U.S. patent number 3,901,623 [Application Number 05/439,844] was granted by the patent office on 1975-08-26 for pivotal vane centrifugal.
This patent grant is currently assigned to Chandler Evans Inc.. Invention is credited to Charles W. Grennan.
United States Patent |
3,901,623 |
Grennan |
August 26, 1975 |
Pivotal vane centrifugal
Abstract
A centrifugal pump having a radial flow impeller characterized
by pivotally mounted vanes. The vanes are shaped and positioned
with respect to one another whereby the dimensions of the flow
channels defined by adjacent vanes may be varied to meet the
required pressure conditions.
Inventors: |
Grennan; Charles W. (Newington,
CT) |
Assignee: |
Chandler Evans Inc. (West
Hartford, CT)
|
Family
ID: |
23746360 |
Appl.
No.: |
05/439,844 |
Filed: |
February 8, 1974 |
Current U.S.
Class: |
415/141;
415/224.5; 416/186A; 415/174.2; 415/900; 416/244R |
Current CPC
Class: |
F04D
29/247 (20130101); F04D 15/0055 (20130101); Y10S
415/90 (20130101) |
Current International
Class: |
F04D
29/24 (20060101); F04D 29/18 (20060101); F04D
15/00 (20060101); F01d 005/12 () |
Field of
Search: |
;416/186A
;415/129,130,140,141 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
|
|
|
|
|
|
|
702,816 |
|
Jan 1954 |
|
GB |
|
788,550 |
|
Jan 1958 |
|
GB |
|
Primary Examiner: Raduazo; Henry F.
Claims
What is claimed is:
1. In a radial flow centrifugal pump, said pump having a drive
shaft and a housing which defines an axial inlet and a collector
for receiving fluid being pumped, means for varying the pump flow
area comprising:
impeller means, said impeller means including a plurality of
pivotally mounted vanes, said vanes being pivotal about axes
oriented parallelly to and disposed circumferentially about the
axis of rotation of the impeller means, said vanes being mounted
for pivoting adjacent their discharge ends and being characterized
by increasing width from their inlet to discharge ends, said vanes
cooperating to define flow channels of variable width therebetween,
the shape and mounting of each of said vanes resulting in the
generation of a pivotal moment in the direction of maximum flow
channel width in response to the summation of the pressure and
mechanical forces applied to the vanes;
means for mounting said impeller means on the pump drive shaft;
and
spring means for loading said pivotal vanes toward the channel
width position commensurate with minimum flow, said spring means
generating forces substantially equal and opposite to the pressure
and mechanical forces imposed on the vanes under minimum flow
conditions, on the operation of said pump the pressure forces on
the vanes and thus the pump blade-to-blade channel width increasing
in response to increases in pump back pressure.
2. The apparatus of claim 1 wherein said spring means each
comprises:
a torsion spring.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention relates to improving the operating
characteristics of pumps and particularly centrifugal pumps which
are required to operate at low flow rates over a wide range of back
pressures with a high maximum output pressure. More specifically,
this invention is directed to low specific speed pumps with radial
stage impellers. Accordingly, the general objects of the present
invention are to provide novel and improved methods and apparatus
of such character.
2. Description of the Prior Art
The present invention has been found to be particularly well suited
for use with centrifugal pumps having a radial flow impeller; such
pumps having an axial inlet and radial discharge for fluid
delivered thereto. The achievement of constant flow, particularly
with varying back pressure, has proven to be an elusive objective
for designers of centrifugal pumps. Restated, a long felt need in
the pump arts is to provide a centrifugal pump which would have the
linear pressure-flow characteristics of a positive displacement
pump, such as a gear or piston pump, but which would not subject
the fluid being pumped to the coarse handling characteristics of a
positive displacement pump. Thus, by way of example, there has not
previously been available a high pressure, low flow centrifugal
pump which would provide an output characterized by minimum
hydraulic noise regardless of variations in back pressure. Such a
pump would, for example, be desirable for use in any control system
sensitive to flow pulsations or in cases where the process fluid
could not stand harsh treatment conditions. The processing of food
or blood plasma is an example where the process fluid must not be
subjected to the coarse handling which is characteristic of
positive displacement pumps. Numerous control systems, such as
those on submarines, present environments where the hydraulic noise
associated with output pressure pulsations is undesirable or
unacceptable.
As discussed above, it has long been desired to provide a
centrifugal pump which would duplicate the constant flow with
varying pressure characteristics of a positive displacement pump.
In addition to the above briefly described examples of where such a
pump could be employed, it is also to be noted that positive
displacement pumps are characteristically sensitive to and thus can
not be employed in the handling of contaminated fluids; i.e.,
fluids with entrained particulate matter. Conversely, centrifugal
pumps are very insensitive to entrained particulate matter and
their ability to handle contaminated fluids is well known. The
applications for pumps providing a constant flow at varying back
pressures while moving contaminated fluids are numerous.
While the above discussion has emphasized a constant flow rate, it
is to be observed that a concomitant long standing desire has been
the provision of a centrifugal pump which can affectively and
quietly vary its flow and pressure to match system demands.
Previous attempts to produce such a pump have resorted to varying
pump speed, throttling techniques or variable pump geometry. As is
well known, pressure rise and flow may be varied by changing pump
speed. However, since the rate of pressure rise does not vary
linearly with the flow capacity of a fixed geometry centrifugal
pump with increases in speed, variations in pump speed offer a
limited solution; i.e., system demands can be matched only over a
limited range of pressures and flows. Throttling, and its
counterpart bypassing, inherently results in inefficient operation
with attendant noise and process fluid temperature increases.
Conventional throttling or bypassing techniques are, accordingly,
not suitable for environments where either noise or the
preservation of the characteristics of the process fluid are
considerations. For an example of a centrifugal pump which employs
throttling at the inlet, reference may be had to Mottram et al.
U.S. Pat. No. 3,442,220. Throttling at the pump input, as is well
known in the art, results in cavitation and thus hydraulic noise.
There are other centrifugal pumps known in the art which resort to
throttling at the pump outlet. U.S. Pat. No. 3,168,870 to
Hornschuch is representative of the prior art technique of internal
bypassing in the interest of varying centrifugal pump capacity.
Centrifugal pumps with variable impeller geometry are also known.
For an example of a centrifugal pump with a variable geometry
impeller which is adapted to high specific speed applications,
reference may be had to copending application Ser. No. 277,593 now
U.S. Pat. No. 3,806,278 entitled "Centrifugal Pump With Variable
Flow Area" which is assigned to the assignee of the present
invention. A further approach to variable geometry impellers are
those proposed pumps which have blade configurations of
conventional cross-section and a single flow channel without pulse
generation compensation. For examples of such further proposed
variable geometry pumps reference may be had to U.S. Pat. No.
2,927,536 to Rhoades and U.S. Pat. No. 3,482,523 to Morando.
It is to be noted that there have, in the prior art, been hydraulic
pump/turbines and variable pitch aircraft propellers which employed
pivoting vanes or blades. These prior art devices have, however,
been predominantly axial flow machines whereas a centrifugal pump
is a radial flow machine. Prior art fluid handling devices with
pivotal blades have also been characterized by rather complex
external actuators which controlled the pivoting of the vanes or
blades about a radial to the main axis of rotation of the
devices.
SUMMARY OF THE INVENTION
The present invention overcomes the above discussed and other
problems of the prior art by providing a novel and improved radial
flow centrifugal pump which is characterized by a variable flow
area. In accordance with the invention the vanes of a radial flow
impeller are pivotally mounted, adjacent their outer periphery, and
are shaped and positioned with respect to one another so as to
permit adjustment of the dimensions of the flow channels between
the pump axial inlet and discharge to meet the required pressure
conditions.
In a preferred embodiment the invention employs curved impeller
blades designed with an artificial blockage which gives the pump an
improved hydraulic radius when compared to the prior art.
Although a conventional volute or diffuser can be employed as the
collector, in a preferred embodiment of the invention the pump may
be characterized by an axial inlet and toroidal collector. The
toroidal collector possesses the desirable features of no cut-water
or tongue for generating pressure pulses.
BRIEF DESCRIPTION OF THE DRAWING
The present invention may be better understood and its numerous
objects and advantages will become apparent to those skilled in the
art by reference to the accompanying drawing wherein like reference
numerals refer to like elements in the several figures and in
which:
FIG. 1 is a cross-sectional, top view of a preferred embodiment of
a self-compensating centrifugal pump with a variable geometry
impeller in accordance with the invention;
FIG. 2 is a front elevation view, partially broken away, of the
impeller assembly of the pump of FIG. 1 in the high flow, high
pressure condition; and
FIG. 3 is a front view, partially broken away, of the impeller
assembly of the pump of FIG. 1 in the low flow, low pressure
condition.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring simultaneously to FIGS. 1-3, a pump in accordance with
the preferred embodiment of the present invention includes a
housing which defines an axial inlet 10 and a toroidal collector
12. As discussed above, the pump includes a pivoting vane impeller
assembly. This impeller assembly is defined by a plurality of
pivotally mounted blades disposed between vaneless front and back
shrounds. The front shroud, or driven vane retainer, is indicated
at 14. The back shroud, or driver vane retainer, is indicated at
16. The driver and driven retainer are held together by a plurality
of through bolts and associated spacers. One of several through
bolts is shown at 18 in FIG. 1. A sleeve or spacer 20 is disposed
about each of the through bolts 18; the sleeves being located by
means of engagement with shoulders formed on the facing surfaces of
the driver and driven vane retainers. The sleeves 20 provide the
pivot points for the vanes, such as vane 22, and also as the
anchors for preload torsion springs, such as spring 24.
The impeller assembly is keyed to the pump drive shaft 34 and is
held in position on the drive shaft by means of a lock nut 26. A
conventional face seal assembly, indicated generally at 28, engages
the rearwardly facing side of the driver retainer 16 as shown. Wear
rings 30 and 32 are respectively provided, for thrust balancing
purposes, between flanges on the driver and driven vane retainers
and the pump housing. The wear rings 30 and 32 are located to
balance axial thrust loads, as is common with prior art open face
impellers, and these wear rings seal the impeller discharge
respectively to the impeller assembly back face and inlet.
Conventional labyrinth seals may be employed in place of wear rings
30 and 32.
FIG. 2 shows the vanes of the pump of FIG. 1 in the high
pressure-high volume flow position. FIG. 3 shows the vanes in the
low pressure-low volume position. Through joint consideration of
FIGS. 2 and 3 it may be seen that the area of the flow channels
defined by the spaces between the pivoting vanes is variable. The
vanes 22 are conventionally curved backwardly. The vanes 22 are,
however, of unusual width when compared to the prior art. The
increased width, at the downstream or discharge ends of the vanes,
is achieved by shaping the vanes whereby they impart an artificial
blockage to fluid flow thereby improving the hydraulic radius of
the impeller. In terms of fluid mechanics the impeller of the
present invention thus approaches the optimum hydraulic radius;
i.e., the minimum friction loss; for a given flow area.
Pumps in accordance with the present invention are
self-compensating and operation of the pivoting vane impeller is
effected by the action of the back pressure against the vane
surfaces producing a moment around the pivot point. The net effect
of this moment, the inertial and centripetal loads plus the pivot
friction is resisted by the coil springs 24 around each pivot; the
coil springs having a tang which engages the walls of a recess
formed in each blade as shown in FIG. 1. Increasing back pressure
thus increases the blade-to-blade channel width, the effective
outside diameter of the impeller and the blade angle. All of these
factors improve the impeller's ability to sustain the requisite
flow against the higher back pressure.
While a preferred embodiment has been shown and described, various
modifications and substitutions may be made thereto without
departing from the spirit and scope of the invention. Accordingly,
it is to be understood that the present invention has been
described by way of illustration and not limitation.
* * * * *