U.S. patent number 3,816,020 [Application Number 05/298,823] was granted by the patent office on 1974-06-11 for pump.
This patent grant is currently assigned to Selgo Pumps, Inc.. Invention is credited to Ethridge F. Ogles.
United States Patent |
3,816,020 |
Ogles |
June 11, 1974 |
PUMP
Abstract
A rotary centrifugal pump having an axial inlet and discharge in
a casing together with an impeller having liquid impelling vanes on
both surfaces thereof with the impeller having central openings
enabling inlet liquid to be impelled by vanes on both surfaces of
the impeller. The pump includes a pressured water cooled bearing
and a seal in which grease or other lubricant is maintained under
pressure by the liquid being pumped. The pump is adapted for use as
a single stage or multiple stage and is capable of producing
relatively high pressures and high volume discharge.
Inventors: |
Ogles; Ethridge F. (Ada,
OK) |
Assignee: |
Selgo Pumps, Inc. (Ada,
OK)
|
Family
ID: |
23152143 |
Appl.
No.: |
05/298,823 |
Filed: |
October 19, 1972 |
Current U.S.
Class: |
415/111; 415/98;
415/180; 415/182.1; 415/208.3 |
Current CPC
Class: |
F04D
29/2211 (20130101); F04D 29/061 (20130101); F04D
29/588 (20130101); F04D 1/06 (20130101); F04D
29/049 (20130101) |
Current International
Class: |
F04D
29/18 (20060101); F04D 29/58 (20060101); F04D
1/00 (20060101); F04D 29/22 (20060101); F04D
1/06 (20060101); F01d 011/00 () |
Field of
Search: |
;415/52,55,59,111,180,182,212 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Husar; C. J.
Attorney, Agent or Firm: O'Brien; Clarence A. Jacobson;
Harvey B.
Claims
What is claimed as new is as follows:
1. A rotary pump comprising a casing having an interior hollow
chamber, a rotary impeller disposed in said chamber, a shaft
connected with said impeller and extending exteriorly of the casing
for rotatably driving the impeller, inlet means in said casing for
admitting flowable material to be pumped to the central portion of
the impeller, said impeller including vanes thereon for impelling
the material as the impeller rotates, outlet means incorporated
into the casing and communicating with the portion of the casing
receiving the periphery of the impeller for receiving the material
impelled by the impeller, said outlet means including radially and
inwardly extending passage defining means communicating with an
outlet pipe extending axially and generally coincident to the
rotational axis of the impeller.
2. The structure as defined in claim 1 wherein said impeller is in
the form of a substantially circular plate, and vanes being
disposed radially on each surface of the plate, the central portion
of the plate including aperture means therein enabling flowable
material to be impelled by the vanes on both sides of the
impeller.
3. The structure as defined in claim 1 wherein said rotary impeller
includes a hub received on said shaft, means rigidly fixing the hub
to said shaft, each end of the hub having a tapering internal
surface, a pair of split tapered collets interposed between the
shaft and the tapered ends of the hub with at least one of the
collets being longitudinally movable on the shaft for centering the
hub and impeller in relation to the shaft, and screw threaded means
connected with the shaft for balancing the collits toward each
other for securing the hub fixedly in concentric relation to the
shaft.
4. The structure defined in claim 2 wherein said aperture means in
the impeller includes a plurality of openings through the plate to
provide hydraulic balance to both surfaces of the impeller
plate.
5. A rotary pump comprising a casing having an interior hollow
chamber, a rotary impeller disposed in said chamber, a shaft
connected with said impeller and extending exteriorly of the casing
for rotatably driving the impeller, inlet means in said casing for
admitting flowable material to be pumped to the central portion of
the impeller, said impeller including vanes thereon for impelling
the material as the impeller rotates, outlet means incorporated
into the casing and communicating with the portion of the casing
receiving the periphery of the impeller for receiving the material
impelled by the impeller, said outlet means including inwardly
extending passage defining means communicating with an outlet pipe
generally coincident to the rotational axis of the impeller, said
impeller being in the form of a substantially circular plate, said
vanes being disposed radially on each surface of the plate, the
central portion of the plate including aperture forming means
therein enabling flowable material to be impelled by the vanes on
both sides of the impeller, said inlet means being in the form of a
tubular member having an inlet pipe communicated therewith, said
shaft being disposed in said tubular member, seal means
interconnecting the shaft and tubular member outwardly of the inlet
pipe for sealing the shaft, and bearing means on said casing
axially outwardly of the tubular member for supporting said shaft
in relation to the casing, and means enabling circulation of
cooling fluid in relation to the bearing means for preventing
excessive temperatures occurring in the bearing means.
6. The structure as defined in claim 5 wherein said means enabling
circulation of cooling fluid including a pipe extending from the
periphery of the chamber in the casing for inlet of cooling fluid,
a pipe communicating with the tubular member to return the cooling
fluid to the inlet means on the pump, and a jacket encircling the
bearing means for enabling circulation of cooling fluid.
7. The structure as defined in claim 6 wherein said seal means
includes a tubular member disposed concentrically within the
tubular member defining the inlet means and receiving a plurality
of seal rings therein in sealing engagement with the shaft,
lubrication means for said seal rings, said lubrication means
including a piston and cylinder to force lubrication means into the
seal rings, and conduit means interconnecting the lubrication
cylinder and piston and the pipe extending from the periphery of
the chamber in the casing for inlet of cooling fluid to the jacket
thereby providing pressure lubrication of the seal rings.
8. A rotary pump comprising a casing having an interior hollow
chamber, a rotary impeller disposed in said chamber, a shaft
connected with said impeller and extending exteriorly of the casing
for rotary driving the impeller, inlet means in said casing for
admitting flowable material to be pumped to the central portion of
the impeller, said impeller including vanes thereon for impelling
the material as the impeller rotates, outlet means incorporated
into the casing and communicating with the portion of the casing
receiving the periphery of the impeller for receiving the material
impelled by the impeller, sad outlet means including inwardly
extending passage defining means communicating with an outlet pipe
generally coincident to the rotational axis of the impeller, said
impeller being in the form of a substantially circular plate, said
vanes being disposed radially on each surface of the plate, the
central portion of the plate including aperture forming means
therein enabling flowable material to be impelled by the vanes on
both sides of the impeller, said impeller including a centrally
disposed annular ring on each side thereof in encircling relation
to the aperture means, one of the rings being received closely
within the inlet means, said casing including a recess receiving
the other annular ring
9. A rotary pump comprising a casing having an interior hollow
chamber, a rotary impeller disposed in said chamber, a shaft
connected with said impeller and extending exteriorly of the casing
for rotatably driving the impeller, inlet means in said casing for
admitting flowable material to be pumped to the central portion of
the impeller, said impeller including vanes thereon for impelling
the material as the impeller rotates, outlet means incorporated
into the casing and communicating with the portion of the casing
receiving the periphery of the impeller for receiving the material
impelled by the impeller, said outlet means including inwardly
extending passage defining means communicating with an outlet pipe
generally coincident to the rotational axis of the impeller, said
outlet means including a substantially circular plate defining the
rear surface of the chamber, said radially extending passage
defining means being rigid with said plate, tapering inlet channels
communicating the outer periphery of the chamber with the radial
passage defining means.
10. The structure as defined in claim 9 wherein said casing is
provided with a deflector ring at the outer periphery of the
impeller, said deflector ring including a plurality of radial
notches therein with each of the notches including an inclined
surface extending circumferentially in the direction of rotation
and inclined axially toward the channels for deflecting the
material being pumped into the channels and passage defining means
for discharge.
11. The structure as defined in claim 10 together with an insert
adapter for converting the pump to a multiple stage pump, said
casing including an inlet portion and a discharge portion, said
portions of the casing being separable at the outer periphery of
the chamber, said insert adapter including a duplication of the
discharge portion and the inlet portion of the casing, a
duplication of the impeller and deflector ring and an extension for
the drive shaft for enabling a single or multiple number of insert
adapters to be incorporated into the pump to enable any number of
stages to be provided.
12. The structure defined in claim 11 wherein said extension for
the drive shaft is threadly connected thereto and includes a
duplicate connection with the impeller.
13. A rotary pump comprising a casing having a hollow interior
chamber with an inlet at one side thereof, a rotary impeller
disposed within said chamber and separating the chamber into two
compartments with the inlet communicating with one compartment,
said impeller including a plate of generally circular configuration
with the periphery of the pate being disposed closely adjacent the
internal periphery of the chamber, said plate including centrally
disposed aperture means communicating the compartments of the
chamber with each other and enabling inlet of flowable material
from the inlet to both compartments for hydraulically balancing the
impeller, said impeller plate including projecting vanes on both
surfaces thereof for impelling flowable material thereof during
rotation, and discharge means communicated with the casing for
discharge of flowable material being pumped.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
The present invention generally relates to a rotary pump having
axial intake and discharge and an impeller having vanes on both
sides thereof for producing a high discharge pressure and a novel
and unique bearing and sealing arrangement for the drive shaft in
relation to the intake of the pump.
2. Description of the Prior Art
Rotary pumps generally of the centrifugal type have been provided
for pumping liquids under various circumstances. An example of one
type pump for this purpose is found in my prior U.S. Pat. No.
3,363,576, issued Jan. 16, 1968. Known centrifugal pumps have been
performed satisfactorily under some conditions but in some
situations, such pumps either perform inefficiently or
inadequately.
SUMMARY OF THE INVENTION
An object of the present invention is to provide a rotary pump
incorporating a casing having a rotary impeller disposed therein
with the impeller having vanes on both surfaces thereof and a
central opening to enable fluid to be pumped from a single axial
inlet by both surfaces of the impeller.
Another object of the invention is to provide a pump in which the
casing is provided with passageways for guiding, directing and
discharging the fluid being pumped from the outer peripheral
portion of the impeller in a radially inward direction for
discharge axially of the pump or axially into a subsequent stage of
the pump.
Another object of the invention is to provide a pump in accordance
with the preceding objects in which the power shaft which drives
the impeller is supported from the casing or other stationary
support by a bearing assembly lubricated by the fluid being pumped
and the power shaft is also sealed by a lubricated seal arrangement
in which the lubricant is maintained under pressure by the pressure
of the fluid being pumped.
A further important object of the present invention is to provide a
rotary pump in which the impeller has central annular ring members
thereon generally in sealing relation to the housing with the
impeller being accurately positioned and supported in relation to
the casing by the bearing and supporting structure for the drive
shaft and a tail shaft provided on the impeller that is journalled
in the casing.
Yet another significant object of the invention is to provide a
rotary pump of the centrifugal type capable of discharge of liquid
at a relatively high volume and high pressure which is efficient in
operation capable of assembly into a single stage or any number of
stages depending upon the output pressure desired, long lasting and
dependable in operation and relatively inexpensive to manufacture
and maintain.
These together with other objects and advantages which will become
subsequently apparent reside in the details of construction and
operation as more fully hereinafter described and claimed,
reference being had to the accompanying drawings forming a part
hereof, wherein like numerals refer to like parts throughout.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a side elevational view of the pump.
FIG. 2 is a longitudinal, sectional view taken substantially upon a
plane passing along section line 2--2 of FIG. 1 illustrating the
relationship of the structural components of the pump.
FIG. 3 is an end elevational view of the impeller and associated
deflector ring and casing with the intake portion of the casing
removed.
FIG. 4 is a view similar to FIG. 3 but with the impeller and
deflector ring removed.
FIG. 5 is an exploded group perspective view illustrating the
components of the pump and their relationship.
FIG. 6 is an elevational view, partially in section, illustrating
the adapter insert by which the pump may be converted from a single
stage to a multiple stage.
FIG. 7 is a group perspective view of the extension assembly used
in the multiple stage pump.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now specifically to the drawings, the pump of the present
invention is generally designated by reference numeral 10 and
includes a casing generally designated by the numeral 12 which
includes an intake portion 14 and a discharge portion 16. The pump
is supplied with rotational power by virtue of a power shaft 18
oriented longitudinally in the casing 12 with the input end thereof
projecting from the intake portion of the casing for connection
with a suitable power source such as an internal combustion engine,
electric motor or the like by any suitable means so that shaft 18
may be rotated at a desired rotational speed with a desired
torque.
The intake portion 14 of the casing 12 includes a longitudinally
extending hollow cylindrical member 20 having a circular plate 22
rigid with one end thereof with reinforcing gussets 24 bracing and
rigidifying the tubular member 20 and plate 22 with respect to each
other. The tubular member 20 is provided with an angularly
extending adapter tube 26 which terminates in a laterally extending
tubular element 28 that forms an inlet for the pump and is
connected to a suitable pipe, conduit or the like for supplying
liquid such as water to the pump.
The gussets 24 extend beyond the end of the tubular member 20 and
rigidly support an annular flange 30 having a plurality of
apertures 32 therein on which is mounted a bearing assembly 34
which journals and supports the shaft 18. The end of the tubular
member 20 is spaced from the flange 30 and receives a seal assembly
36 which sealingly engages the shaft 18 and prevents water leakage
along the shaft 18 from the interior of the pump.
The casing 12 includes a hollow chamber 38 which may be considered
the working chamber of the pump and is annular in configuration and
this chamber receives an impeller generally designated by the
numeral 40 and an annular deflector ring 42 which is stationary
with respect to the casing with the impeller rotating with the
shaft 18.
As illustrated in FIG. 2, the plate 22 abuts and is rigid with a
flange 44 on the discharge portion 16 of the casing with the
periphery of the plate 22 also defining a flange that is secured in
rigid relation with the flange 44 by suitable through bolts
received in apertures 46. The interior surface of the plage 22 is
inclined as at 48 with the inner edge of the inclined surface 48
merging with the interior of the tubular member 20 and the outer
edge of the inclined surface 48 being defined by a shoulder 50 that
extends peripherally of the plate 22 inwardly of the circumference
thereof.
The discharge portion of the casing 16 also includes a plate 52
which has an inclined surface 54 that is integral with the flange
44 and diverges from the inclined surface 48 and cooperates
therewith to define the hollow chamber 38 which receives the
impeller 40. Centrally of the plate 52, there is provided an
annular shoulder or recess 56 that is the same diameter as and in
alignment with the interior of the tubular member 20 with the rear
limit of the recess or shoulder 56 being defined by a circular
plate 58 which forms a rearward partition wall or closure for the
hollow chamber 38.
As illustrated in FIG. 5, the impeller 40 includes a circular plate
60 having a centrally disposed tubular hub 62 therein which extends
to both sides of the plate 60.
Each side of the plate 60 is provided with a plurality of radially
extending but arcuately curved vanes 64 and 66 with the vanes 64
and 66 being in alternate relationship. The vanes 64 extend
completely inwardly to and are joined with the hub 62 while the
inner ends of the vanes 66 terminate in circumferentially spaced
relation to the hub 62. The inner ends of the vanes 64 have the
same depth as the length of the hub 62 projecting from the plate 60
with the inner ends of the vanes 64 being designated by numeral 68
with the outer ends of the inner end portions 68 of the vanes 64
defining axially extending shoulders on which is mounted an annular
ring 70 that is rigidly secured to the shoulders defined by the
juncture of the outer portion of the vane 64 and the inner portion
68 thereof with the outer edge of the ring 70 generally being flush
with the end of the hub 62 as illustrated in FIG. 2. The vanes 66
terminate in alignment with the ring 70 with the vanes 64 and 66
being rigidly secured to the plate 60 and substantially equally
spaced with the omission of the inner ends of the vanes 66
providing an open area inwardly of the ring with an elongated and
generally oval-shaped opening 72 being provided in the plate 60
with the openings 72 communicating between the two sides of the
plate 60. The relationship of the openings 72, the vanes 64 and 66
and the annular ring 70 is illustrated in FIG. 3 with the
relationship of the rings 70 to the interior of the tubular member
20 and the shoulder or recess 56 being illustrated in FIG. 2. Thus,
as water enters through the inlet 28 into the tubular member 20 it
will flow through the ring 70 received in the tubular member 20
with the water being divided with a portion of it being impelled
outwardly along the surface of the impeller plate 60 facing the
tubular member 20 and the remaining portion of the water passing
through the openings 72 and moving radially outwardly and being
impelled by the vanes on the opposite side of the impeller plate 60
thereby providing effective movement of the water or other liquid
during rotation of the impleller 40 in a clockwise direction as
viewed in FIG. 5 with the vanes being arcuately curved so that such
rotation will impel the water or other liquid outwardly in the
annular chamber 38 toward the periphery of the casing 12 where it
comes into contact with the deflector ring 42.
The deflector ring 42 includes an annular member 74 which has an
inner edge 76 that closely surrounds the impeller plate 60 and has
a width substantially equal to the width of the combined impeller
plate 60 and the other ends of the vanes 64 and 66. The inner edge
76 of the annular member 74 is provided with a plurality of
arcuately extending notches 78 defined by an outer periphery that
tapers from the inner edge 76 towards the outer edge of the annular
member in the direction of rotation of the impeller plate 60 with
the terminal edge of each notch 78 being substantially radially
disposed on the side of the annular member 74 which faces the plate
22 as designated by numeral 80 in FIG. 5. The opposite side of each
notch 78, that is, where the notch communicates with the surface of
the annular member 74 which faces the discharge portion 16 of the
casing, the annular member is provided with an elongated arcuately
curved and tapering groove 82 which extends in the direction of
rotation of the impeller so that water which is discharged from the
impeller will enter the notches 78 and be deflected or directed
toward the discharge portion 16 of the casing by the tapering
configuration of the groove 82 which commences at the radial edge
80 which is substantially a feather edge or very thin edge and
inclines towards the surface of the annular member 74 which faces
the discharge portion 16 of the casing. In order to seal the
annular member 74 in relation to the casing, an O-ring of neoprene,
or the like designated by numeral 84 is provided between the inner
edge of the flange 44 which has a recess therein and a
corresponding peripheral notch or recess in the annular member 74.
As illustrated, the plate 52 of the discharge portion is closely
adjacent to the annular member 74 and serves to define the outer
portion of the hollow chamber 38.
At the inner edge of the flange 44, a plurality of tapering
channels or passageways 86 are provided which commence as shallow
grooves at the inlet end 88 thereof and progressively deepen in the
direction of rotation of the impeller and movement of the water or
liquid until they reach a maximum axial depth and communicate with
a radially, inwardly extending curved passageway 90 which extends
to and communicates with the interior of a tubular member 92 which
forms an extension on the plate 58 and which includes an internally
threaded extension 94 that defines a discharge pipe for the liquid
being pumped. As illustrated in FIG. 4, three circumferentially
spaced and isolated channels or passageways 86 are provided with
the tapering of the groove 86 being gradual and continuous into the
passageway 90 with the juncture between the passageway 86 and the
passageway 90 being smoothly curved and rounded with the bottom
limits of the passageway 86 also being curved and generally of
U-shaped configuration as illustrated in FIG. 2. Where the water or
liquid exits from the passageway 90 into the hollow interior of the
tubular member 92, curved deflectors 96 are provided for deflecting
the water and making more efficient movement of the water
possible.
The circular plate 58 is provided with a tubular member 100
extending axially in concentric relation to the tubular member 92
with the outer end thereof being rounded and closed as at 102. The
tubular member 100 forms a bearing member for an internally
threaded extension 104 on the shaft 18. The extension 104 has an
external surface that is journalled in the interior surface of the
tubular member 100 and includes radial openings 106 for receiving a
spanner wrench or the like for threading the extension 104 rigidly
onto the threaded end 108 of a reduced end portion 110 on the shaft
18. The reduced end portion 119 is received within the hub 62 of
the impeller 40 and includes a shoulder 112 at the inner end of the
reduced end portion 110. The reduced end portion 110 receives a
pair of tapered split collars 114 thereon with the inner collar
having its large end abutted against the shoulder 112 and the outer
collar received in the discharge end of the impeller hub 62 with
the end portions of the hub 62 being bevelled at an angle
corresponding to the external surfaces of the collars 114. Also,
the hub 62 and the reduced end portion 110 is grooved to receive a
key 116 in order to securely lock the impeller 40 to the shaft 18
but enable disassembly thereof. A split collar 118 is disposed on
the threaded portion 108 or the outer end of the reduced end
portion 110 with its large end abutting the large end of the
rearmost collar 114 and the tapering surface thereof is engaged
with an internal tapering surface 120 on the extension 104 so that
as the extension 104 is rotated, the internal threads thereon will
fixedly assemble the impeller 40 on the shaft 18 with the shaft and
impeller being concentrically oriented due to the tapered split
collars 114 and 118. The threaded connection of the extension also
enables the pump to be assembled into a multiple stage pump in a
manner defined hereinafter and if desired, the tubular member 100
may be provided with an inserted bushing or the like to extend the
wear capabilities thereof.
Referring now specifically to FIG. 2, the bearing assembly 34
includes a tubular sleeve 122 received on the power shaft between
threaded portions 124 and 126 thereon. The ends of the sleeve 122
are internally tapered at 128 and tapered split collars 130 are
mounted on the shaft 18 in engagement with the tapered ends 128 on
the sleeve 122 and nuts 132 are threaded onto the threaded portions
124 and 126 to rigidly fix the sleeve 122 on the shaft 118 in
concentric relation thereto. The external surface of the sleeve 122
is provided with reduced end portions 134 and 136 which define
shoulders 138 and 140 respectively. The reduced end portions 134
and 136 receive conventional bearing assemblies 142 and 144
respectively with the inner races of the bearing assemblies
engaging the shoulders 138 and 140 as illustrated in FIG. 2.
The bearing assembly 34 also includes an inner end plate 146 that
is apertured for alignment with and engagement with the flange 30
and the apertures 32 therein with the apertures in the plate 146
being designated by numeral 148. One side of the plate 146 is
provided with a projecting shoulder 150 which extends into the
interior of the flange 30 as illustrated in FIG. 2 and the opposite
side of the plate 146 is provided with a cylindrical extension 152
which defines a seat for engaging the external race of the bearing
assembly 142. The bearing assembly 34 also includes a tubular
member 154 which includes an outwardly extending flange 156 on its
inner end having apertures 158 therein for engagement with the
plate 146 and registry with the openings therein so that bolts may
be employed for securing the bearing assembly to the flange 30. The
flange 156 and the internal dimension of the tubular member 154
engage the extension 152 on the plate 146 to provide for accurate
alignment thereof and the outer end of the tubular member 154 is
provided with an inwardly extending flange 160 which engages the
outer race of the bearing assembly 144 and the bolts which extend
through the flange 156 and 30 and the plate 146 serve to retain the
bearing assembly 34 in position and accurately support and align
the shaft 18 with respect to the casing 12 which provides for
accurate positioning of the rotary impeller in relation to the
casing 12.
Disposed around the tubular member 154 is a water jacket 162 in the
form of a tubular member having inturned flanges at each end
thereof and O-ring seals 164 in the inner edge of the flanges in
sealing engagement with the tubular member 154. Threaded fittings
166 and 168 are provided in the water jacket 162 for receiving and
connection with a water line 170 communicated with the high
pressure side of the pump such as the discharge portion thereof and
a similar pipe or conduit 172 interconnects the fitting 168 and a
similar fitting 174 on the inlet 28 of the pump for providing for
circulation of water and cooling of the bearing assembly 34.
Supporting brackets 176 and 178 are provided each of which includes
a split clamp sleeve 180 which encircles a reduced end portion 182
on the tubular member 154 and a corresponding surface on the
discharge pipe or tubular member 92 respectively. This bracket will
effectively retain the water jacket 162 in position or any other
suitable fastening means may be provided for this purpose. The high
pressure water pipe, tube or the like 170 is communicated with the
discharge portion 16 of the casing 12 in any suitable manner such
as by the use of a T-connection 184 provided with a suitable
pressure gauge 186 and the pipe or hose 170 is provided with
another similar T-connection 188 to which a branch pipe 190 is
connected that is associated with the seal assembly 36 with the
pipe 190 including a pressure regulator 192 and a check valve 194
disposed outwardly of a cylinder 196 which has a piston movable
therein and which forces lubricant into the seal assembly with the
lubricant being any suitable grease or the like so that as pressure
is exerted on the outside of the piston within the cylinder 196,
grease will be forced into the seal. A suitable check valve 198 is
provided to prevent water pressure in the pump from reverse flowing
into the lubricant cylinder when the pump is not operating.
The seal assembly 36 includes a tubular member 200 receiving
conventional seal elements with a retaining flange 204 serving to
retain the seal members 202 within the tubular member 200. A
passageway 206 is provided in communication with the lubricant
cylinder 196 through the check valve 198 for retaining lubricant
under pressure within the seal. The inner end of the tubular member
200 is bevelled or tapered at 208 and a collar 210 having a
correspondingly tapered surface can engage the end of the tubular
member 200 and is longitudinally movable on the shaft 18 with an
O-ring seal 212 being provided to prevent water pressure in the
pump from damping the seals 202 when the pump is inoperative
inasmuch as the collar 210 serves as a protecting device against
high pressure water coming into direct contact with the seals 202.
A limit collar 214 is secured to the shaft by a suitable setscrew
in a manner to limit the longitudinal movement of the protective
collar 210 in relation to the tubular member 200. The inner end of
the collar 210 is bevelled or tapered and is maintained as small as
possible in length and diameter to eliminate unnecessary
restrictions in the flow path of the water passing into the
pump.
With this construction, as the shaft is rotated, water enters
through the inlet through the intake tubular member 20 and is
pumped by the impeller and discharged through the notches and
grooves in the deflector ring, the passageways in the discharge
portion of the housing and out through tubular member 92 into the
discharge pipe 94. All components are maintained at a desired
thickness which will provide the requisite strength and at the same
time all flow restrictions are reduced by eliminating sharp corners
and providing deflecting vanes, guides and the like for water
passing through the pump.
The pump may be converted from a single stage pump as illustrated
in FIG. 2 to a multiple stage pump as illustrated in FIG. 6 by the
insertion of an adapter 220 between the intake portion 14 of the
casing and the discharge portion 16 thereof. The adapter 220
includes a duplicate of the plate 52, inclined surface 54 and the
other associated structure of the discharge portion except that the
tubular member is provided at its rearmost end with a duplicate of
the plate 22 and the inclined surface 48 thereon which, when
combined with the discharge portion 16 defines a second chamber the
same as the hollow chamber 38 so that a second rotor positioned
thereon will pump the water through the second stage of the pump.
In inserting the adapter, it is only necessary to remove the
discharge portion 16 from the intake portion 14 and the impeller 40
which is assembled therewith. The extension 104 is also removed and
in lieu thereof, an extension adapter 222 is attached to the
threaded end 108 of the shaft 18. The adapter 222 (see FIG. 7) is
the same as the extension 104 except that it is provided with a
rigid shaft portion 224 that has a threaded end portion 226 thus,
in effect, forming an extension of the reduced end portion 110 of
the shaft 18 so that the extension 104 may be reapplied to the
threaded end 226 in the same manner as it was originally applied to
the threaded end 108 with the association of all the other
components remaining the same.
The foregoing is considered as illustrative only of the principles
of the invention. Further, since numerous modifications and changes
will readily occur to those skilled in the art, it is not desired
to limit the invention to the exact construction and operation
shown and described, and accordingly all suitable modifications and
equivalents may be resorted to, falling within the scope of the
invention.
* * * * *