U.S. patent number 3,918,831 [Application Number 05/439,845] was granted by the patent office on 1975-11-11 for centrifugal pump with variable impeller.
This patent grant is currently assigned to Chandler Evans Inc.. Invention is credited to Charles W. Grennan.
United States Patent |
3,918,831 |
Grennan |
November 11, 1975 |
Centrifugal pump with variable impeller
Abstract
A centrifugal pump with a variable breadth impeller
characterized by telescoping mirror image impeller sections. The
blades on the mating impeller sections cooperate to define multiple
cascades, consisting of pairs of hydraulically parallel flow
channels circumferentially offset from each other, which discharge
into a common collector.
Inventors: |
Grennan; Charles W. (Newington,
CT) |
Assignee: |
Chandler Evans Inc. (West
Hartford, CT)
|
Family
ID: |
23746365 |
Appl.
No.: |
05/439,845 |
Filed: |
February 8, 1974 |
Current U.S.
Class: |
415/131; 415/140;
415/141; 415/143 |
Current CPC
Class: |
F04D
29/2277 (20130101); F04D 29/042 (20130101); F04D
15/0038 (20130101) |
Current International
Class: |
F04D
29/22 (20060101); F04D 29/18 (20060101); F04D
15/00 (20060101); F03B 015/04 (); F01D
007/00 () |
Field of
Search: |
;415/186A,149,133,177,131,140,141,157,204,203,143 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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 a fluid being pumped, means for varying the pump
capacity comprising:
a driver impeller coupled to the pump drive shaft, said driver
impeller including a base member having a plurality of vane
defining projections on a first face thereof;
a driven impeller, said driven impeller including a base member
having a plurality of vane defining projections on a first face
thereof, said driven impeller being positioned with the vanes
thereof facing and engaging the vanes on said driver impeller
whereby said impellers define multiple cascades of flow channels
which discharge into the common pump collector; and
means including an inducer spring positioned within the assembly
defined by said driver and driven impellers for varying the axial
relationship between said impellers, said spring inducing flow into
said flow channels and cooperating with said driver and driven
impellers to establish a preselected impeller flow area at a given
back pressure.
2. The apparatus of claim 1 further comprising:
seal means for hydraulically isolating the pump inlet and collector
regardless of impeller assembly width whereby the pressure
differential across the impeller assembly is balanced against the
inducer spring and the flow areas within the impeller assembly are
sensitive to the pump back pressure.
3. 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
capacity comprising:
a driver impeller coupled to the pump drive shaft, said driver
impeller including a disc-shaped base member having a plurality of
arcuate projections on one face thereof, said projections defining
impeller vanes which increase in width from the inlet toward the
collector;
a driven impeller, said driven impeller including a discshaped base
member having a plurality of arcuate projections on one face
thereof, said projections defining impeller vanes which increase in
width from the inlet toward the collector, said driven impeller
being the mirror image of said driver impeller and being positioned
with the vanes thereof facing and engaging the vanes on said driver
impeller, said engaged impeller vanes cooperating to define pairs
of diverging circumferentially offset flow channels whereby said
impellers define multiple cascades of flow channels which discharge
into the common pump collector; and
self-compensating hubless flow inducer means at least partly
positioned within the assembly defined by said driver and driven
impellers, said flow inducer means varying the axial relationship
between said driver and driven impellers to vary the depth of the
impeller flow channels.
4. The apparatus of claim 3 wherein said hubless flow inducer means
comprises:
an inducer spring, said spring urging said driver and driven
impellers toward one another.
5. The apparatus of claim 4 further comprising:
seal means for fluidically isolating the pump inlet and collector
regardless of the relative position of said impellers whereby the
pressure differential across the impeller assembly will oppose said
inducer spring.
6. The apparatus of claim 3 wherein said inducer means
comprises:
an inducer spring, said spring including flow into the impeller and
cooperating with said driver and driven impellers to establish a
preselected impeller flow area at a given pump back pressure.
7. The apparatus of claim 3 wherein said impeller flow channels are
of constant arc from the inlet to the discharge ends thereof, the
width of said vanes on each impeller approximating the width of the
channels defined by the vanes of the mating impeller.
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
entitled "Centrifugal Pump With Variable Flow Area", now U.S. Pat.
No. 3,806,278 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.
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 breath of the impeller
is adjusted to meet the required pressure conditions. Impeller
breadth adjustment is accomplished through the use of an impeller
which is divided into mirror image male and female sections. The
sections of the impeller are designed to mate with each other
whereby the impeller blades cooperate to define multiple cascades
which discharge into a common collector or volute. These cascades,
which consist of pairs of hydraulically parallel flow channels
circumferentially offset from each other, establish counteracting
pressure pulses which have a subtractive effect leading to constant
pump output pressure. The flow channels, for example the channels
of each parallel pair, may be of identical cross-section or may be
purposefully varied.
The cross-section of the flow channels of the multiple cascades of
a pump in accordance with the present invention is varied by
telescoping the male and female halves of each impeller by causing
movement of one or both of the impeller sections in a direction
parallel to the axis of rotation. This telescoping of the impeller
halves may be achieved through the use of an actuator or actuators
located within the rotating impeller assembly or by an externally
positioned actuator which operates on the impeller assembly. In
accordance with a preferred embodiment of the invention, a
self-compensating pump having an actuator within the rotating
impeller assembly is provided; the actuator balancing the pressure
differential across the impeller against the bias of a hubless
inducer whereby the flow rate in the impeller wil be automatically
sensitive to pump back pressure. Thus, in accordance with the
invention, actuators for varying the impeller geometry may be
designed to provide for automatic compensation. Alternatively
adjustment may be achieved under the control of a human
operator.
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. Restated,
in accordance with the present invention the impeller blades are
themselves of unusual width and, for most applications, the width
of the blades is equal to the width of the channel between the
vanes of the mating part.
Although a conventional volute or diffuser can be employed, in
accordance with a preferred embodiment of the invention a pump may
be characterized by an axial inlet and a toroidal collector. The
toroidal collector will possess 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 centrifugal pump with a
variable geometry impeller in accordance with a preferred
embodiment of the invention;
FIG. 2 is a front view depicting the driver impeller of the pump of
FIG. 1;
FIG. 3 is a front view depicting the driven impeller of the pump of
FIG. 1;
FIG. 4A is an enlarged partial schematic view showing the pump of
FIG. 1 in a low flow, low pressure condition; and
FIG. 4B is an enlarged partial schematic view showing the pump of
FIG. 1 in the high flow, high pressure condition.
DESCRIPTION OF THE PREFERRED EMBODIMENT:
With reference now to FIG. 1, a pump in accordance with a preferred
embodiment of the present invention comprises a variable breadth
impeller comprising two mating impeller sections or halves. A first
of these impeller sections, hereinafter referred to as the driver
impeller, is indicated at 10 in FIGS. 1, 2 and 4. The second
impeller section, hereinafter referred to as the driven impeller,
is indicated at 12 in FIGS. 1, 3 and 4. The driver impeller 10 is
keyed to the pump drive shaft 14 and is held in position on the
drive shaft by means of a lock nut 16. Rearwardly of the driver
impeller 10, and coaxial with the shaft 14, is a conventional face
seal assembly which is indicated generally at 18. A conventionally
loaded wear ring 20 is disposed about a rearwardly extending
portion of the driver impeller 10, as shown between the impeller
and the pump housing, for the purpose of sealing the pump discharge
to the impeller back face. Wear ring 20 is thus located to balance
axial thrust loads. A labyrinth seal may be employed rather than
wear ring 20 if deemed desirable or necessary.
As may be seen from FIGS. 4A and 4B, the driver and driven
amplifiers are telescopingly related and, even in the high
flow-high pressure condition depicted in FIG. 4B, there is
sufficient bearing area for the driven impeller 12 to be caused to
rotate with the drive shaft 14; torque being transmitted to the
driven impeller via the driver impeller 10.
Referring again to FIG. 1, and with reference also to FIGS. 4A and
4B, the driven impeller 12 is provided with an aperture coaxial
with the pump axis and a flange 21 which extends forwardly toward
the pump inlet 22. Impeller flange 21 is engaged by a nut 24 which
has a radially inward extending portion which defines a shoulder at
the upstream end of nut 24. A hubless inducer 26 passes through the
axial aperture in driven impeller 12 and is positioned in a recess
29 provided in the facing surface of the driver impeller 10.
Inducer 26 is, in the disclosed embodiment, a flat coil spring
having a solid washer-like downstream end which is received in
recess 29 of driver impeller 10. The opposite or upstream end of
spring 26 has an external flange which, via an annular spacer
member 30, presses the axially movable driven impeller 12 against
the shaft mounted driver impeller 10. As discussed above, the two
impellers are interlocked through their mirror image vanes. In the
compressed condition, as depicted in FIG. 4A, the hydraulically
parallel flow paths or channels defined by the interlocking vanes
offer minimum flow area for the fluid being pumped. A pair of flow
channels 34 and 36, and the vanes 34' and 36' respectively on the
driver and driven impellers which define these flow channels, are
indicated on FIGS. 2-4.
Fluid discharged radially outward from the flow channels defined by
the driver and driven impellers 10 and 12 is received, in the
disclosed embodiment, in a toroidal collector indicated
schematically at 32. Collector 32 possesses the desirable features
of no cut-water or tongue for generating pulses and does not result
in the generation of a circumferential pressure gradient which is
transmitted to the pump bearings.
A wear ring 38 is radially located with respect to the driver
impeller 10 so as to balance the pressure gradient against the
spring loading of the hubless inducer 26. The wear ring 38 seals
the pump discharge from the inlet and the flow area in the impeller
assembly is thus sensitive to the pump back pressure.
A particularly unique feature of the present invention, as may best
be seen from FIGS. 2 and 3, is the use of a backward curved
impeller having vanes of unusual width. This unusual vane width is
achieved by fabrication of the vanes with an artificial blockage
which gives the impeller an improved hydraulic radius. In the
disclosed embodiment of the invention the flow channels are of
constant arc from the inlet to discharge ends thereof and the width
of the vanes on each of the driver and driven impellers
approximates the width of the channels defined by the vanes of the
mating impeller. In terms of fluid mechanics this design approaches
the optimum hydraulic radius; i.e., minimum friction loss; for a
given area.
During operation of the variable breadth impeller of the present
invention, the hubless inducer 26 performs the function of an axial
inducer charging the fluid into the radial impellers. The pressure
within the impellers will act to separate the impeller assembly
against the tension of the inducer coil 26. This action results
from the location of the wear ring 38 and the pressure forces
generated within the impeller assembly. The breadth of the impeller
is, therefore, directly responsive to system back pressure.
In the above described preferred embodiment of the invention, the
single impeller assembly defines two cascades which charge into a
common collector or volute to thus establish counteracting pressure
pulses. These counteracting pressure pulses have a subtractive
affect and accordingly a substantially constant pump output is
achieved. The desirable characteristics of the present invention
are thus achieved through the use of mirror image impellers
defining multiple cascades which discharge into a common collector.
The desirable affects are enhanced in the disclosed embodiment
through the use of a self-compensating actuator wherein feedback
pressure works against an inducer spring.
Also in the above described preferred embodiment of the invention,
the automatic control of the pump is predicted upon the presumption
that the back pressure of the system within which the pump is
connected will be unaffected by flow rate. Any impeller will
produce a flow rate (Q) directly proportional to the blade or
passage area (S) and peripheral speed (V) and inversely
proportional to the back pressure (P). This relationship may be
stated as follows:
(1) Q = fV.sup.2 S/P
Employing the actuator system discussed above, the impeller will
have a passage area (S) and/or peripheral speed (V) proportional to
back pressure (P). This relationship may be expressed as
follows:
(2) S = fP/V.sup.2
If back pressure is invariant with flow, the system is balanced and
the flow will remain constant within the consistency of the V.sup.2
S/P ratio built into the actuator. If, however, the system back
pressure varies with flow, as with a conventional discharge
throttled plumbing loop, then the actuator will drive the impeller
to the maximum flow position as depicted in FIG. 4B. If this mode
of operation is not desired a different mode of actuation will be
implemented.
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.
* * * * *