U.S. patent number 3,644,056 [Application Number 05/017,135] was granted by the patent office on 1972-02-22 for centrifugal pump.
This patent grant is currently assigned to Koninklijke Machinefabriek Stork N.V.. Invention is credited to Samuel I. Wiselius.
United States Patent |
3,644,056 |
Wiselius |
February 22, 1972 |
CENTRIFUGAL PUMP
Abstract
A centrifugal pump comprising a vaned impeller which has an
axial inlet wherein the impeller vanes at the inlet end are extend
in the normal direction of rotation of the impeller and in the
axial direction, the extension from that end of the inlet edge
adjacent the impeller hub, to the other end thereof gradually
increasing from zero to a maximum value, and the total extension
with respect to an axial plane through that end of the inlet edge
which is adjacent the hub covering an arc length equivalent to an
angle of between 30.degree. and 180.degree..
Inventors: |
Wiselius; Samuel I. (Hengelo,
NL) |
Assignee: |
Koninklijke Machinefabriek Stork
N.V. (Hengelo, NL)
|
Family
ID: |
21780924 |
Appl.
No.: |
05/017,135 |
Filed: |
March 6, 1970 |
Current U.S.
Class: |
415/218.1;
415/143; 416/179; 415/72; 415/228; 416/188 |
Current CPC
Class: |
F04D
29/2277 (20130101) |
Current International
Class: |
F04D
29/22 (20060101); F04D 29/18 (20060101); F04d
007/00 () |
Field of
Search: |
;415/71,72,77,143,215
;416/176,179,180-188 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Husar; C. J.
Claims
What I claim is:
1. In a centrifugal pump having a drive shaft, a hub assembly fixed
to said drive shaft for rotation therewith about the axis of said
drive shaft, and a plurality of impeller vanes on said hub
assembly, each impeller vane having a main body joined to said hub
assembly along a line curving inwardly with respect to said axis
and terminating at a base point spaced radially outwardly of said
axis, the main body of each impeller vane also having an outer edge
curving inwardly with respect to said axis and terminating in a tip
point spaced radially outwardly from said axis and axially
outwardly of said base point with there being an inner, inlet edge
extending between said tip point and said base point, said outer
edge being contoured to sweep in closely spaced relation of an
associated portion of the pump casing, the improvement wherein:
said tip point is located circumferentially beyond said base point
with respect to the direction of rotation of said shaft such that
planes containing said axis and said base point and said tip point
respectively include an angle having a value between 30.degree. and
180.degree..
2. In a centrifugal pump as defined in claim 1 wherein said angle
is 90.degree..
Description
The invention relates to a centrifugal pump comprising a vaned
impeller which has an axial inlet and which is mounted in a casing,
the inlet edge of said vanes being situated entirely in front of a
plane which passes through that end of the inlet edge which is
adjacent the impeller of and which is perpendicular to the impeller
shaft. the
According to the invention the impeller vanes are extended in the
normal direction of rotation of the impeller and in the axial
direction, at the inlet side with respect to the inlet edge as the
latter would be determined by the required capacity of the pump, is
the extension from that end short term the inlet edge of the vane
which is adjacent the impeller hub, to scales other end thereof
gradually increasing from zero to a maximum value, and is the total
extension with respect to an axial plane through that end of the
inlet edge which is adjacent the hub covering an arc length
equivalent to an angle of between 30.degree. and 180.degree..
As a result of the extension of the front edge of the vane, such
extension being maximum at the outer periphery of the axial inlet,
the incoming liquid comes into contact with the inlet edge of the
vanes at a much smaller angle than 90.degree.. It has been found
that even a relatively small extension gives the required effect.
This reduces any difficulties in connection with the manufacture of
the impeller and it has also surprisingly been found that no
vibration occurs. Since the extension can be relatively small,
there is also a relatively small increase in the vane area so that
the extension does not reduce the efficiency of the pump to any
appreciable extent.
As is described above the said extension of the vanes would not be
required to achieve the desired pump characteristic.
The invention can be applied to various types of centrifugal pump.
For example, the outlet direction of the flow may be radial,
semiaxial/semiradial, or axial. The impeller may be either open or
closed, i.e., provided with a front plate which is secured to and
corotates with the vanes.
The invention will be explained in detail in the following
description with reference to one exemplified embodiment and the
drawing.
FIG. 1 illustrates an impeller of a pump according to the invention
in axial view from the inlet side;
FIG. 2 is a cross section of which a number of axial cross sections
in various planes between the beginning and the end of the vane are
projected on one another in the drawing plane;
FIG. 3 is a perspective view weighing an impeller.
FEDDER THE NUMBER 1
The impeller illustrated in the drawing comprises a backplate 3
which is secured by a hub 2 on a shaft 1, the vanes being secured
to the plate 3. For the sake of clarity, FIG. 1 illustrates only
one vane 4 completely. The end of a vane 5 is also indicated to
show the spacing between the various vanes. The impeller inlet is
denoted by reference 6; in FIG. 1, the maximum diameter of this
inlet is shown by the broken line 7. The connection between the
vane and the backplate 3 is indicated by the line 8. The edge of
the vane which cooperates with the casing for sealing purpose is
denoted by reference 9. The end point of the line 8 at the base
point 10 and the end point of the line 9 at the tip point 11
indicate the boundary points of the inlet edge 12 of the vane 4.
The exit edge of the vane 4 is at 13. The broken line 14 shows how
the inlet edge of the vane 4 would be if it were dimensioned in the
normal way to obtain a required pump characteristic. With respect
to the construction having the inlet edge 14, the vane has an
extension piece 15 past the axial plane which in FIG. 1 intersects
the vane 4 as shown by the dot-dash line 16. This plane passes
through the base point 10, i.e., that end of the inlet edge 12
which is situated on the smallest diameter, and in FIG. 3 it is
defined by the centerline of the shaft 1 and radial lines 17 and
18. The line 17 is situated in the plane perpendicular to the shaft
1 and extending through the base point 10, while the line 18 is
situated in a correspondingly disposed plane passing through the
tip point 11. The extension covers an angle .alpha.. Depending upon
conditions, the angle .alpha. will be between 30.degree. and
180.degree.. As a result of the extension with the part 15 which
extends in the normal direction of rotation of the impeller the
speed of the incoming liquid coming into contact with the leading
edge rotating at high speed will be such, with respect to the said
leading edge 12, that one component will extend along the leading
edge and one component will extend perpendicular to said edge. The
absolute value of the component extending perpendicularly to the
leading edge is much smaller than the absolute value of the actual
speed of the liquid with respect to the leading edge of the vane.
This greatly reduces any risk of cavitation.
In a preferred embodiment the angle .alpha. has a value of
90.degree.. Then the angle between the leading edge of the vane and
the actual direction of the liquid is 30.degree.. The absolute
value of the component of the speed extending perpendicular to the
leading edge is then one-half of the absolute value of the actual
speed of the liquid with respect to the leading edge of the vane.
The decrease in pressure as a result of the speed of the liquid in
this circumstances is only one-fourth of the decrease which would
be the result if the actual speed of the liquid would extent
perpendicular to the leading edge.
FIG. 2 illustrates each point of the impeller in the same plane of
the drawings. Each point of the impeller has been drawn in a plane
extending through the shaft, all said planes being rotated until
they are situated in the drawing plane. This figure therefore shows
how the various points of the vanes are situated axially with
respect to one another.
* * * * *