump - Google Patents

Magnetically coupled sealless centrifugal pump Download PDF

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Publication number
WO2018085293A1
WO2018085293A1 PCT/US2017/059378 US2017059378W WO2018085293A1 WO 2018085293 A1 WO2018085293 A1 WO 2018085293A1 US 2017059378 W US2017059378 W US 2017059378W WO 2018085293 A1 WO2018085293 A1 WO 2018085293A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
stuffing box
rotor
axis
drive output
Prior art date
Application number
PCT/US2017/059378
Other languages
French (fr)
Inventor
Rex Warren Beach
Nicholas William Ortega
James Gregory Farley
Christopher Jon Distaso
Original Assignee
Psg Worldwide, Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Psg Worldwide, Inc. filed Critical Psg Worldwide, Inc.
Priority to CN201780066503.0A priority Critical patent/CN110249135B/en
Priority to EP17867899.1A priority patent/EP3523539B1/en
Priority to CA3041837A priority patent/CA3041837C/en
Priority to MX2019004713A priority patent/MX2019004713A/en
Priority to JP2019544804A priority patent/JP6949975B2/en
Priority to AU2017353926A priority patent/AU2017353926B2/en
Priority to BR112019007743-0A priority patent/BR112019007743B1/en
Publication of WO2018085293A1 publication Critical patent/WO2018085293A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/026—Details of the bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/041—Axial thrust balancing
    • F04D29/0413—Axial thrust balancing hydrostatic; hydrodynamic thrust bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F04D29/0473—Bearings hydrostatic; hydrodynamic for radial pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/622—Adjusting the clearances between rotary and stationary parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/404—Transmission of power through magnetic drive coupling

Definitions

  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • Figure 1 is a cross-sectional elevation of a magnetically driven centrifugal pump taken through the axis of impeller rotation;
  • Figure 2 is a cross-sectional detail of the stuffing box illustrated in Figure 1 ;
  • Figure 3 is a detail of the magnets and bushings in the stuffing box of Figure 2;
  • Figure 4 is a cross-sectional elevation of a second embodiment of a magnetically driven centrifugal pump taken through the axis of impeller rotation;
  • Figure 5 is a cross-sectional detail of the stuffing box illustrated in Figure 4.
  • Figure 6 is a detail of the magnets and bushings in the stuffing box of Figure 5.
  • FIG. 1 each show the surface of sections through the access of impeller rotation 1 0.
  • a bushing is about the hub of the impeller to securely support the rotatable impeller.
  • 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 1 5 extending away from the vanes of the impeller 14.
  • the pump case 12 and housing structure 1 3 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 1 6 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 1 8 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 1 2.
  • 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 1 5 so that the impeller 14 is detachably fixed to the rotor 26.
  • 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.
  • 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 1 2.
  • 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.
  • 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.
  • 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.
  • 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 1 5.
  • the mounting hub 27 includes an outer ring 41 .
  • the annular impeller bushing 40 is engaged with the mounting hub 27. This arrangement thus allows engagement of all of the bushings with the rotor 26.
  • the annular impeller bushing 40 remains between the stuffing box inner 20 and the impeller hub 15 to positively mount the impeller 14.
  • the bushing 48 directly engages the impeller hub 15 to the same end.
  • 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 1 5 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.
  • 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.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A magnetically driven centrifugal pump has a pump case, an open vane impeller in the pump case, a stuffing box including a stuffing box outer being fixed relative to the pump case and a stuffing box inner threadedly engaged with the stuffing box outer, and a rotor axially fixed and rotatably mounted in the stuffing box inner. Bushings are arranged between the rotor and the stuffing box inner. A drive is fixed relative to the pump case and includes a drive output extending into the rotor. There is a magnetic coupling between the rotor and the drive and a canister fixed to the stuffing box and extending through the magnetic coupling to isolate the rotor from the drive. A rub ring closes the end of the stuffing box inner and constrains the drive output from damaging the cannister under catastrophic bearing failure.

Description

S P E C I F I C A T I O N
TITLE
MAGNETICALLY COUPLED SEALLESS CENTRIFUGAL PUMP
BACKGROUND OF THE INVENTION
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.
SUMMARY OF THE INVENTION
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.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a cross-sectional elevation of a magnetically driven centrifugal pump taken through the axis of impeller rotation;
Figure 2 is a cross-sectional detail of the stuffing box illustrated in Figure 1 ;
Figure 3 is a detail of the magnets and bushings in the stuffing box of Figure 2;
Figure 4 is a cross-sectional elevation of a second embodiment of a magnetically driven centrifugal pump taken through the axis of impeller rotation;
Figure 5 is a cross-sectional detail of the stuffing box illustrated in Figure 4; and
Figure 6 is a detail of the magnets and bushings in the stuffing box of Figure 5. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Turning in detail to the drawings, the Figures each show the surface of sections through the access of impeller rotation 1 0. 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, Figures 1 through 3, differ from the second embodiment, Figures 4 through 6, by the support arrangements for the impeller. In both embodiments, a bushing is about the hub of the impeller to securely support the rotatable impeller.
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 1 5 extending away from the vanes of the impeller 14. The pump case 12 and housing structure 1 3 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 1 6 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 1 8 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 1 2. 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 1 5 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 1 2.
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 1 5. In the first embodiment as illustrated in Figures 1 through 3, the mounting hub 27 includes an outer ring 41 . The annular impeller bushing 40 is engaged with the mounting hub 27. This arrangement thus allows engagement of all of the bushings with the rotor 26. At the same time, the annular impeller bushing 40 remains between the stuffing box inner 20 and the impeller hub 15 to positively mount the impeller 14. In the second embodiment, as seen in Figures 4 through 6, the bushing 48 directly engages the impeller hub 15 to the same end. With either arrangement, the rotor 26 is rotationally mounted by the annular rotor bushing 38 and the annular impeller bushing 40 within the stuffing box inner 20.
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 1 5 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.

Claims

Claims:
1 . A magnetically driven centrifugal pump having an axis of impeller rotation (10), comprising
a pump case (12);
an open vane impeller (14) in the pump case (12) rotatably mounted about the axis of impeller rotation (10);
a stuffing box (16) including a stuffing box outer (18) being fixed relative to the pump case (12) and a stuffing box inner (20) threadedly engaged with the stuffing box outer (18) about the axis of impeller rotation (10);
a rotor (26) axially fixed and rotatably mounted about the axis of impeller rotation (10) in the stuffing box inner (20), the impeller (14) being fixed to rotate with the rotor (26);
a drive (28) fixed relative to the pump case (12) and including a drive output (29) rotatably mounted about the axis of impeller rotation (10) and extending into the stuffing box(16);
a magnetic coupling (30) between the rotor (26) and the drive output (29); a canister (36) fixed to the stuffing box (1 6) and extending through the magnetic coupling (30) to isolate the rotor (26) from the drive (28).
2. The magnetically driven centrifugal pump of claim 1 further comprising
an annular rotor bushing (38) between the rotor (26) and the stuffing box inner (20);
an annular impeller bushing (40) between the impeller (14) and the stuffing box inner (20);
two opposed thrust bushings (42, 44), a first of the opposed thrust bushings (44) being between the stuffing box inner (20) and the rotor (26).
3. The magnetically driven centrifugal pump of claim 2, the stuffing box inner (20) including a detachable cap (24), a second of the two thrust bushings (42) being between the detachable cap (24) and the rotor (26).
4. The magnetically driven centrifugal pump of claim 3 further comprising
a process fluid shunt (46) extending from a first location (48) in
communication with the impeller (14), through the annular impeller bushing (40), the first of the thrust bushings (44), the annular rotor bushing (38), a second of the thrust bushings (42) and the magnetic coupling (30) outwardly of the canister (36), in seriatim, to a second location (50) in communication with the impeller (14), the first location (48) being outwardly of the second location (50) from the axis of impeller rotation (10).
5. The magnetically driven centrifugal pump of claim 2, the annular impeller bushing (40) being engaged with the impeller (14).
6. The magnetically driven centrifugal pump of claim 1 further comprising a rub ring (52) mounted to the stuffing box (16) and extending inwardly to circumferentially surround the drive output (29), the drive output (29) including a circumferential ring (54) at the rub ring (52), the rub ring having a maximum compressive deformation, the canister (36) being circumferentially spaced from the drive output (29) at a distance greater than the maximum compressive deformation.
7. A magnetically driven centrifugal pump having an axis of impeller rotation (10), comprising
a pump case (12);
an impeller (14) in the pump case (12) rotatably mounted about the axis of impeller rotation (10), the impeller (14) including vanes and an impeller hub (15); a stuffing box (16) mounted in the pump case (1 2);
a rotor (26) axially fixed and rotatably mounted about the axis of impeller rotation (10) in the stuffing box (16), the rotor (26) having a mounting hub (27) fixed thereto about the axis of impeller rotation (10), the impeller hub (15) being detachably fixed to rotate with the mounting hub (27);
a drive (28) fixed relative to the pump case (12) and including a drive output (29) rotatably mounted about the axis of impeller rotation (10) relative to and extending into the rotor (26);
a magnetic coupling (30) between the rotor (26) and the drive output (29); a canister (36) fixed to the stuffing box (1 6) and extending through the magnetic coupling (30) to isolate the rotor (26) from the drive (28).
an annular rotor bushing (38) between the rotor (26) and the stuffing box (16);
an annular impeller bushing (40) between the impeller hub (27) and the stuffing box (16);
two opposed thrust bushings (42, 44), a first of the opposed thrust bushings (44) being between the stuffing box (1 6) and the rotor (26), the annular rotor bushing (38) and the annular impeller bushing (40) being mounted to rotationally support the rotor (26) and the impeller (14).
8. The magnetically driven centrifugal pump of claim 7, the impeller (14) being threadedly engaged with the mounting hub (27).
9. The magnetically driven centrifugal pump of claim 7, the stuffing box (16) including a detachable cap (24), a second of the two thrust bushings (42) being between the detachable cap (24) and the rotor (26).
10. The magnetically driven centrifugal pump of claim 9 further comprising
a process fluid shunt (46) extending from a first location (48) in
communication with the impeller (14), through the annular impeller bushing (40), the first of the thrust bushings (44), the annular rotor bushing (38), a second of the thrust bushings (42) and the magnetic coupling (30) outwardly of the canister (36), in seriatim, to a second location (50) in communication with the impeller (14), the first location (48) being outwardly of the second location (50) from the axis of impeller rotation (10).
1 1 . The magnetically driven centrifugal pump of claim 7 further comprising
a rub ring (52) mounted to the stuffing box (16) and extending inwardly to circumferentially surround the drive output (29), the drive output (29) including a circumferential ring (54) at the rub ring (52) having a maximum compressive deformation, the canister (36) being circumferentially spaced from the drive output (29) at a distance greater than the maximum compressive deformation.
12. A magnetically driven centrifugal pump having an axis of impeller rotation (10), comprising
a pump case (12);
an impeller (14) in the pump case (12) rotatably mounted about the axis of impeller rotation (10);
a stuffing box (16) fixed relative to the pump case (12);
a rotor (26) axially fixed and rotatably mounted about the axis of impeller rotation (10) in the stuffing box (16), the impeller (14) being fixed to rotate with the rotor (26);
a drive (28) fixed relative to the pump case (12) and including a drive output (29) rotatably mounted about the axis of impeller rotation (10) and extending into the rotor (26);
a magnetic coupling (30) between the rotor (26) and the drive output (29); a canister (36) fixed to the stuffing box (1 6) and extending through the magnetic coupling (30) to isolate the rotor (26) from the drive (28);
a rub ring (52) mounted to the stuffing box (16) and extending inwardly from a periphery of the stuffing box (1 6) to circumferentially surround the drive output (29), the drive output (29) including a circumferential ring (54) having a maximum compressive deformation, the canister (36) being circumferentially spaced from the drive output (29) at a distance greater than the maximum compressive deformation.
PCT/US2017/059378 2016-11-01 2017-10-31 Magnetically coupled sealless centrifugal pump WO2018085293A1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
CN201780066503.0A CN110249135B (en) 2016-11-01 2017-10-31 Magnetic coupling seal-free centrifugal pump
EP17867899.1A EP3523539B1 (en) 2016-11-01 2017-10-31 Magnetically coupled sealless centrifugal pump
CA3041837A CA3041837C (en) 2016-11-01 2017-10-31 Magnetically coupled sealless centrifugal pump
MX2019004713A MX2019004713A (en) 2016-11-01 2017-10-31 Magnetically coupled sealless centrifugal pump.
JP2019544804A JP6949975B2 (en) 2016-11-01 2017-10-31 Magnetically coupled sealless centrifugal pump
AU2017353926A AU2017353926B2 (en) 2016-11-01 2017-10-31 Magnetically coupled sealless centrifugal pump
BR112019007743-0A BR112019007743B1 (en) 2016-11-01 2017-10-31 CENTRIFUGAL PUMP WITHOUT MAGNETICALLY COUPLED SEALING

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201662416059P 2016-11-01 2016-11-01
US62/416,059 2016-11-01

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EP (1) EP3523539B1 (en)
JP (1) JP6949975B2 (en)
CN (1) CN110249135B (en)
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US11396890B2 (en) 2022-07-26
JP6949975B2 (en) 2021-10-13
US20200256340A1 (en) 2020-08-13
US10738782B2 (en) 2020-08-11
US20180119698A1 (en) 2018-05-03
AU2017353926B2 (en) 2020-04-30
EP3523539A1 (en) 2019-08-14
EP3523539B1 (en) 2020-08-12
CA3041837A1 (en) 2018-05-11
AU2017353926A1 (en) 2019-05-02
JP2019534423A (en) 2019-11-28
MX2019004713A (en) 2019-12-11
BR112019007743A2 (en) 2019-07-09
EP3523539A4 (en) 2019-10-02
CA3041837C (en) 2021-08-10
CN110249135A (en) 2019-09-17
CN110249135B (en) 2021-09-21

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