|Publication number||US3771910 A|
|Publication date||Nov 13, 1973|
|Filing date||Sep 8, 1971|
|Priority date||Sep 11, 1970|
|Also published as||DE2135529A1, DE2135529B2, DE2135529C3|
|Publication number||US 3771910 A, US 3771910A, US-A-3771910, US3771910 A, US3771910A|
|Original Assignee||Laing Nikolaus|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (7), Referenced by (22), Classifications (25)|
|External Links: USPTO, USPTO Assignment, Espacenet|
Unitedv States Patent n 1 Laing Y Nov. 13, 1973 AXIAL THRUST COMPENSATION FOR CENTRIFUGAL PUMPS lnventor: Nikolaus Laing, l-lofener Weg 35-37, Aldingen bei Stuttgart, Germany Filed: Sept. 8, 1971 Appl. No.: 178,600
 Foreign Application Priority Data Sept. 11, 1970 Austria 8260 11.8. C1 417/420, 415/104, 415/106 Int. Cl F04b 35/04 Field of Search 415/104, 105, 106;
References Cited UNITED STATES PATENTS 2,810,349 10/1957 Zozulin ..417/420 3,107,310 10/1963 Carriere et al.... 417/420 3,354,833 11/1967 Laing 417/420 3,447,469 6/1969 Laing.... 417/420 3,490,379 1/1970 'Laing.... 417/420 3,649,137 3/1972 Laing.... 417/420 3,710,156 1/1973 Laing 417/420 Primary Examiner-C. J. Husar Attorney-Pennie, Edmonds, Morton, Taylor &
Adams  ABSTRACT An inductive driven centrifugal pump having an impeller mounted in a bearing for limited universal movement and including a seal between the impeller and a portion of the pump casing and fluid passage means connecting opposite sides of the impeller whereby fluid pressure acting on opposite sides of the impeller is equalized.
6 Claims, 4 Drawing Figures PATENTEUHUY '1 3 19B SHEET 2 BF 2 IN Vl-QN TOR AXIAL TIIRUST COMPENSATION FOR CENTRIFUGAL PUMPS BACKGROUND OF THE INVENTION kind having a shrouded impeller and a single entry eye, the impeller being rotatable in a casing the interior of which is subjected to wholly or partially to the pressure generated by the pump. In such a pump, the impeller is subject to an axial thrust because of the following. The effective front axially-projected area of the intake eye is unbalanced as to the fluid pressure upon it, namely the mean intake pressure (or suction), which acts on the upstream or front side of the impeller only; whilst the fluid pressure within the casing acts on the axially projected areaof the shroud to result in an axial thrust on the front of the impeller in one sense of direction and in the opposite sense of direction this fluid pressure acts on the back of the impeller over the whole of its projected area. Such pumps are known (and are the particular kind to which the invention applies) in which the impeller rotor unit embodies a magnetic mass having a spherical convex contour corresponding to the spherical concave contour of a thin non-magnetic wall of the casing, there being a small gap between such contours, the rotor unit then being driven as an induction motor by the electromagnetic field of coil windings external to the said wall. For example, centrifugal pumps of this type are described in US Pat. No. 3,354,833. The magnetic forces tend to thrust the rotor unit axially and rearwardly but such thrust is not always sufficient to exceed the net axial thrust due to the fluid pressures above referred to.
When the impeller of such a pump is allowed some universal angular freedom to tilt by running on a spherical-type bearing, the combined effect of the fluid pressure and magnetic thrusts may be such especially when running in a throttled condtion as to lift the impeller rotor unit away from such hearing, which is a circumstance which must be avoided.
The main aim of the invention-is to ensure, in such a pump, that inall circumstances of running the impeller rotor is held in engagement with the bearing.
SUMMARYOF THE INVENTION The invention therefore resides primarily in a centrifugal pump of the kind having a single sided shrouded impeller, a casing in which the pump-generated fluid pressure exists or at least a partial pump pressure exists which greater than that in the intake eye, and a spherical bearing and induction a electromagnetic drive where the pump is provided a seal between the impeller rotor unit and the casing at an effective radius such as to define an axially-projected area approximately equal to the effective axially-projected area of the entry eye of the impeller, the bearing being on the low pressure side of the seal, and fluid communication being provided between the entry eye and the front side of the seal.
By this means, the fluid entry pressure normally excrted on one side of the impeller resulting in net forces tending to lift the impeller from the bearing is relieved.
DESCRIPTION OF THE DRAWINGS The invention includes various embodiments of the foregoing characterising features; four of these are illustrated in .the accompanying drawings in which each of i FIG. 1 is a schematic sectional view in the plane of the median axis of rotation and of a diameter of the impeller of a centrifugal pump constructed according to the invention;
FIG. 2 is a view similar to FIG. 1 of a second embodiment of a pump constructed according to the invention; I
FIG. 3 is a view similar to FIG. 1 of a third embodment of a pump constructed according to the invention; and
' FIG. 4 is a view similar to FIG. 1 of a still fourth embodiment of a pump constructed according to the invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIG. 1 there is illustrated a fixed intake duct 1 of a centrifugal type pump aligned with a hollow stubshaft 2 leading fluid in to the eye region 3 of the an impeller which is'generally indicated. at 4. The impeller has radially-disposed vanes 5 which interattacha front shroud 7 and theimpeller disc 8. The disc 8 is somewhat domed to form a central boss 9, in which on the rear side of the disc is fixed the rotating cup 10 of a spherical bearing having ball 11 and non-rotating cup 12. The cup 12 is sealedly secured in a frustoconical axial extension 13 of a thin, nonmagnetic, concavely spherically contoured casing wall 14 which is joined to the pump casing.
The impeller 4 is part of an impeller rotor unit, comprising the impeller itself and a magnetic mass 15 which is convexly spherically contoured to correspond with the wall 14; the spherical centres of the casing, mass 15; cups 9 and 12 are all common with that of the ball 11, so that the rotor unit as a whole is able to tilt universally as well as to rotate.
External to the wall 14 and not shown, there is provided in known manner' as for example as shown in US Pat. No. 3,354,833 electromagnetic winding to drive the rotor unit in the manner of an induction motor. For that reason the gap between the surfaces of 14 and 15 is made minimal. This gap is, however, in effect a chamber charged at the pump-generated pressure. This pressure is operative therefore on the rearwardly axially-projected area of the rotor unit to tend to thrust the rotor off the bearing; and the same pressure acts on the forwardly axially-projected area of the shroud 7, to thrust the rotor towards the bearing. The two effective areas being substantially equal (as will be explained) the opposed thrusts balance out. The magnetic force between the mass 15 and exterior inductive winding (not shown) still however, produces a rearward thrust on the rotor unit tending to keep the elements 9, l0 and 11 properly engaged.
Holes 16 are bored through the impeller disc 8 so as to form fluid passages connecting the front side of the impeller containing the eye area 3 with the rear or back side of the impeller.
The extension 13 has at its inner end a seal element 17 in the form of an annular lip whose margin is in a plane in which the spherical centre lies. The element 17 has a close clearance from a cylindrical bore 18 which is coaxial in the impeller disc 8 and which the holes 16 connect with the eye region 3. The pressure on the forward side of the seal element 17 is, therefore, the intake or eye pressure of the pump and the bearing is within this low-pressure ambience. The seal element in effect results in relieving the impeller of the axial thrust otherwise caused by the eye pressure. It is true that when the rotor unit tilts, a slight increase of the seal clearance will occur but this is not important if the dimensions are fairly small. The internal hollow A of the mass 15 is frustoconical like the extension 13, so as to afford clearance for rotor tilt. The ends of the duct 1 and stub 2 are complementarily spherical again on the ball-centre to permit the universal tilting required.
Indicated at A is the annular axial projected area of the shroud 7 (which is the same as that of the mass 15) and at B, the like area of the eye (which is the same as that of the seal element 17).
In FIG. 2, so far as they apply the same references are used. In this embodiment of the invention the seal element 20 is relatively much larger in effective area, corresponding to the larger projected area of the eye 3; the area of the shroud is proportionately less. In this case the seal element 20 is screwed on to the tubular axial extension 22 of the wall 14. In order to facilitate assembly the element 20 is notched as at 21 for the engagement of a tool for which access is provided by the hole 16. The size of the element 20 is now such that it could not effectively seal in a cylinder as in FIG. 1, so the mass 15 is provided with a spherically formed liner 23 with which the margin of the element 20 forms a small but constant clearance. The function of the design is the same as in the FIG. 1 example.
In FIG. 3 again like parts have the same references. In this embodiment however the seal is considerably changed. The cup 12 is again mounted on a casing extension 30 and this is itself fixed with a boss 31 forming an axial extension of the casing wall 14. The magnetic mass 15 is provided with a frustoconical internal lining 33 which has an inward flange or lip 34 with a spherically concentricexternal surface. Against this surface bears a seal ring 35 which is a short cylinder slidable axially in a cylindrical annular recess 36 formed in the boss 31. The ring 35 is urged axially, for example by a resilient corrugated washer at 37, so that its edge at 35A bears lightly but positively against the surface of the lip 34. This seal defines substantially the same axially-projected area as that of the eye 3. The hole (or holes) 16 connect the eye with the interior of the mass 15 as before.
Lastly turning to FIG. 4, there is shown a variant of the FIG. 3 embodiment (again the references, where common, are retained) in which the seal is like that of FIG. 3 but mounted in the rotor unit. In this construction the magnetic mass 15 has a skirt-like liner 40 surrounding andwell clear of the support extension 30 of the casing wall 14. The liner 40 has a cylindrical axial channel or recess 41 in which is axially slidable a seal ring 42, again urged axially by a resilient washer (not shown). The edge of the ring 42 is fashioned spherically to bear against the concave interior surface of the wall 14. The function is as in the previous embodiments.
1. A centrifugal pump of the type having a casing, an axial fluid inlet in said casing, a rotatable impeller in said casing having an eye area on the front surface thereof opposite said inlet subjected to the fluid pressure in said inlet and a shrouded area on the front surface extending radially outwardly from said eye area subjected to increased fluid pressure imparted by said impeller when said pump is operating, bearing means mounting said impeller for rotation and adjacent the rear surface thereof, magnetic means on said impeller for effecting a magnetic couple with an inductive drive means, and a separating wall forming a part of said casing sealing said impeller from the inductive drive means; the improvement which comprises including a circular sealing means between said separating wall and said impeller where the axially projected area defined by the sealing means along'the outer diameter thereof is approximately equal to the axially projected area of said eye area, and including fluid passage means in the impeller extending from the eye area on the front side thereof to a rear side thereof axially opposite said eye area whereby the fluid pressure acting on the rear side will be the same as the fluid pressure acting on the eye area.
2. A centrifugal pump according to claim 1 wherein said impeller has a convex spherical surface, said separating wall has a concave spherical surface closely spaced with respect to said convex surface, and wherein said sealing means comprises an annular element fixed to said separating wall, said element being closely spaced from a circular surface on said impeller.
3. A centrifugal pump according to claim 2 wherein said bearing is a spherical bearing and wherein said annular element lies in a plane passing through the center of said bearing.
4. A centrifugal pump according to claim 2 wherein said bearing is a spherical bearing, were said impeller has a concave spherical surface, and where said annular element is closely spaced to the concave surface of said impeller.
5. A centrifugal pump according to claim 1 wherein said sealing means comprises an annular element on said separating wall moveable axially with respect thereto and engaging said impeller.
6. A centrifugal pump according to claim 1 wherein said sealing means comprises an annular element on said impeller moveable axially with respect thereto and engaging said separating wall.
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|U.S. Classification||417/420, 415/104, 415/106|
|International Classification||F04D13/02, F16C17/08, F04D29/04, F04D29/22, F04D13/06, F04D15/00, F16C17/04, F04D29/18|
|Cooperative Classification||F04D29/22, F04D13/024, F04D29/2266, F04D29/186, F04D13/06, F16C17/08, F04D29/041|
|European Classification||F04D29/22, F04D29/22D2, F04D13/06, F04D29/18C, F04D29/041, F04D13/02B3, F16C17/08|